Integrated bearing system for shafts in dynamic support pump systems

Abstract

Pump systems for pressurized fluid within a closed loop transmission bus are disclosed herein. An example of the pump systems disclosed herein includes a pump including an impeller to increase kinetic energy of fluid flowing through the impeller, an electric motor including a rotor shaft coupled to the impeller to provide torque to the rotor shaft, a first bearing to support the rotor shaft at a first operating speed range, the first bearing coupled to an inner race, a second bearing to support the rotor shaft at a second operating speed range, the rotor shaft coupled to an outer race, and one or more canting elements configured to: engage the inner race with the outer race at the first operating speed range; and disengage the inner race from the outer race at the second operating speed range.

Description

Technical Field

[0001] This disclosure generally relates to fluid pumps, and more specifically, to an integrated bearing system for a shaft in a dynamically supported pump system. Background Technology

[0002] Aircraft typically include various accessory systems that support the operation of the aircraft and / or its gas turbine engines. For example, such accessory systems may include lubrication systems for lubricating engine components, engine cooling systems for supplying cooling air to engine components, and environmental control systems for supplying cooled air to the aircraft's cockpit. Therefore, during the operation of these accessory systems, heat is added to or removed from fluids (e.g., oil, air, etc.). Attached Figure Description

[0003] Figure 1 This is a side view of the example aircraft.

[0004] Figure 2 This is a schematic cross-sectional view of an example gas turbine engine for an aircraft.

[0005] Figure 3 This is a schematic diagram of an example thermal management system used to transfer heat between fluids.

[0006] Figure 4 An example heat transfer bus pump is shown.

[0007] Figure 5 A first example radially coupled fluid pump system is shown in accordance with the teachings disclosed herein.

[0008] Figure 6 A second example radially coupled fluid pump system is shown in accordance with the teachings disclosed herein.

[0009] Figure 7 A third example of a radially coupled fluid pump system is shown, based on the teachings disclosed herein.

[0010] Figure 8 This is a flowchart illustrating the operation of a radially coupled fluid pump system.

[0011] Figure 9 An example integrated bearing system for dynamically supporting a rotating shaft in an example pump system, in accordance with the teachings of this disclosure, is shown.

[0012] Figure 10 An example integrated bearing system for dynamically supporting a rotating shaft in an example pump system, in accordance with the teachings of this disclosure, is shown.

[0013] Figure 11 An example swashplate clutch for engaging and disengaging a bearing in an example integrated bearing system, in accordance with the teachings of this disclosure, is shown.

[0014] Figure 12A An example engagement state of an example brace element of an example integrated bearing system according to the teachings of this disclosure is shown.

[0015] Figure 12B An example of the separated state of an example brace element of an example integrated bearing system according to the teachings of this disclosure is shown.

[0016] Figure 13 An example load path supported by an example integrated bearing system during operation of an example pump system, in accordance with the teachings of this disclosure, is shown.

[0017] Figure 14 This is a flowchart illustrating the example operation of an example integrated bearing system for an example pump system.

[0018] Figure 15 A first example barrier jar is shown in accordance with the teachings disclosed herein.

[0019] Figure 16 It shows that it can be used Figure 15 The first example barrier tank uses an example inner shell layer.

[0020] Figure 17A A cross-section of the first example barrier tank is shown after the first example manufacturing operation.

[0021] Figure 17B A cross-section of the first example barrier tank is shown after the second example manufacturing operation.

[0022] Figure 17C A cross-section of the first example barrier tank is shown after the third example manufacturing operation.

[0023] Figure 18 It means manufacturing Figure 15 and 17A A flowchart of the example method for the first example barrier jar in -C.

[0024] Figure 19 A second example barrier jar is shown in accordance with the teachings disclosed herein.

[0025] Figure 20A It shows Figure 19 The second example barrier can of the first example fiber.

[0026] Figure 20B It shows Figure 19 The second example of the barrier can and the second example of the fiber.

[0027] Figure 20C It shows Figure 19 The second example barrier tank and the third example fiber.

[0028] Figure 20D It shows Figure 19 The second example barrier tank and the fourth example fiber.

[0029] Figure 21 It shows Figure 19 A magnified view of a portion of the second example barrier jar.

[0030] Figure 22A It means manufacturing Figure 19 , 20A The flowchart of the example method for the second example barrier jar with -D and 21.

[0031] Figure 22B It means manufacturing Figure 19 , 20A The flowchart of another example method for the second example barrier tank with -D and 21.

[0032] Figure 23 An example pump system including a first example oil separator is shown in accordance with the teachings disclosed herein.

[0033] Figure 24 Another example pump system including a second example oil separator is shown in accordance with the teachings disclosed herein.

[0034] Figure 25 Another example pump system, including a second example oil separator and a third example oil separator, is shown in accordance with the teachings disclosed herein.

[0035] Figure 26 Another example pump system including a planetary gearbox is shown in accordance with the teachings disclosed herein.

[0036] Figure 27 It shows Figure 26 The cross-section of the planetary gearbox.

[0037] Figure 28 Another example pump system including a bearing assembly is shown in accordance with the teachings disclosed herein.

[0038] Figure 29 It is by Figure 28 A schematic representation of the support provided by the bearing assembly.

[0039] Figure 30A It shows that it can be used Figure 23-26 The first example rotary separator used in the pump system of 28.

[0040] Figure 30B It shows that it can be used Figure 23-26 The second example rotary separator used in the pump system of 28.

[0041] Figure 30C It shows that it can be used Figure 23-26 The third example rotary separator used in the pump system of 28.

[0042] Figure 31A It shows that it can be used Figure 23-26 The first example of a static separator used in the pump system of 28.

[0043] Figure 31B It shows Figure 31A The first example of a stationary separator is another example of a directional separator.

[0044] Figure 31C It shows that it can be used Figure 23-26 The second example of a stationary separator used in the pump system of 28.

[0045] Figure 32 It is possible to be with Figure 23-26 A schematic representation of a first example layout associated with the pump system of 28.

[0046] Figure 33 It is possible to be with Figure 23-26 A schematic representation of a second example layout associated with the pump system of 28.

[0047] Figure 34 It is possible to be with Figure 23-26 A schematic representation of a third example layout associated with the pump system of 28.

[0048] Figure 35 It is possible to be with Figure 23-26 A schematic representation of a fourth example layout associated with the pump system of 28.

[0049] Figure 36 A first example axial flux motor driven pump system for fluid in a pressurized closed-loop system is shown in accordance with the teachings of this disclosure.

[0050] Figure 37 A second example axial flux motor driven pump system for fluid in a pressurized closed-loop system is shown in accordance with the teachings of this disclosure.

[0051] The figures are not drawn to scale. Generally, the same reference numerals will be used throughout the figures and accompanying written description to refer to the same or similar parts. Detailed Implementation

[0052] "Comprising" and "including" (and all their forms and tenses) are used herein as open-ended terms. Therefore, whenever a claim uses any form of "comprising" or "including" (e.g., including, containing, having, etc.) in a preamble or in any type of claim statement, it should be understood that additional elements, terms, etc., may be present without exceeding the scope of the corresponding claim or statement. As used herein, when the phrase "at least" is used as a transitional term, for example, in the preamble of a claim, it is as open-ended as the terms "comprising" and "including". The term "and / or", when used, for example, in the form of A, B, and / or C, refers to any combination or subset of A, B, and C, such as (1) A alone, (2) B alone, (3) C alone, (4) A and B, (5) A and C, (6) B and C, or (7) A and B and C. As used herein in the context of describing structures, components, items, objects, and / or things, the phrase "at least one of A and B" is intended to refer to any of the following implementations: (1) at least one A, (2) at least one B, or (3) at least one A and at least one B. Similarly, as used herein in the context of describing structures, components, items, objects, and / or things, the phrase "at least one of A or B" is intended to refer to any of the following implementations: (1) at least one A, (2) at least one B, or (3) at least one A and at least one B. As used herein in the context of describing the conduct or execution of processes, instructions, actions, activities, and / or steps, the phrase "at least one of A and B" is intended to refer to any of the following implementations: (1) at least one A, (2) at least one B, or (3) at least one A and at least one B. Similarly, as used herein in the context of describing the conduct or execution of processes, instructions, actions, activities and / or steps, the phrase “at least one of A or B” is intended to refer to any of the following implementations: (1) at least one A, (2) at least one B, or (3) at least one A and at least one B.

[0053] As used herein, singular references (e.g., “a,” “an,” “first,” “second,” etc.) do not exclude plurals. As used herein, the term “a” or “an” refers to one or more of those objects. The terms “a” (or “an”), “one or more,” and “at least one” are used interchangeably herein. Furthermore, although individually listed, multiple means, elements, or methods may be performed by, for example, the same entity or object. Additionally, although individual features may be included in different examples or claims, these may be combined, and inclusion in different examples or claims does not imply that the combination of features is impractical and / or disadvantageous.

[0054] As used herein, unless otherwise stated, the term "above" describes the relationship of two parts relative to the Earth. The first part is above the second part if at least one portion of the second part lies between the Earth and the first part. Similarly, as used herein, the first part is "below" the second part when the first part is closer to the Earth than the second part. As stated above, the first part can be above or below the second part, having one or more of the following: other parts between them, no other parts between them, the first and second parts in contact, or the first and second parts not in direct contact with each other.

[0055] As used in this application, a statement that any part (e.g., layer, membrane, region, area, or plate) is in any way (e.g., positioned, located, disposed on, or formed on, etc.) on another part indicates that the referred part is in contact with other parts, or that the referred part is above other parts, having one or more intermediate parts located therebetween.

[0056] As used herein, unless otherwise indicated, a connection reference (e.g., attachment, coupling, connection, and joining) may include intermediate components between elements referred to by the connection reference and / or relative movement between those elements. Therefore, a connection reference does not necessarily imply that two elements are directly connected and / or fixed to each other. As used herein, the statement that any part is in “contact” with another part is defined to mean that there is no intermediate part between the two parts.

[0057] Unless otherwise specifically stated, descriptors such as “first,” “second,” and “third” as used herein do not imply or otherwise indicate priority, physical order, arrangement in a list, and / or any sorting, but are merely used as labels and / or arbitrary names to distinguish elements for the purpose of understanding the disclosed examples. In some examples, the descriptor “first” may be used to refer to an element in the detailed description, while different descriptors (such as “second” or “third”) may be used in the claims to refer to the same element. In such cases, it should be understood that such descriptors are only used to clearly identify those elements that may, for example, otherwise share the same name.

[0058] As used herein throughout the specification and claims, approximate language is applied to modify any quantitative expression that may allow for variation without altering its underlying function. Therefore, values ​​modified by one or more terms such as “about,” “approximate,” and “substantially” are not limited to specified exact values. In at least some cases, approximate language may correspond to the precision of the instrument used to measure the value, or the precision of the method or machine used to construct or manufacture the part and / or system. For example, approximate language may refer to a margin of ten percent.

[0059] The terms "front" and "rear" refer to relative positions within a gas turbine engine, pump, or carrier, and to the normal operating posture of the gas turbine engine, pump, or carrier. For example, regarding a gas turbine engine, "front" refers to the position closer to the engine inlet, while "rear" refers to the position closer to the engine nozzle or exhaust port. Further, regarding a pump, "front" refers to the position closer to the pump inlet, while "rear" refers to the position closer to the end of the pump opposite the inlet.

[0060] The terms "upstream" and "downstream" refer to the relative directions of flow within a path. For example, relative to fluid flow, "upstream" refers to the direction from which the fluid flows, while "downstream" refers to the direction from which the fluid flows.

[0061] As used herein, the phrase “communication”, including its variations, includes direct communication and / or indirect communication via one or more intermediate components, and does not require direct physical (e.g., wired) communication and / or constant communication, but additionally includes selective communication at periodic intervals, scheduled intervals, non-periodic intervals, and / or one-off events.

[0062] As used herein, “processor circuitry” is defined to include (i) one or more dedicated circuits configured to perform a specific operation and comprising one or more semiconductor-based logic devices (e.g., electrical hardware implemented by one or more transistors), and / or (ii) one or more general-purpose semiconductor-based circuits programmed with instructions to perform a specific operation and comprising one or more semiconductor-based logic devices (e.g., electrical hardware implemented by one or more transistors). Examples of processor circuitry include programmable microprocessors, field-programmable gate arrays (FPGAs) capable of being instantiated with instructions, central processing units (CPUs), graphics processing units (GPUs), digital signal processors (DSPs), XPUs, or microcontrollers and integrated circuits such as application-specific integrated circuits (ASICs). For example, an XPU may be implemented by a heterogeneous computing system comprising multiple types of processor circuitry (e.g., one or more FPGAs, one or more CPUs, one or more GPUs, one or more DSPs, etc., and / or combinations thereof) and an application programming interface (API) that can assign computational tasks to any one(s) of the multiple types of processing circuitry best suited to perform the computational tasks.

[0063] As used herein, in the context of describing the position and / or orientation of a first object relative to a second object, the term "substantially orthogonal" includes the term orthogonal, and more broadly includes the meaning that the first object is positioned and / or oriented relative to the second object at an absolute angle not exceeding five degrees (5°) to the orthogonality. For example, a first axis substantially orthogonal to a second axis is positioned and / or oriented relative to the second axis at an absolute angle not exceeding five degrees (5°) to the orthogonality.

[0064] As used herein, "radially" is used to express one or more points along a radial vector that originates from the central axis of the rotating body and points perpendicularly outward from the central axis. In some examples, two gears are referred to as radially connected or coupled, meaning that the two gears are physically in contact with each other at one or more points along the outer edge surface of the gear's circumference via interlocking teeth. In some examples, two pulleys are referred to as radially connected or coupled, meaning that the two pulleys are physically in contact with the drive belt at one or more points along the outer edge surface of the pulley's circumference.

[0065] Centrifugal fluid pumps move fluid through a system by converting the rotational kinetic energy of an impeller into the hydrodynamic energy of the flowing fluid. In other words, the angular velocity of the impeller is proportional to the flow rate of the fluid leaving the pump. The impeller is supplied with a change in rotational kinetic energy from an electric motor, which applies mechanical work to the impeller shaft, which is connected to the rotor of the motor. The rotor is supplied with a change in mechanical work (i.e., mechanical power) over a period of time from the stator in the electric motor, which applies an electromagnetic force to the rotor in the form of torque. If the motor supplies a constant amount of electrical energy to the stator, the rotor will supply a constant amount of mechanical energy to the impeller. In this case, the mechanical power supplied to the pump by the motor will be equal to the quotient of the rotational kinetic energy and the time of power supply. In rotating systems (such as centrifugal fluid pumps), the mechanical power of the impeller is equal to the product of torque and angular velocity. If the rotor of the electric motor and the impeller shaft of the centrifugal fluid pump are axially connected (e.g., via a magnetic coupling), the rotor's torque and angular velocity will be transmitted to the impeller via the connecting shaft and will have the same value.

[0066] In some examples of fluid pump systems, the motor shaft (e.g., rotor) can be axially coupled to the impeller shaft via a magnetic coupling. The magnetic coupling transmits torque between the two shafts without physical contact. In some examples, the magnetic coupling can take the form of an inner hub and an outer hub, with the inner hub secured to a first shaft (e.g., impeller shaft) and the outer hub secured to a second shaft (e.g., rotor shaft). In the example outer hub, a series of magnets (e.g., bar magnets) are positioned to surround the example inner hub, each magnet having an opposite charge to the preceding magnet in the series. In the inner hub, a similar series of magnets is positioned about the axis of rotation of the first shaft. In some examples, the outer and inner hubs have the same number of magnets. Because magnets with opposite charges attract each other via a magnetic field, rotation of the outer hub around the inner hub causes the inner hub to rotate at the same rate. In other words, the example inner and outer hubs are rotatably interlocked. This type of magnetic coupling can be called a coaxial magnetic coupling. Because there is no physical contact between the inner and outer hubs of the coaxial magnetic coupling, the containment barrier can be fastened to the housing surrounding the inner hub, preventing fluid from flowing from the inner hub side to the outer hub side.

[0067] Example aircraft and engines that can implement the examples disclosed herein

[0068] In the accompanying drawings disclosed herein, the same numerals are used throughout the drawings to indicate the same elements. Referring now to the drawings, Figure 1 This is a side view of one embodiment of the aircraft 10. As shown, in several embodiments, the aircraft 10 includes a fuselage 12 and a pair of wings 14 (one shown), extending outward from the fuselage 12. In the illustrated embodiment, a gas turbine engine 100 is supported on each wing 14 to propel the aircraft through the air during flight. Additionally, as shown, the aircraft 10 includes a vertical stabilizer 16 and a pair of horizontal stabilizers 18 (one shown). However, in alternative embodiments, the aircraft 10 may include any other suitable configuration, such as any other suitable number or type of engines.

[0069] Furthermore, the aircraft 10 may include a thermal management system 200 for transferring heat between fluids supporting the operation of the aircraft 10. More specifically, the aircraft 10 may include one or more accessory systems configured to support the operation of the aircraft 10. For example, in some embodiments, such accessory systems include a lubrication system for lubricating components of the engine 100, a cooling system for supplying cooling air to components of the engine 100, an environmental control system for supplying cooled air to the cockpit of the aircraft 10, and so on. In this embodiment, the thermal management system 200 is configured to transfer heat from one or more other fluids supporting the operation of the aircraft 10 (e.g., fuel supplied to the engine 100) to one or more other fluids supporting the operation of the aircraft 10 (e.g., oil in the lubrication system, air in the cooling system and / or air in the environmental control system), and / or transfer heat from one or more fluids supporting the operation of the aircraft 10 (e.g., oil in the lubrication system, air in the cooling system and / or air in the environmental control system) to one or more other fluids supporting the operation of the aircraft 10 (e.g., fuel supplied to the engine 100). However, in alternative embodiments, the thermal management system 200 may be configured to transfer heat between any other suitable fluids supporting the operation of the aircraft 10.

[0070] The above description and Figure 1 The configuration of the aircraft 10 shown is provided only to place the subject matter in an exemplary field of use. Therefore, the subject matter can be readily adapted to any type of aircraft and / or any other suitable heat transfer application.

[0071] Figure 2 This is a schematic cross-sectional view of one embodiment of a gas turbine engine 100. In the illustrated embodiment, the engine 100 is configured as a high-bypass turbofan engine. However, in alternative embodiments, the engine 100 may be configured as a propeller fan engine, a turbojet engine, a turboprop engine, a turboshaft gas turbine engine, or any other suitable type of gas turbine engine.

[0072] Generally, the engine 100 extends along an axial centerline 102 and includes a fan 104, a low-pressure (LP) spool 106, and a high-pressure (HP) spool 108, all at least partially enclosed by an annular nacelle 110. More specifically, the fan 104 may include a fan rotor 112 and a plurality of fan blades 114 (one shown) coupled to the fan rotor 112. In this respect, the fan blades 114 are circumferentially spaced and extend radially outward from the fan rotor 112. Furthermore, the LP and HP spools 106, 108 are positioned downstream of the fan 104 along the axial centerline 102. As shown, the LP spool 106 is rotatably coupled to the fan rotor 112, thereby allowing the LP spool 106 to rotate the fan blades 114. Additionally, a plurality of outlet guide vanes or struts 116 are circumferentially spaced from each other and extend radially between the housing 118 surrounding the LP rotor 106 and the HP rotor 108 and the nacelle 110. Therefore, the strut 116 supports the nacelle 110 relative to the outer shell 118, such that the outer shell 118 and the nacelle 110 define a bypass airflow passage 120 located therebetween.

[0073] The housing 118 generally surrounds or encloses the compressor section 122, combustion section 124, turbine section 126, and exhaust section 128 in a series flow sequence. In some examples, the compressor section 122 may include a low-pressure (LP) compressor 130 of LP spool 106 and a high-pressure (HP) compressor 132 of HP spool 108, with the HP compressor 132 positioned downstream of the LP compressor 130 along an axial centerline 102. Each compressor 130, 132 may further include one or more rows of stator blades 134 interleaved with one or more rows of compressor rotor blades 136. Thus, the compressors 130, 132 define a compressed air flow path 133 extending therethrough. Furthermore, in some examples, the turbine section 126 includes a high-pressure (HP) turbine 138 of HP spool 108 and a low-pressure (LP) turbine 140 of LP spool 106, with the LP turbine 140 positioned downstream of the HP turbine 138 along an axial centerline 102. Each turbine 138, 140 may further include one or more rows of stator blades 142 that are interleaved with one or more rows of turbine rotor blades 144.

[0074] Additionally, the LP spool 106 includes a low-pressure (LP) spool 146, while the HP spool 108 includes a high-pressure (HP) spool 148, which is positioned concentrically around the LP spool 146. In this embodiment, the HP spool 148 is rotatably coupled to the turbine rotor blades 144 of the HP turbine 138 and the compressor rotor blades 136 of the HP compressor 132, such that rotation of the turbine rotor blades 144 of the HP turbine 138 rotatably drives the compressor rotor blades 136 of the HP compressor 132. As shown, the LP spool 146 is directly coupled to the turbine rotor blades 144 of the LP turbine 140 and the compressor rotor blades 136 of the LP compressor 130. Furthermore, the LP spool 146 is coupled to the fan 104 via a gearbox 150. In this respect, rotation of the turbine rotor blades 144 of the LP turbine 140 rotatably drives the compressor rotor blades 136 of the LP compressor 130 and the fan blades 114.

[0075] In some examples, engine 100 can generate thrust to propel the aircraft. More specifically, during operation, air (indicated by arrow 152) enters the inlet section 154 of engine 100. Fan 104 supplies a first portion of air 152 to bypass airflow passage 120 (indicated by arrow 156) and a second portion of air 152 to compressor section 122 (indicated by arrow 158). The second portion 158 of air 152 first flows through LP compressor 130, where compressor rotor blades 136 progressively compress the second portion 158 of air 152. Next, the second portion 158 of air 152 flows through HP compressor 132, where compressor rotor blades 136 continue to progressively compress the second portion 158 of air 152. The compressed second portion 158 of air 152 is then delivered to combustion section 124. In combustion section 124, a second portion 158 of air 152 mixes with fuel and burns to generate high-temperature, high-pressure combustion gas 160. The combustion gas 160 then flows through an HP turbine 138, from which turbine rotor blades 144 extract a first portion of kinetic and / or thermal energy. This energy extraction causes the HP shaft 148 to rotate, thereby driving the HP compressor 132. The combustion gas 160 then flows through an LP turbine 140, from which turbine rotor blades 144 extract a second portion of kinetic and / or thermal energy. This energy extraction causes the LP shaft 146 to rotate, thereby driving the LP compressor 130 and fan 104 via gearbox 150. The combustion gas 160 then exits the engine 100 through exhaust section 128.

[0076] As described above, the aircraft 10 may include a thermal management system 200 for transferring heat between fluids supporting the operation of the aircraft 10. In this regard, the thermal management system 200 may be located within the engine 100. For example, as Figure 2 As shown, the thermal management system 200 is located within the housing 118 of the engine 100. However, in alternative examples, the thermal management system 200 may be located at any other suitable location within the engine 100.

[0077] Furthermore, in some examples, engine 100 defines a third flow path 170. Generally, the third flow path 170 extends from the compressed air flow path 133 defined by compressor section 122 to a bypass airflow passage 120. In this respect, the third flow path 170 allows a portion of the compressed air 158 from compressor section 122 to bypass combustion section 124. More specifically, in some examples, the third flow path 170 may define a concentric or non-concentric passage relative to the compressed air flow path 170 downstream of one or more of compressors 130, 132, or fan 104. The third flow path 170 may be configured to selectively remove a portion of the compressed air 158 from the compressed air flow path 170 via one or more variable guide vanes, nozzles, or other actuable flow control structures. Additionally, as will be described below, in some embodiments, thermal management system 200 may transfer heat to the air flowing through the third flow path 170. However, the pressure and / or flow rate of the fluid within the thermal management system 200 (e.g., a heat exchange fluid, such as a supercritical fluid (e.g., supercritical carbon dioxide (sCO2) etc.)) limits the rate at which heat energy can be transferred between the air and the heat exchange fluid. Additionally, it is advantageous for the thermal management system 200 to generate pressure and / or flow rate using components (e.g., the pump system) that minimize and / or otherwise reduce the physical size of the thermal management system 200 and / or the components included therein (e.g., the pump system). Furthermore, the thermal management system 200 can ensure that the heat exchange fluid is free of contaminants during heat energy transfer.

[0078] The above description and Figure 2 The construction of the gas turbine engine 100 shown is provided only to place the subject matter in an exemplary field of use. Therefore, the subject matter can be readily adapted to any type of gas turbine engine construction, including other types of aerospace-based gas turbine engines, marine-based gas turbine engines, and / or land-based / industrial gas turbine engines.

[0079] Example thermal management systems that can be implemented using the examples disclosed herein

[0080] Figure 3This is a schematic diagram of an example embodiment of a thermal management system 200 for transferring heat between fluids. Generally, it will be described above and... Figure 1 and 2 The thermal management system 200 is discussed in the context of the aircraft 10 and gas turbine engine 100 shown. However, the disclosed thermal management system 200 can be implemented in any aircraft and / or any gas turbine engine with any other suitable construction.

[0081] As shown in the figure, the thermal management system 200 includes a heat transfer bus 202. Specifically, in several examples, the heat transfer bus 202 is configured as one or more fluid conduits through which a fluid (e.g., a heat exchange fluid) flows. As described below, the heat exchange fluid flows through various heat exchangers, such that heat is added to and / or removed from the heat exchange fluid. In this respect, the heat exchange fluid can be any suitable fluid, such as supercritical carbon dioxide. Furthermore, in this example, the thermal management system 200 includes a pump 204 configured to pump the heat exchange fluid through the heat transfer bus 202.

[0082] Additionally, the thermal management system 200 includes one or more heat source heat exchangers 206 arranged along the heat transfer bus 202. More specifically, the heat source heat exchangers 206 are fluidly coupled to the heat transfer bus 202, such that a heat exchange fluid flows through the heat source heat exchangers 206. In this respect, the heat source heat exchangers 206 are configured to transfer heat from the fluid supporting the operation of the aircraft 10 to the heat exchange fluid, thereby cooling the fluid supporting the operation of the aircraft 10. Thus, the heat source heat exchangers 206 add heat to the heat exchange fluid. Although Figure 3 Two heat source heat exchangers 206 are shown, but the thermal management system 200 may include a single heat source heat exchanger 206 or three or more heat source heat exchangers 206.

[0083] The heat source heat exchanger 206 can correspond to any suitable heat exchanger that cools the fluid supporting the operation of the aircraft 10. For example, in one embodiment, at least one of the heat exchangers 206 is a heat exchanger for the lubrication system of the engine 100. In this example, the heat exchanger 206 transfers heat from the oil that lubricates the engine 100 to the heat transfer fluid. In another example, at least one of the heat exchangers 206 is a heat exchanger for the cooling system of the engine 100. In this example, the heat exchanger 206 transfers heat from the cooling air discharged from the compressor section 122 (or compressor exhaust chamber) of the engine 100 to the heat transfer fluid. However, in alternative examples, the heat source heat exchanger 206 can correspond to any other suitable heat exchanger that cools the fluid supporting the operation of the aircraft 10.

[0084] Furthermore, the thermal management system 200 includes a plurality of radiator heat exchangers 208 arranged along a heat transfer bus 202. More specifically, the radiator heat exchangers 208 are fluidly connected to the heat transfer bus 202, such that a heat exchange fluid flows through the radiator heat exchangers 208. In this respect, the radiator heat exchangers 208 are configured to transfer heat from the heat exchange fluid to other fluids supporting the operation of the aircraft 10, thereby heating the other fluids supporting the operation of the aircraft 10. Thus, the radiator heat exchangers 208 remove heat from the heat exchange fluid. Although Figure 3 Two radiator heat exchangers 208 are shown, but the thermal management system 200 may include three or more radiator heat exchangers 208.

[0085] The radiator heat exchanger 208 can correspond to any suitable heat exchanger that heats the fluid supporting the operation of the aircraft 10. For example, at least one of the heat exchangers 208 is a heat exchanger for the fuel system of the engine 100. In this example, the fuel system heat exchanger 208 transfers heat from the heat transfer fluid to the fuel supplied to the engine 100. In another embodiment, at least one of the heat exchangers 208 is a heat exchanger that contacts the air 156 flowing through the bypass airflow passage 120 of the engine 100. In this example, the heat exchanger 208 transfers heat from the heat transfer fluid to the air 156 flowing through the bypass airflow passage 120.

[0086] In several examples, one or more heat exchangers 208 are configured to transfer heat to the air flowing through the third flow path 170. In this example, the heat exchanger 208 comes into contact with the airflow flowing through the third flow path 170. Therefore, heat from the heat exchange fluid flowing through the heat transfer bus 202 can be transferred to the airflow through the third flow path 170. Using the third flow path 170 as a radiator for the thermal management system 200 provides one or more technical advantages. For example, the third flow path 170 provides greater cooling than other bleed air sources because a larger volume of air flows through it compared to other bleed air flow paths. Furthermore, the air flowing through the third flow path 170 is colder than the air flowing through other bleed air flow paths and compressor bleed air. Additionally, the air in the third flow path 170 is pressurized, allowing the heat exchanger 208 to be smaller than heat exchangers relying on other radiators within the engine. Furthermore, in embodiments where engine 100 is non-piped, using a third flow path 170 as a radiator does not increase drag on engine 100, unlike using ambient air (e.g., a heat exchanger in contact with air flowing around engine 100). However, in alternative embodiments, radiator heat exchanger 208 may correspond to any other suitable heat exchanger that heats the fluid supporting the operation of aircraft 10.

[0087] Furthermore, in several embodiments, the thermal management system 200 includes one or more bypass conduits 210. Specifically, as shown, each bypass conduit 210 is fluidly coupled to the heat transfer bus 202, such that the bypass conduit 210 allows at least a portion of the heat exchange fluid to bypass one of the heat exchangers 206, 208. In some examples, the heat exchange fluid bypasses one or more of the heat exchangers 206, 208 to regulate the temperature of the heat exchange fluid within the heat transfer bus 202. The flow of the example heat exchange fluid through the bypass conduit 210 is controlled to regulate the pressure of the heat exchange fluid within the heat transfer bus 202. Figure 3 In the example shown, each heat exchanger 206, 208 has a corresponding bypass conduit 210. However, in an alternative embodiment, any number of heat exchangers 206, 208 may have corresponding bypass conduits 210, as long as at least one bypass conduit 210 is present.

[0088] Additionally, in several examples, the thermal management system 200 includes one or more heat source valves 212 and one or more radiator valves 214. Generally, each heat source valve 212 is configured to control the flow of heat exchange fluid through a bypass conduit 210 that bypasses the heat source heat exchanger 206. Similarly, each radiator valve 214 is configured to control the flow of heat exchange fluid through a bypass conduit 210 that bypasses the radiator heat exchanger 208. In this respect, each valve 212, 214 is fluidly coupled to the heat transfer bus 202 and the corresponding bypass conduit 210. Thus, each valve 212, 214 can move between fully and / or partially open and / or closed positions to selectively block the heat exchange flow through its corresponding bypass conduit 210.

[0089] Based on the pressure of the heat exchange fluid within the heat transfer bus 202, control valves 212 and 214. More specifically, as indicated above, in certain circumstances, the pressure of the heat exchange fluid flowing through the heat transfer bus 202 may fall outside the desired pressure range. When the pressure of the heat exchange fluid is too high, the thermal management system 200 can induce accelerated wear. In this regard, when the pressure of the heat exchange fluid within the heat transfer bus 202 exceeds a maximum pressure value or otherwise increases to a pressure value, one or more heat source valves 212 open. In this case, at least a portion of the heat exchange fluid flows through the bypass conduit 210 instead of the heat source heat exchanger 206. Therefore, less heat is added to the heat exchange fluid via the heat source heat exchanger 206, thereby lowering the temperature and thus reducing the fluid pressure. In several embodiments, the maximum pressure value is between 3800 and 4000 pounds per square inch or less. In some embodiments, the maximum pressure value is between 2700 and 2900 pounds per square inch, such as 2800 pounds per square inch. In other embodiments, the maximum pressure value is between 1300 and 1500 pounds per square inch, such as 1400 pounds per square inch. This maximum pressure value largely prevents the thermal management system 200 from inducing accelerated wear.

[0090] In some examples, the maximum pressure value is set before and / or during operation based on parameters associated with the thermal management system 200 (e.g., materials used, pump 204 design, aircraft 10 design, gas turbine engine 100 design, heat exchange fluid, etc.). The example maximum pressure value can be adjusted relative to the pressure capacity of the heat transfer bus 202, pump 204, heat exchangers 206, 208, bypass duct 210, and / or valves 212, 214. Some examples of the pump 204 architecture affecting the example maximum pressure capacity are described in more detail below.

[0091] Conversely, when the pressure of the heat exchange fluid is too low, pump 204 may experience operability problems and increased wear. Therefore, when the pressure of the heat exchange fluid within the heat transfer bus falls below a minimum pressure value or is otherwise reduced, one or more radiator valves 214 open. In this situation, at least a portion of the heat exchange fluid flows through bypass conduit 210 instead of radiator heat exchanger 208. Consequently, less heat is removed from the heat exchange fluid via radiator heat exchanger 208, increasing the temperature and thus the fluid pressure. In several embodiments, the minimum pressure value is 1070 psi or more. In some embodiments, the minimum pressure value is between 1150 and 1350 psi, such as 1250 psi. In other embodiments, the minimum pressure value is between 2400 and 2600 psi, such as 2500 psi. This minimum pressure value is generally used when the heat exchange fluid is in a supercritical state (e.g., when the heat exchange fluid is carbon dioxide).

[0092] Therefore, the thermal management system 200 can be configured to operate such that the pressure of the heat transfer fluid is maintained within a range extending between a minimum pressure value and a maximum pressure value. In some examples, the range extends from 1070 psi to 4000 psi. Specifically, in one example, the range extends from 1250 psi to 1400 psi. In another embodiment, the range extends from 2500 psi to 2800 psi.

[0093] Therefore, when the heat load placed on the thermal management system 200 changes, the operation of pump 204 and valves 212, 214 allows the exposed thermal management system 200 to maintain the pressure of the heat exchange fluid within the heat transfer bus 202 within a specific range of values.

[0094] Furthermore, the example pump 204 drives the heat exchange fluid to flow through the thermal management system 200. In some examples, the thermal management system 200 includes one or more pumps 204, depending on the desired flow rate of the heat exchange fluid in the heat transfer bus 202, the delta pressure across the pump 204, and / or kinetic energy loss. For example, the pump 204 may increase the output head to accelerate the flow of the heat exchange fluid to a first flow rate. As the heat exchange fluid crosses the heat transfer bus 202, the sample kinetic energy of the heat exchange fluid is dissipated due to friction, temperature changes, etc. Due to kinetic energy loss, the heat exchange fluid decelerates to a second flow rate at some point upstream of the pump 204. If the sample second flow rate is lower than the desired operating flow rate of the heat exchange fluid, the pump 204 may have a different architecture with a higher output first flow rate, or one or more additional pumps 204 may be included in the thermal management system 200. Variations of the example pump 204 architecture are described in more detail below.

[0095] Figure 4 An example heat transfer bus pump 400 is shown (e.g., magnetically driven pump, hermetic electric pump, fluid pump, sCO2 pump, etc.). Figure 3 Pump 204, etc.). Figure 4 In the example shown, the heat transfer bus pump 400 drives the fluid (e.g., a heat exchange fluid, such as CO2) through a connection to a flow line (e.g., Figure 3 One or more fluid conduits 402 (heat transfer bus 202). Specifically, fluid flows through inlet pipe 404 and encounters impeller 406 (e.g., compressor impeller), which rotates to drive fluid through compressor collector 408 (e.g., volute), which is fluidly coupled to fluid conduit 402. Furthermore, fluid conduit 402 can supply fluid to one or more heat exchangers (e.g., heat transfer bus 202). Figure 3 (Heat source exchanger 206 and / or radiator exchanger 208). Therefore, the heat transfer bus pump 400 can pump fluid to manage and... Figure 1 Aircraft 10 Figure 2 The thermal energy of the working fluid associated with the gas turbine engine 100 and / or any other suitable system.

[0096] exist Figure 4 In the example shown, the heat transfer bus pump 400 includes a motor 410, which is positioned within a motor housing 412. As discussed in further detail below, the motor 410 indirectly drives the rotation of the impeller 406. Figure 4 In this configuration, motor 410 is an induction motor, operably connected to a variable frequency drive (VFD) (not shown) via a feedthrough connector 414, which is connected to the motor housing 412. The VFD can be operably connected to control circuitry that controls the rotational speed of motor 410, such as Full Authority Digital Engine Control (FADEC) (not shown). For example, the control circuitry can operate motor 410 based on the pressure and / or temperature of the fluid in fluid conduit 402 and / or heat transfer bus pump 400. In some examples, the control circuitry can operate motor 410 based on the pressure and / or temperature of the working fluid affected by the fluid. Additionally or alternatively, the control circuitry can operate motor 410 based on vibration measurements obtained via an accelerometer, which is operably connected to heat transfer bus pump 400 and / or fluid conduit 402.

[0097] exist Figure 4In this configuration, the motor housing 412 is at least partially surrounded by a cooling jacket 416 to prevent the motor 410 from overheating. The rear end of the motor housing 412 is connected to a rear bearing housing 418. The front end of the motor housing 412 is connected to an intermediate bearing housing 420 via bolts 422. Further, the intermediate bearing housing 420 is connected to a connecting housing 424 opposite the motor housing 412 via bolts 426. The connecting housing 424 is connected to a front bearing housing 428 opposite the intermediate bearing housing 420 via bolts 430. Additionally, the front bearing housing 428 is connected to a back plate 432 and a compressor collector 408 on the opposite side of the back plate 432 via bolts 434.

[0098] exist Figure 4 In the example shown, the rotor 436 of the motor 410 is fixedly coupled to the shaft 438. Therefore, the motor 410 drives the rotation of the shaft 438. The rear end of the shaft 438 is supported by a first roller bearing 440 (e.g., a first rolling element bearing), which is coupled to a rear bearing housing 418. Specifically, the first roller bearing 440 is coupled to the rear bearing housing 418 via a first bearing cup 442 and a bearing washer 444 positioned between the first roller bearing 440 and the rear bearing housing 418. Figure 4 In the example shown, a preloaded spring 446 is positioned between a first bearing cup 442 and a bearing washer 444. Similarly, the front end of shaft 438 is supported by a second roller bearing 448 (e.g., a second rolling element bearing), which is coupled to an intermediate bearing housing 420. Specifically, the second roller bearing 448 is coupled to the intermediate bearing housing 420 via a second bearing cup 449. The first roller bearing 440 and the second roller bearing 448 are filled with an oil lubricant (e.g., grease, motor oil, etc.) to reduce resistance to the rotation of shaft 438 and to reduce wear encountered by bearings 440 and 448 during shaft 438 rotation.

[0099] exist Figure 4 In the example shown, the front end of shaft 438 extends at least partially through intermediate bearing housing 420. The rear end of first magnetic coupling member 450 (e.g., concave magnetic coupling member) is positioned around the front end of shaft 438. To engage shaft 438 and first magnetic coupling member 450, retaining bolt 451 is inserted through the rear end of first magnetic coupling member 450 and the front end of shaft 438. Specifically, the width of the head 453 of retaining bolt 451 is greater than the width of the orifice 455 in first magnetic coupling member 450 through which retaining bolt 451 extends. As a result, shaft 438 drives rotation of first magnetic coupling member 450.

[0100] exist Figure 4In the example shown, the first magnetic coupling element 450 is positioned around the barrier can 452 (e.g., a shroud). To attach the barrier can 452 to the front bearing housing 428, a barrier can retainer 454 (e.g., a retainer ring) is positioned around the flange 456 of the barrier can 452 and is attached to the rear end of the front bearing housing 428 via bolts 458. Further, an O-ring 459 is positioned between the flange 456 of the barrier can 452 and the barrier can retainer 454. The barrier can 452 hermetically seals the rear end of the front bearing housing 428, thereby preventing fluid spillage. Therefore, the barrier can 452 prevents fluid from flowing through the connecting housing 424 and mixing with other fluids (such as the oil lubricant of the first roller bearing 440 and / or the second roller bearing 448), which would otherwise hinder the safe transfer of heat between the fluid and the working fluid. Additionally or alternatively, the barrier can 452 may hermetically seal the motor housing 412 to prevent the oil lubricant from mixing with and contaminating the fluid.

[0101] exist Figure 4 In the example shown, the barrier can 452 is positioned around a second magnetic coupling member 460 (e.g., a convex magnetic coupling member), which is magnetically coupled to a first magnetic coupling member 450. Specifically, the opposing magnetic poles of the first magnetic coupling member 450 and the second magnetic coupling member 460 are aligned on opposite sides of the barrier can 452 to magnetically couple the first magnetic coupling member 450 to the second magnetic coupling member 460. As a result, the first magnetic coupling member 450 and the second magnetic coupling member 460 are rotatably interlocked. Therefore, the first magnetic coupling member 450 can drive the rotation of the second magnetic coupling member 460. In some examples, the connecting housing 424 includes a vent 461 to allow fluid (e.g., hydrogen, air, etc.) to circulate in and out of the connecting housing 424. Furthermore, when the barrier can 452 generates heat due to encountering the rotating magnetic field generated by the first magnetic coupling member 450 and the second magnetic coupling member 460, the fluid can absorb the heat from the barrier can 452 to prevent the barrier can 452 from melting. In some examples, a fan drives fluid circulation through a vent 461 in the coupling housing 424. In other examples, the vent 461 is open to the atmosphere or another fluid housing, which provides fluid to absorb heat from the barrier tank 452.

[0102] exist Figure 4 In the example shown, the second magnetic coupling element 460 is coupled to the pull rod 462 via a top cap 464. The pull rod 462 extends through the front bearing housing 428 and the back plate 432 to couple to the impeller 406. Additionally, the second magnetic coupling element 460 is coupled to and / or extends from the shaft 466, which is positioned around the pull rod 462. Similarly, the shaft 466 extends through the front bearing housing 428 and the back plate 432 to couple to the impeller 406. As a result, the pull rod 462 and the shaft 466 cause the impeller 406 to rotate together with the second magnetic coupling element 460 and pump fluid.

[0103] exist Figure 4 In the example shown, the axial portion 468 of shaft 466 is supported by journal bearing assembly 470. Further, the radial portion 472 of shaft 466 is supported by thrust bearing assembly 474. For example, journal bearing assembly 470 and / or thrust bearing assembly 474 may include foil bearings. In some examples, journal bearing assembly 470 and thrust bearing assembly 474 are bolted to front bearing housing 428. Additionally or alternatively, thrust bearing assembly 474 may be coupled to one of journal bearing assemblies 470.

[0104] exist Figure 4 In the example shown, the heat transfer bus pump 400 includes a secondary flow network having an inlet 475 in a front bearing housing 428. Specifically, in the secondary flow network, fluid enters the front bearing housing 428 and flows between a radial portion 472 of the shaft 466 and a thrust bearing assembly 474. Further, in the secondary flow network, a first portion of the fluid flows around the shaft 466 and enters a compressor collector 408 between the impeller 406 and the backplate 432. A second portion of the fluid in the secondary flow network flows around the shaft 466 toward a barrier tank 452. Separation of the rear end of a second magnetic coupling 460 from the barrier tank 452 allows fluid to flow through the second magnetic coupling 460 and return via the shaft 466 toward the impeller 406. Further, the shaft 466 includes a conduit 476 that guides fluid to flow between the backplate 432 and the impeller 406, such that the fluid enters the compressor collector 408. Therefore, when the motor 410 drives the shaft 438 to rotate, the impeller 406 pumps fluid through the fluid conduit 402.

[0105] In some examples, the heat transfer bus pump 400 includes means for containing fluid. For example, the means for containing fluid may be implemented by a compressor collector 408, a front bearing housing 428, and / or a back plate 432.

[0106] In some examples, the heat transfer bus pump 400 includes means for compressing the fluid. For example, the means for compressing the fluid may be implemented by an impeller 406.

[0107] In some examples, the heat transfer bus pump 400 includes means for sealing the device it houses. For example, the means for sealing may be implemented by a barrier tank 452.

[0108] Radial coupling pump system for fluids in pressurized closed-loop systems

[0109] As referenced above Figure 4As described, some example fluid pump systems and centrifugal fluid pump systems operate with an electric motor axially aligned with an impeller (e.g., impeller 406). In such an example fluid pump, the torque and angular velocity of the motor shaft (e.g., rotor shaft 438) are directly transmitted to the impeller shaft (e.g., impeller shaft 466) and ultimately to the impeller. For example, if the electric motor (e.g., motor 410) provides 2000 watts (W) of mechanical power to the rotor shaft, and the rotor shaft rotates at an angular rate of 3600 revolutions per minute (rpm), the rotor produces a torque of 5.31 Newton-meters (Nm). In this example, since the rotor is axially aligned with and coupled to the impeller via the impeller shaft, the impeller will also have an angular velocity of 3600 rpm (378 radians per second (rad / s)) and a torque of 5.31 Nm.

[0110] In some examples, axially configured fluid pumps, such as those described above Figure 4 The heat transfer bus pump 400 (“axially coupled pump 400”) is limited by the amount of angular velocity that the impeller can convert into a fluid flow rate. An example angular velocity of the impeller is limited based on the available mechanical power supplied by the electric motor to the pump system (e.g., axially coupled pump 400). In other words, the electric motor causes a first angular velocity of the rotor shaft, which is substantially similar to (e.g., within one percent) the second angular velocity of the impeller. Therefore, the power of the electric motor limits the flow rate of the fluid leaving pump 400 (e.g., heat exchange fluids, such as supercritical fluids (e.g., supercritical carbon dioxide (sCO2)) etc.). For example, aircraft (e.g., Figure 1 On the aircraft 10) Figure 3 The thermal management system 200 may include an axially coupled pump 400 to pressurize the fluid to a first pressure (e.g., 1450 psi, 1475 psi, 1500 psi, etc.), which is associated with a first impeller angular velocity (e.g., 4800 rpm, 5000 rpm, 5200 rpm, etc.). However, the axially coupled pump 400 of the example described above may be unable to pressurize the example sCO2 to a pressure sufficient to maintain the fluid in a supercritical state due to heat loss in the example thermal management system 200. A larger and more powerful electric motor would have to be incorporated into the axially coupled pump 400, which would take up more space and add additional weight to the system. If the axially coupled pump 400 of the example described above were able to pressurize the heat exchange fluid to a second pressure (e.g., 1550 psi, 1575 psi, 1600 psi, etc.) associated with the first impeller angular velocity, the electric motor of the axially coupled pump 400 (e.g., motor 410) may need to be maintained or replaced after an initial period of operation (e.g., one year).

[0111] In the examples disclosed herein, a radially coupled pump system can utilize the same (e.g., substantially similar) motor and / or the same power output as the motor 410 of the axially coupled pump 400, while outputting a higher impeller angular velocity. In the examples disclosed herein, a radially coupled pump system can also utilize a smaller motor and / or a smaller power output, while outputting the same (e.g., substantially similar) impeller angular velocity as the motor 410 of the axially coupled pump 400. In the examples disclosed herein, a radially coupled pump system can also reduce the axial length of the pump relative to the axially coupled pump 400, thereby saving system resources (e.g., ...). Figure 3 The space in the thermal management system 200).

[0112] Figure 5 A method for pressurization systems (e.g., is shown) Figure 3 A cross-sectional view of a radially coupled pump system 500 for fluids (e.g., heat exchange fluids, such as supercritical fluids (e.g., SO2, etc.)) in a thermal management system 200. Figure 5 As shown, the radially coupled pump system 500 (“pump system 500”) includes a pump 502 and an electric motor 504. In some examples, the pump system 500 is used to pump sCO2 through an aircraft (e.g., Figure 1 The aircraft 10) and / or gas turbine engine (e.g., Figure 2 The thermal management system on the gas turbine engine 100. In some examples, the electric motor 504 of the pump system 500 includes a stator 506, a rotor 508, a radial motor bearing 510, a motor housing 512, a cooling jacket 514, a connecting housing 516, and a drive wheel 518.

[0113] Figure 5 The example motor 504 of the pump system 500 shown includes a stator 506 and a rotor 508. In some examples, the stator 506 includes a field magnet (e.g., an electromagnet or a permanent magnet) that generates a magnetic field based on a current (e.g., direct current or alternating current) passing through various electromagnets in the stator 506. The example stator 506 generates a first set of magnetic fields that apply a force (e.g., a Lorentz force) to a second set of magnetic fields generated by the rotor 508. The example rotor 508 generates the second set of magnetic fields via a permanent magnet or electromagnet. Since the stator 506 is stationary and fixed in place, this force causes the example rotor 508 to rotate and generate torque.

[0114] The example motor 504 of the pump system 500 includes a radial motor bearing 510 that supports the weight of the rotor shaft 508 and maintains the radial and / or axial alignment of the rotor 508. The example radial motor bearing 510 supports the radial load (e.g., weight) and thrust load of the rotor 508. In some examples, the radial motor bearing 510 is a rolling element bearing, such as an angular contact ball bearing, a hybrid ceramic bearing, a tapered roller bearing, a deep groove single ball bearing, a double ball bearing, a spherical bearing, etc. In some examples, the radial motor bearing 510 uses a liquid lubricant (e.g., grease, oil, etc.) to reduce friction and wear in the rotating elements of the radial motor bearing 510. In some examples, the radial motor bearing 510 uses a solid lubricant (e.g., a silver coating) to reduce friction and wear in the rotating elements of the radial motor bearing 510. In some examples, the radial motor bearing 510 is a foil bearing that uses pressurized air to form a non-contact barrier between the rotor shaft and the sleeve of the radial motor bearing 510 at sufficiently high rotational speeds. Although Figure 5 The electric motor 504 shown includes two radial motor bearings 510, but one or more radial motor bearings 510 may be used in the electric motor 504.

[0115] The example motor 504 of the pump system 500 includes a motor housing 512 to frame and / or otherwise support the stator 506, radial motor bearing 510, etc. In some examples, the motor housing 512 is additively manufactured (e.g., via direct metal laser sintering (DMLS), 3D printing, etc.) to accommodate custom geometry and construction of the stator 506, radial motor bearing 510, cooling jacket 514, etc.

[0116] Since the example stator 506 uses an electromagnet to generate eddy currents, therefore Figure 5 The example pump system 500 shown includes a cooling jacket 514 to dissipate heat generated by the stator 506 during operation. In some examples, the cooling jacket 514 is mechanically fixed to the motor housing 512 and includes cooling fins, vents, channels, etc., to transfer heat from the stator 506 to air, water, gaseous coolant, liquid coolant, etc. Figure 5 The example motor housing 512 shown is an additive manufacturing structure that includes a cooling jacket 514 as an additive manufacturing part of the motor housing 512, such that the cooling jacket 514 and the motor housing 512 are the same additive manufacturing part. Figure 5 The example cooling jacket 514 shown is manufactured in conjunction with the motor housing 512 to surround the stator 506 and transfers heat from the stator 506 to air, water, gaseous coolant, liquid coolant, etc. via cooling fins, vents, channels, etc.

[0117] The example motor 504 of the pump system 500 includes a coupling housing 516 to support the radial motor bearing 510 and / or other parts of the pump system 500. Example portions of the pump system 500 supported by the coupling housing 516 are described in more detail below. In some examples, the coupling housing 516 is manufactured separately from the motor housing 512 and is secured to the motor housing 512 via bolts, pins, interference fits, and / or adhesives. In some examples, the coupling housing 516 is additively manufactured as part of the motor housing 512, such that the coupling housing 516 and the motor housing 512 are identical additively manufactured portions.

[0118] The example electric motor 504 of the pump system 500 includes a drive wheel 518 coupled to a rotor shaft 508. Figure 5 The example drive wheel 518 of the pump system 500 shown is connected to the rotor shaft 508 via one or more bolts, resulting in a direct torque transmission from the rotor shaft 508 to the drive wheel 518. For example, if the stator 506 generates a first torque to cause the rotor 508 to rotate at a first angular velocity, the drive wheel 518 also rotates at a first angular velocity. The example drive wheel 518 is radially coupled to the driven wheel 520 to convert the first torque and first angular velocity into a second torque and second angular velocity output by the driven wheel 520.

[0119] Figure 5 The example pump 502 of the pump system 500 shown includes a driven wheel 520, a radial coupling bearing 521, a coupling shaft 522, an impeller shaft 524, a magnetic coupling element 526, an impeller 528, a radial pump bearing 530, a thrust shaft 532, a thrust bearing 534, a barrier tank 536, an outer hub 538, an inner hub 540, and a back plate 542. Figure 5 The drive wheel 518 and driven wheel 520 of the pump system 500 shown may be gears (e.g., spur gears, helical gears, double helical gears, etc.) radially connected via interlocking teeth, or pulleys radially connected via a drive belt. In some examples, the teeth of the drive wheel 518 generate a force on the teeth of the driven wheel 520. In some examples, the drive belt in contact with the drive wheel 518 generates a tension force acting on the outer surface of the driven wheel 520. The example force, tension force, and / or example first torque generated by the drive wheel 518, and the example first angular velocity when the drive wheel 518 rotates, are based on the mechanical power output of the electric motor 504.

[0120] Equation 1 below represents the instantaneous mechanical power of the driving wheel 518 and / or driven wheel 520 based on torque and angular velocity:

[0121] (Equation 1) P = τω.

[0122] In Equation 1, P is power, τ is torque, and ω is angular velocity. Due to power conservation, and because the driving wheel 518 and driven wheel 520 are radially connected via gear teeth and / or a transmission belt, the instantaneous power (P1) of the driving wheel 518 is substantially similar to the instantaneous power (P2) of the driven wheel 520 (e.g., within 1%). Therefore, assuming no energy loss between the driving wheel 518 and driven wheel 520 due to heat, vibration, bending, friction, transmission belt creep, etc. (e.g., 100% efficiency), the transmission of torque and angular velocity between the driving wheel 518 and driven wheel 520 can be expressed by the following Equation 2:

[0123] P1 = P2

[0124] (Equation 2) τ1ω1=τ2ω2.

[0125] In Equation 2, τ1 is the torque output of the drive wheel 518, ω1 is the angular velocity of the drive wheel 518, τ2 is the torque output of the driven wheel 520, and ω2 is the angular velocity of the driven wheel 520.

[0126] Example drive wheel 518 generates a first torque (τ1), and example driven wheel 520 generates a second torque (τ2). Equation 3 below is used to determine the torque output of the rotating wheels:

[0127] (Equation 3) In Equation 3, F is the tangential force generated by the driving wheel 518 and / or the driven wheel 520, L is the length from the axis of rotation of the driving wheel 518 and / or the driven wheel 520 to the point where the force (F) is applied (e.g., the radius of the driving wheel 518 and / or the driven wheel 520), and D is the diameter of the driving wheel 518 and / or the driven wheel 520. The force F generated by the driving wheel 518 is substantially similar to the force F generated by the driven wheel 520 due to Newton's third law (e.g., within 1%), with some losses due to heat, vibration, bending, friction, drive belt creep, etc. Therefore, assuming no such losses occur (e.g., 100% efficiency), Equations 2 and 3 can be combined and simplified to Equation 4 as shown below:

[0128] τ1ω1=τ2ω2

[0129]

[0130] (Equation 4)

[0131] Equation 4 can be used to determine the angular velocities of the driven wheel 520 and the impeller 528 based on the angular velocity ω1 of the driving wheel 518, the diameter D1 of the driving wheel 518, and the diameter D2 of the driven wheel 520. Therefore, if the driving wheel 518 has a larger diameter than the driven wheel 520, the impeller 528 rotates at a faster rate than the rotor shaft 508 because the impeller 528 is axially connected to the driven wheel 520 via the impeller shaft 524, the magnetic coupling element 526, etc.

[0132] exist Figure 5 In the example shown, according to Equation 4, the drive wheel 518 has a larger diameter than the driven wheel 520, so that the second angular velocity is higher than the first angular velocity. The driven wheel 520 is fixed (e.g., via one or more bolts) to the connecting shaft 522. An example radial connecting bearing 521 supports the weight generated by the connecting shaft 522 and other parts connected to the connecting shaft 522. The example connecting shaft 522 is configured such that the connecting shaft 522 is axially coupled to the impeller shaft 524 via a magnetic coupling 526. The example impeller shaft 524 is also axially coupled to the impeller 528 via one or more fasteners (e.g., bolts, rods, interference fits, etc.). Since the connecting shaft 522, the magnetic coupling 526, and the impeller shaft 524 connect the driven wheel 520 to the impeller 528, the second angular velocity of the driven wheel 520 is directly transmitted to the impeller 528. In other words, the impeller 528 and the driven wheel 520 are rotatably interlocked and rotate at the same rate.

[0133] The example pump 502 of the pump system 500 includes a radial pump bearing 530 to support the radial load generated by the impeller shaft 524. In some examples, the radial pump bearing 530 is a rolling element bearing similar to the radial motor bearing 510. Figure 5 In the example pump system 500 shown, the radial pump bearing 530 is a foil bearing. In some examples, the radial pump bearing 530 includes a spring-loaded foil liner inside the bearing sleeve. When the impeller shaft 524 begins to rotate, the example spring-loaded foil liner supports the weight of the impeller shaft 524. As the second angular velocity of the impeller shaft 524 increases, the air pressure between the impeller shaft 524 and the spring-loaded foil liner increases. As the second angular velocity continues to increase, the air pressure also increases until it pushes the spring-loaded foil liner outward from the axis of rotation. An example air gap formed in the radial pump bearing 530 between the impeller shaft 524 and the sleeve of the radial pump bearing 530 then supports the weight of the impeller shaft 524.

[0134] The example radial pump bearing 530 does not use fluid lubrication (e.g., oil lubricant) that could contaminate the heat exchange fluid. However, the example radial pump bearing 530 (e.g., foil bearing) cannot support the axial loads generated by the driven wheel 520, the connecting shaft 522, and / or the impeller shaft 524. Figure 5The example motor housing 512 and backplate 542 shown frame a thrust bearing 534 such that the thrust bearing 534 supports the thrust load generated by the impeller shaft 524. The example thrust shaft 532 is fixed to the impeller shaft 524, and / or otherwise rigidly extends from the impeller shaft 524 perpendicularly to its axis of rotation. As the impeller shaft 524 rotates and transmits axial and / or thrust loads to the thrust shaft 532, the thrust bearing 534 counteracts the axial loads from the thrust shaft 532 while allowing the impeller shaft 524 to rotate with limited (e.g., less than 1%) energy loss. Although in Figure 5 The diagram shows two thrust shafts 532 and one thrust bearing 534, but the pump system 500 may have two or more thrust shafts 532 and / or one or more thrust bearings 534. In some examples, the thrust bearing 534 may be a thrust ball bearing, a cylindrical thrust roller bearing, a tapered roller thrust bearing, a spherical roller thrust bearing, a magnetic bearing, etc.

[0135] Figure 5 The example pump 502 of the pump system 500 shown includes a magnetic coupling 526 to connect a coupling shaft 522 and an impeller shaft 524. The example magnetic coupling 526 includes an outer hub 538 and an inner hub 540, both of which include permanent magnets of alternating polarities about an axis of rotation. The example inner hub 540 is a convex component of the magnetic coupling 526 and is fitted within the outer hub 538 (e.g., a concave component). The magnetic force of the permanent magnets causes the coupling shaft 522 to transmit torque directly to the impeller shaft 524, causing the impeller shaft 524 and impeller 528 to rotate at the same second angular velocity as the driven wheel 520. The coupling shaft 522 is magnetically coupled to the impeller shaft 524 such that a gap exists between the convex and concave components. An example barrier tank 536 (e.g., barrier tank 452) is designed to fit within the gap without physically and / or magnetically interfering with the magnetic coupling 526.

[0136] Example barrier tank 536 is secured within magnetic coupling 526, coupling housing 516, and / or motor housing 512 to hermetically seal driven wheel 520, coupling shaft 522, and motor 504 away from fluid (e.g., heat exchange fluid, such as supercritical fluid (e.g., sCO2, etc.)). Example barrier tank 536 also hermetically seals example oil used as lubricant by radial motor bearing 510, drive wheel 518, driven wheel 520, and / or motor 504, preventing contamination of the heat exchange fluid. In some examples, barrier tank 536 is coupled with... Figure 4 The barrier tank 452 has the same structure, materials, design, etc. In some examples, Figure 5 Barrier tank 536 can also be with Figure 4The barrier tank 452 is secured to the coupling housing 516 and / or the motor housing 512 in the same manner, such as via flanges, barrier tank retainer rings and / or bolts.

[0137] In some examples, barrier can 536 includes an inner shell, an intermediate layer, and an outer layer. In some examples, the inner and outer layers are composed of various combinations of ceramics, polymers, or composite materials, while the intermediate layer is composed of metal electroformed onto the inner layer mandrel. Further examples of barrier can 536, including materials, structure, design, etc., are described in more detail in other parts of this document.

[0138] This document discloses a radially coupled pump system 500. Examples disclosed herein include an electric motor 504 that drives a pump 502 via a drive wheel 518 axially connected to a rotor shaft 508. Examples disclosed herein further include a driven wheel 520 radially coupled to the drive wheel 518 via a gear mechanism or belt. Examples disclosed herein further include the driven wheel 520 axially coupled to an impeller shaft 524 via a magnetic coupling 526. Examples disclosed herein further include the drive wheel 518 having a first diameter and the driven wheel 520 having a second diameter smaller than the first diameter. Therefore, examples disclosed herein further include the drive wheel 518 rotating at a first angular velocity and the driven wheel 520 rotating at a second angular velocity greater than the first angular velocity. Examples disclosed herein allow the electric motor 504 to be mounted above or below a portion of the pump 502, such that the pump system 500 is relative to an axially coupled and aligned pump system (e.g., Figure 4 The pump 400 saves space in the axial direction. The examples disclosed herein are relative to… Figure 4 Example pump 400 operates motor 504 more efficiently, increases the lifespan of motor 504, increases the power density of pump system 500, and increases the maximum angular velocity of impeller 528 because motor 504 can output less mechanical power than motor 410 to achieve the same angular velocity as impeller 406.

[0139] Figure 6 A method for pressurization systems (e.g., is shown) Figure 3 A cross-sectional view of a radially coupled pump system 600 for a fluid (e.g., a heat exchange fluid, such as a supercritical fluid (e.g., sCO2, etc.)) in a thermal management system 200. Figure 6 As shown, the radially coupled pump system 600 (“pump system 600”) includes a pump 602 and an electric motor 604. In some examples, the pump system 600 is used to pump sCO2 through an aircraft (e.g., Figure 1 The aircraft 10) and / or gas turbine engine (e.g., Figure 2The thermal management system on the gas turbine engine 100. In some examples, the electric motor 604 of the pump system 600 includes a stator 606, a rotor 608, a radial motor bearing 610, a motor housing 612, a mounting rod 613, a cooling jacket 614, and a drive wheel 618.

[0140] Figure 6 The example motor 604 of the pump system 600 shown includes a stator 606 and a rotor 608. In some examples, the stator 606 includes a field magnet (e.g., an electromagnet or a permanent magnet) that generates a magnetic field based on a current (e.g., direct current or alternating current) passing through various electromagnets in the stator 606. The example stator 606 generates a first set of magnetic fields that apply a force (e.g., a Lorentz force) to a second set of magnetic fields generated by the rotor 608. The example rotor 608 generates the second set of magnetic fields via a permanent magnet or electromagnet. Since the stator 606 is stationary and fixed in place, this force causes the example rotor 608 to rotate and generate torque.

[0141] The example stator 606 of the pump system 600 is structurally configured to be fixed in a suitable position inside the rotor 608. The example rotor 608 is designed to... Figure 5 The rotor 508 rotates at a similar first torque and first angular velocity. However, the rotor 608 encloses the stator 606, while Figure 5 The stator 506 encloses the rotor 508. Example stator 606 is secured to mounting rod 613. Example mounting rod 613 is secured to motor housing 612 via one or more bolts. Example mounting rod 613 also supports radial motor bearing 610 such that the inner sleeve of radial motor bearing 610 is statically attached to mounting rod 613.

[0142] The example electric motor 604 of the pump system 600 includes a radial motor bearing 610 that supports the weight of the rotor shaft 608 and / or drive wheel 618. The example radial motor bearing 610 also maintains the radial and / or axial alignment of the rotor 608 and / or drive wheel 618. The example radial motor bearing 610 supports the radial loads (e.g., weight) and thrust loads generated by the rotor 608. In some examples, the radial motor bearing 610 is a rolling element bearing, such as an angular contact ball bearing, a hybrid ceramic bearing, a tapered roller bearing, a deep groove single ball bearing, a double ball bearing, a spherical bearing, etc. In some examples, the radial motor bearing 610 uses a liquid lubricant (e.g., grease, oil, etc.) to reduce friction and wear in the rotating elements of the radial motor bearing 610. In some examples, the radial motor bearing 610 uses a solid lubricant (e.g., a silver coating) to reduce friction and wear in the rotating elements of the radial motor bearing 610. In some examples, the radial motor bearing 610 is a foil bearing that uses pressurized air to form a non-contact barrier between the rotor shaft and the sleeve of the radial motor bearing 610 at sufficiently high rotational speeds. Although Figure 6 The electric motor 604 shown includes two radial motor bearings 610, but one or more radial motor bearings 610 may be used in the electric motor 604.

[0143] The example motor 604 of the pump system 600 includes a motor housing 612 to frame and / or otherwise support a mounting rod 613, which in turn supports a stator 606, a radial motor bearing 510, and the like. In some examples, the motor housing 612 is additively manufactured (e.g., via direct metal laser sintering (DMLS), 3D printing, etc.) to accommodate custom geometry and construction of the mounting rod 613, stator 606, radial motor bearing 610, cooling jacket 614, rotor 608, drive wheel 618, and the like. Figure 6 The example motor housing 612 shown can be additively manufactured to include the mounting rod 613 and / or cooling sleeve 614 in the same manufacturing process. Alternatively, the motor housing 612 can be additively manufactured separately from the mounting rod 613 and / or cooling sleeve 614, such that the geometry and tolerances of the motor housing 612 can be suitably adapted to various parts of the motor 604, including the mounting rod 613 and / or cooling sleeve 614. Additionally or alternatively, the motor housing 612, mounting rod 613, and / or cooling sleeve 614 can be manufactured separately via a subtractive manufacturing method.

[0144] Since the example stator 606 uses an electromagnet to generate eddy currents, therefore Figure 6The example pump system 600 shown includes a cooling jacket 614 to dissipate heat generated by the stator 606 during operation. In some examples, the cooling jacket 614 is mechanically fixed to the stator 606 and / or mounting rod 613 and includes cooling fins, vents, channels, etc., to transfer heat from the stator 606 to air, water, gaseous coolant, liquid coolant, etc. Figure 6 The example mounting rod 613 shown may be an additive manufacturing structure that includes a cooling sleeve 614 as an additive manufacturing part of the mounting rod 613, such that the cooling sleeve 614 and the mounting rod 613 are the same additive manufacturing part. Figure 5 The example cooling jacket 614 shown can be manufactured in conjunction with the mounting rod 613, such that the stator 606 is precisely assembled around and / or connected to the cooling jacket 614. In some examples, the cooling jacket 614 is manufactured in conjunction with the stator 606 such that the cooling jacket 614 and the stator 606 are identical parts, and the cooling jacket 614 transfers heat from the stator 606 to air, water, gaseous coolant, liquid coolant, etc., via cooling fins, vents, channels, etc.

[0145] The example electric motor 604 of the pump system 600 includes a drive wheel 618 coupled to a rotor shaft 608. Figure 6 The example drive wheel 618 of the pump system 600 shown is connected to the rotor shaft 608, such that there is a direct torque transmission from the rotor shaft 608 to the drive wheel 618. For example, if the stator 606 generates a first torque to cause the rotor 608 to rotate at a first angular velocity, the drive wheel 618 also rotates at a first angular velocity. The example drive wheel 618 has a shell construction that surrounds the rotor 608 and is secured to the rotor via one or more fastening techniques (e.g., bolts, pins, interference fits, adhesives, etc.). In some examples, the drive wheel 618 is additively manufactured to include one or more components of the rotor 608 (e.g., permanent magnets). The example drive wheel 618 is radially coupled to a driven wheel 620 (e.g., via a gear mechanism or belt) to convert the first torque and first angular velocity into a second torque and second angular velocity output by the driven wheel 620.

[0146] Figure 6The example pump 602 of the pump system 600 shown includes a pump housing 615, a coupling housing 616, a driven wheel 620, a radial coupling bearing 621, a coupling shaft 622, an impeller shaft 624, a magnetic coupling element 626, an impeller 628, a radial pump bearing 630, a thrust shaft 632, a thrust bearing 634, a barrier tank 636, an outer hub 638, an inner hub 640, and a back plate 642. The example pump 602 of the pump system 600 includes a coupling housing 616 to support the radial coupling bearing 621. The example radial coupling bearing 621 supports the weight generated by the coupling shaft 622 and other parts connected to the coupling shaft 622. In some examples, the coupling housing 616 is manufactured separately from the motor housing 612 and is secured to the motor housing 612 via bolts, fasteners, adhesives, etc. In some examples, the coupling housing 616 is additively manufactured as part of the motor housing 612, such that the coupling housing 616 and the motor housing 612 are identical additively manufactured parts.

[0147] Figure 6 The pump system 600 shown has a drive wheel 618 and a driven wheel 620 that are radially connected via interlocking teeth (e.g., spur gears, helical gears, double helical gears, etc.) or a pulley that is radially connected via a drive belt. In some examples, the teeth of the drive wheel 618 generate a force on the teeth of the driven wheel 620. In some examples, the drive belt in contact with the drive wheel 618 generates a tension force acting on the outer surface of the driven wheel 620. The example force, tension force, and / or example first torque generated by the drive wheel 618, and the example first angular velocity when the drive wheel 618 rotates, are based on the mechanical power output of the electric motor 604. As described above, Equation 1 represents the instantaneous mechanical power of the drive wheel 618 and / or the driven wheel 620 based on torque and angular velocity.

[0148] Due to power conservation, and because the driving wheel 618 and driven wheel 620 are radially connected via gear teeth and / or a transmission belt, the instantaneous power (P1) of the driving wheel 618 is substantially similar to that of the driven wheel 620 (P2) (e.g., within 1%). Therefore, assuming no energy loss between the driving wheel 618 and driven wheel 620 due to heat, vibration, bending, friction, transmission belt creep, etc. (e.g., 100% efficiency), the transmission of torque and angular velocity between the driving wheel 618 and driven wheel 620 can be expressed by Equation 2 as described above.

[0149] Example drive wheel 618 generates a first torque (τ1), and example driven wheel 620 generates a second torque (τ2). As described above, Equation 3 is used to determine the torque output of the rotating wheels. The force F generated by drive wheel 618 is substantially similar to the force F generated by driven wheel 620 due to Newton's third law (e.g., within 1%), with some losses due to heat, vibration, bending, friction, and drive belt creep. Therefore, assuming no such losses occur (e.g., 100% efficiency), Equations 2 and 3 can be combined and simplified to Equation 4 as described above, and Equation 4 can be used to determine the angular velocities of driven wheel 620 and impeller 628. Therefore, if drive wheel 618 has a larger diameter than driven wheel 620, impeller 628 will rotate at a greater rate than rotor shaft 608 because impeller 628 is axially connected to driven wheel 620 via impeller shaft 624, magnetic coupling 626, etc.

[0150] exist Figure 6 In the example shown, according to Equation 4, the drive wheel 618 has a larger diameter than the driven wheel 620, so that the second angular velocity is higher than the first angular velocity. The driven wheel 620 is fixed (e.g., via one or more bolts) to the connecting shaft 622. The example connecting shaft 622 is configured such that it is axially coupled to the impeller shaft 624 via a magnetic coupling 626. The example impeller shaft 624 is also axially connected to the impeller 628 via one or more fasteners (e.g., bolts, rods, interference fits, etc.). Since the connecting shaft 622, the magnetic coupling 626, and the impeller shaft 624 connect the driven wheel 620 to the impeller 628, the second angular velocity of the driven wheel 620 is directly transmitted to the impeller 628. In other words, the impeller 628 and the driven wheel 620 are rotatably interlocked and rotate at the same rate.

[0151] Example pump 602 of pump system 600 includes a pump housing 615 to frame and / or otherwise support radial pump bearing 630 and thrust bearing 634. In some examples, pump housing 615 is additively manufactured to fit the specific construction and / or geometry of one or more radial pump bearings 630, thrust bearing 634, and / or impeller shaft 624. In some examples, pump housing 615 is additively manufactured together with coupling housing 616 and / or motor housing 612 such that pump housing 615 is an identical part of coupling housing 616 and / or motor housing 612. Figure 6 The example pump housing 615 shown is manufactured separately from the coupling housing 616 and the motor housing 612 (e.g., additive manufacturing). Figure 6 The example pump housing 615 shown is fastened to the connecting housing 616 and the motor housing 612 by one or more bolts. In some examples, the pump housing 615 is fastened to the connecting housing 616 and the motor housing 612 by one or more bolts, pins, interference fits and / or adhesives.

[0152] Example pump 602 of pump system 600 includes a radial pump bearing 630 to support radial loads generated by impeller shaft 624. In some examples, the radial pump bearing 630 is a rolling element bearing similar to the radial motor bearing 610 and / or the radial coupling bearing 621. Figure 6 In the example pump system 600 shown, the radial pump bearing 630 is a foil bearing. In some examples, the radial pump bearing 630 includes a spring-loaded foil liner inside the bearing sleeve. When the impeller shaft 624 begins to rotate, the example spring-loaded foil liner supports the weight of the impeller shaft 624. As the second angular velocity of the impeller shaft 624 increases, the air pressure between the impeller shaft 624 and the spring-loaded foil liner increases. As the second angular velocity continues to increase, the air pressure also increases to a point where the air pressure pushes the spring-loaded foil liner perpendicularly outward from the axis of rotation. An example air gap formed in the radial pump bearing 630 between the impeller shaft 624 and the sleeve of the radial pump bearing 630 then supports the weight of the impeller shaft 624.

[0153] The example radial pump bearing 630 does not use fluid lubrication (e.g., oil lubricant) that could contaminate the fluid. However, the example radial pump bearing 630 (e.g., foil bearing) cannot support the axial loads generated by the driven wheel 620, the connecting shaft 622, and / or the impeller shaft 624. Figure 6 The example pump housing 615 and back plate 642 shown frame a thrust bearing 634 such that the thrust bearing 634 supports the thrust load generated by the impeller shaft 624. The example thrust shaft 632 is fixed to the impeller shaft 624, and / or otherwise rigidly extends from the impeller shaft 624 perpendicularly to its axis of rotation. As the impeller shaft 624 rotates and transmits axial and / or thrust loads to the thrust shaft 632, the thrust bearing 634 counteracts the axial loads from the thrust shaft 632 while allowing the impeller shaft 624 to rotate with limited (e.g., less than 1%) energy loss. Although in Figure 5 The diagram shows two thrust shafts 632 and one thrust bearing 634, but the pump system 600 may have two or more thrust shafts 632 and / or one or more thrust bearings 634. In some examples, the thrust bearing 634 may be a thrust ball bearing, a cylindrical thrust roller bearing, a tapered roller thrust bearing, a spherical roller thrust bearing, a magnetic bearing, etc.

[0154] Figure 6The example pump 602 of the pump system 600 shown includes a magnetic coupling 626 to connect a coupling shaft 622 and an impeller shaft 624. The example magnetic coupling 626 includes an outer hub 638 and an inner hub 640, both of which include permanent magnets of alternating polarities about an axis of rotation. The example inner hub 640 is a convex component of the magnetic coupling 626 and is fitted within the outer hub 638 (e.g., a concave component). The magnetic force of the permanent magnets causes the coupling shaft 622 to transmit torque directly to the impeller shaft 624, causing the impeller shaft 624 and the impeller 628 to rotate at the same second angular velocity as the driven wheel 620. The coupling shaft 622 is magnetically coupled to the impeller shaft 624 such that a gap exists between the convex and concave components. An example barrier tank 636 (e.g., barrier tank 452) is designed to fit within the gap without physically and / or magnetically interfering with the magnetic coupling 626.

[0155] Example barrier tank 636 is secured within magnetic coupling 626, coupling housing 616, and / or pump housing 615 to hermetically seal driven wheel 620, coupling shaft 622, and motor 604 away from the fluid. Example barrier tank 636 also hermetically seals example oil used as lubricant by radial motor bearing 610, drive wheel 618, driven wheel 620, and / or motor 604, preventing fluid contamination. In some examples, barrier tank 636 is coupled with… Figure 4 The barrier tank 452 has the same structure, materials, design, etc. In some examples, Figure 6 Barrier tank 636 can also be with Figure 4 The barrier tank 452 is secured to the coupling housing 616 and / or the motor housing 612 in the same manner, such as via flanges, barrier tank retainer rings and / or bolts.

[0156] In some examples, barrier can 636 includes an inner shell, an intermediate layer, and an outer layer. In some examples, the inner and outer layers are composed of various combinations of ceramics, polymers, or composite materials, while the intermediate layer is composed of metal electroformed onto the inner layer mandrel. Further examples of barrier can 636, including materials, structure, design, etc., are described in more detail in other parts of this document.

[0157] This document discloses a radially coupled pump system 600. Examples disclosed herein include an electric motor 604 having a stator 606 mounted inside a cylindrical rotor shaft 608 that rotates about the outside of the stator 606. Examples disclosed herein include a drive wheel 618 that surrounds and is fixed to the rotor 608 such that the rotor 608 directly transmits a first torque output to the drive wheel 618. Examples disclosed herein include the drive wheel 618 being radially coupled to a driven wheel 620 via a gear mechanism or belt. Examples disclosed herein further include the driven wheel 620 being axially coupled to an impeller shaft 624 via a magnetic coupling 626. Examples disclosed herein further include the drive wheel 618 having a first diameter and the driven wheel 620 having a second diameter smaller than the first diameter. Therefore, examples disclosed herein further include the drive wheel 618 rotating at a first angular velocity and the driven wheel 620 rotating at a second angular velocity greater than the first angular velocity. The examples disclosed herein allow the electric motor 604 to be mounted above or below a portion of the pump 602, such that the pump system 600 is relative to an axially coupled and aligned pump system (e.g., Figure 4 The pump 400 saves space in the axial direction. The examples disclosed herein are relative to… Figure 4 Example pump 400 operates motor 604 more efficiently, increases the lifespan of motor 604, increases the power density of pump system 600, and increases the maximum angular velocity of impeller 628 because motor 604 can output less mechanical power than motor 410 to achieve the same angular velocity as impeller 406.

[0158] Figure 7 A method for pressurization systems (e.g., is shown) Figure 3 A cross-sectional view of a radially coupled pump system 700 for a fluid (e.g., a heat exchange fluid, such as a supercritical fluid (e.g., CO2)) in a thermal management system 200. Figure 7 As shown, the radially coupled pump system 700 (“pump system 700”) includes a pump 702 and an electric motor 704. In some examples, the pump system 700 is used to pump sCO2 through an aircraft (e.g., Figure 1 The aircraft 10) and / or gas turbine engine (e.g., Figure 2 The thermal management system on the gas turbine engine 100. In some examples, the electric motor 704 of the pump system 700 includes a stator 706, a rotor 708, a radial motor bearing 710, a motor housing 712, a cooling jacket 714, a connecting housing 716, a connecting shaft 718, a connecting bolt 719, a magnetic coupling element 720, a drive wheel 722, a drive wheel axle 724, a radial drive wheel axle bearing 726, a barrier tank 728, an inner hub 730, and an outer hub 732.

[0159] Figure 7 The example motor 704 of the pump system 700 shown includes a stator 706 and a rotor 708. In some examples, the stator 706 includes a field magnet (e.g., an electromagnet or a permanent magnet) that generates a magnetic field based on a current (e.g., direct current or alternating current) passing through various electromagnets in the stator 706. The example stator 706 generates a first set of magnetic fields that apply a force (e.g., a Lorentz force) to a second set of magnetic fields generated by the rotor 708. The example rotor 708 generates the second set of magnetic fields via a permanent magnet or electromagnet. Since the stator 706 is stationary and fixed in place, this force causes the example rotor 708 to rotate and generate torque.

[0160] The example motor 704 of the pump system 700 includes a radial motor bearing 710 that supports the weight of the rotor shaft 708 and maintains the radial and / or axial alignment of the rotor 708. The example radial motor bearing 710 supports the radial load (e.g., weight) and thrust load of the rotor 708. In some examples, the radial motor bearing 710 is a rolling element bearing, such as an angular contact ball bearing, a hybrid ceramic bearing, a tapered roller bearing, a deep groove single ball bearing, a double ball bearing, a spherical bearing, etc. In some examples, the radial motor bearing 710 uses a liquid lubricant (e.g., grease, oil, etc.) to reduce friction and wear in the rotating elements of the radial motor bearing 710. In some examples, the radial motor bearing 710 uses a solid lubricant (e.g., a silver coating) to reduce friction and wear in the rotating elements of the radial motor bearing 710. In some examples, the radial motor bearing 710 is a foil bearing that uses pressurized air to form a non-contact barrier between the rotor shaft and the sleeve of the radial motor bearing 710 at sufficiently high rotational speeds. Although Figure 7 The electric motor 704 shown includes two radial motor bearings 710, but one or more radial motor bearings 710 may be used in the electric motor 704.

[0161] The example motor 704 of the pump system 700 includes a motor housing 712 to frame and / or otherwise support a stator 706, radial motor bearings 710, etc. In some examples, the motor housing 712 is additively manufactured (e.g., via direct metal laser sintering (DMLS), 3D printing, etc.) to accommodate custom geometry and construction of the stator 706, radial motor bearings 710, cooling jacket 714, etc.

[0162] Since the example stator 706 uses an electromagnet to generate eddy currents, therefore Figure 7The example pump system 700 shown includes a cooling jacket 714 to dissipate heat generated by the stator 706 during operation. In some examples, the cooling jacket 714 is mechanically fixed to the motor housing 712 and includes cooling fins, vents, channels, etc., to transfer heat from the stator 706 to air, water, gaseous coolant, liquid coolant, etc. Figure 7 The example motor housing 712 shown is an additive manufacturing structure that includes a cooling jacket 714 as an additive manufacturing part of the motor housing 712, such that the cooling jacket 714 and the motor housing 712 are the same additive manufacturing part. Figure 7 The example cooling jacket 714 shown is manufactured in conjunction with the motor housing 712 to surround the stator 706 and transfers heat from the stator 706 to air, water, gaseous coolant, liquid coolant, etc. via cooling fins, vents, channels, etc.

[0163] The example motor 704 of the pump system 700 includes a coupling housing 716 to support the drive wheel axle bearing 726, a barrier tank 728, etc. Figure 7 In the example shown, the coupling housing 716 is manufactured separately from the motor housing 712 and is secured to the motor housing 712 by one or more bolts. In some examples, the coupling housing 716 (via additive or subtractive manufacturing) is manufactured separately from the motor housing 712 and is secured to the motor housing 712 by bolts, pins, interference fits, and / or adhesives. In some examples, the coupling housing 716 is additively manufactured as part of the motor housing 712, such that the coupling housing 716 and the motor housing 712 are identical additively manufactured parts.

[0164] The example electric motor 704 of the pump system 700 includes a drive wheel 722 coupled to a rotor shaft 708. Figure 7 The example drive wheel 722 of the pump system 700 shown is connected to the rotor shaft 708 via a coupling shaft 718 and a magnetic coupling member 720, such that there is a direct torque transmission from the rotor shaft 708 to the drive wheel 722. For example, if the stator 706 generates a first torque to cause the rotor 708 to rotate at a first angular velocity, the drive wheel 722 also rotates at a first angular velocity. The example drive wheel 722 is radially coupled to the driven wheel 734 to convert the first torque and the first angular velocity into a second torque and a second angular velocity output by the driven wheel 734.

[0165] Figure 7The example motor 704 of the pump system 700 shown includes a magnetic coupling 720 to connect a coupling shaft 718 and a drive wheel shaft 724. The example coupling shaft 718 is rigidly connected to the rotor shaft 708 via coupling bolts 719 aligned with the axes of rotation of both the rotor shaft 708 and the coupling shaft 718. The example magnetic coupling 720 includes an outer hub 732 and an inner hub 730, both of which include permanent magnets of alternating polarities about the axes of rotation. The example inner hub 730 is a convex component of the magnetic coupling 720 and is fitted within the outer hub 732 (e.g., a concave component). The magnetic force of the permanent magnets causes the coupling shaft 718 to transmit torque directly to the drive wheel shaft 724, causing the drive wheel shaft 724 and the drive wheel 722 to rotate at the same second angular velocity as the rotor shaft 708. The coupling shaft 718 is magnetically coupled to the drive wheel shaft 724 such that a gap exists between the convex and concave components. Example barrier can 728 (e.g., barrier can 452) is designed to fit within the gap without physically and / or magnetically interfering with the magnetic coupling 720.

[0166] Example barrier tank 728 is secured within magnetic coupling member 720 and / or coupling housing 716 to hermetically seal motor 504 away from fluid. Example barrier tank 728 also hermetically seals the radial motor bearing 710, rotor shaft 708, and / or example oil used as lubricant by motor 704, preventing fluid contamination. In some examples, barrier tank 728 is coupled with... Figure 4 The barrier tank 452 has the same structure, materials, design, etc. In some examples, Figure 7 The barrier tank 728 can also be with Figure 4 The barrier can 452 is secured to the coupling housing 716 in the same manner, such as via flanges, barrier can retainer rings and / or bolts.

[0167] In some examples, the barrier can 728 includes an inner shell layer, an intermediate layer, and an outer layer. In some examples, the inner and outer layers are composed of various combinations of ceramics, polymers, or composite materials, while the intermediate layer is composed of metal electroformed onto the inner layer mandrel. Further examples of the barrier can 728, including materials, structure, design, etc., are described in more detail in other parts of this document.

[0168] The example electric motor 704 of the pump system 700 includes a radial drive axle bearing 726 to support the radial load generated by the drive axle 724. In some examples, the radial drive axle bearing 726 is a rolling element bearing similar to the radial motor bearing 710. Figure 7In the example pump system 700 shown, the radial drive shaft bearing 726 is a foil bearing. In some examples, the radial drive shaft bearing 726 includes a spring-loaded foil liner inside the bearing sleeve. When the drive shaft 724 begins to rotate, the example spring-loaded foil liner supports the weight of the drive shaft 724. As the initial angular velocity of the drive shaft 724, connecting shaft 718, and rotor shaft 708 increases, the air pressure between the drive shaft 724 and the spring-loaded foil liner increases. As the initial angular velocity continues to increase, the air pressure also increases to a point where the air pressure pushes the spring-loaded foil liner outward from the axis of rotation. An example air gap formed in the radial drive shaft bearing 726 between the drive shaft 724 and the sleeve of the radial drive shaft bearing 726 then supports the weight of the drive shaft 724.

[0169] The example radial drive wheel axle bearing 726 does not use fluid lubrication (e.g., oil lubricant) that could contaminate the fluid. However, the example radial drive wheel axle bearing 726 (e.g., foil bearing) cannot support the axial loads generated by the drive wheel 722 and / or drive wheel axle 724. Figure 7 In the illustrated pump system 700, the magnetic coupling 720 supports axial loads (e.g., thrust loads). In some examples, the drive shaft 724 may include one or more thrust shafts, which are fixed and / or otherwise extend radially outward from the drive shaft 724 perpendicular to its axis of rotation. In some examples, the coupling housing 716 and / or the pump housing 735 frame one or more thrust bearings that support one or more example thrust shafts that may be included together with the drive shaft 724.

[0170] Figure 7 The example pump 702 of the pump system 700 shown includes a driven wheel 734, a pump housing 735, an impeller shaft 736, an impeller 738, a radial pump bearing 740, a thrust shaft 742, and a thrust bearing 744. Figure 7 The driving wheel 722 and driven wheel 734 of the pump system 700 shown may be gears (e.g., spur gears, helical gears, double helical gears, etc.) radially connected via interlocking teeth, or pulleys radially connected via a drive belt. In some examples, the teeth of the driving wheel 722 generate a force on the teeth of the driven wheel 734. In some examples, the drive belt in contact with the driving wheel 722 generates a tension force acting on the outer surface of the driven wheel 734. The example force, tension force, and / or example first torque generated by the driving wheel 722, and the example first angular velocity when the driving wheel 722 rotates, are based on the mechanical power output of the electric motor 704. As described above, Equation 1 represents the instantaneous mechanical power of the driving wheel 722 and / or driven wheel 734 based on torque and angular velocity.

[0171] Due to power conservation, and because the drive wheel 722 and driven wheel 734 are radially connected via gear teeth and / or a transmission belt, the instantaneous power (P1) of the drive wheel 722 is substantially similar to the instantaneous power (P2) of the driven wheel 734 (e.g., within 1%). Therefore, assuming no energy loss between the drive wheel 722 and driven wheel 734 due to heat, vibration, bending, friction, transmission belt creep, etc. (e.g., 100% efficiency), the transmission of torque and angular velocity between the drive wheel 722 and driven wheel 734 can be expressed by Equation 2 as described above.

[0172] Example drive wheel 722 generates a first torque (τ1), and example driven wheel 734 generates a second torque (τ2). As described above, Equation 3 is used to determine the torque output of the rotating wheels. The force F generated by drive wheel 722 is substantially similar to the force F generated by driven wheel 734 due to Newton's third law (e.g., within 1%), with some losses due to heat, vibration, bending, friction, drive belt creep, etc. Therefore, assuming no such losses occur (e.g., 100% efficiency), Equations 2 and 3 can be combined and simplified to Equation 4 as described above, and Equation 4 can be used to determine the angular velocities of driven wheel 734 and impeller 738. Therefore, if drive wheel 722 has a larger diameter than driven wheel 734, impeller 738 will rotate at a greater rate than rotor shaft 708 because impeller 738 is axially connected to driven wheel 734 via impeller shaft 736.

[0173] exist Figure 7 In the example shown, according to Equation 4, the drive wheel 722 has a larger diameter than the driven wheel 734, so that the second angular velocity is higher than the first angular velocity. The driven wheel 734 is fixed (e.g., via one or more bolts, welds, adhesives, interference fits, etc.) to the impeller shaft 736. The example impeller shaft 736 is axially connected to the impeller 738 via one or more fasteners (e.g., bolts, rods, interference fits, etc.). Since the impeller shaft 736 connects the driven wheel 734 to the impeller 738, the second angular velocity of the driven wheel 734 is directly transmitted to the impeller 738. In other words, the impeller 738 and the driven wheel 734 are rotatably interlocked and rotate at the same rate.

[0174] The example pump 702 of the pump system 700 includes a radial pump bearing 740 to support the radial load generated by the impeller shaft 736. In some examples, the radial pump bearing 740 is a rolling element bearing similar to the radial motor bearing 710. Figure 7In the example pump system 700 shown, the radial pump bearing 740 is a foil bearing. In some examples, the radial pump bearing 740 includes a spring-loaded foil liner inside the bearing sleeve. When the impeller shaft 736 begins to rotate, the example spring-loaded foil liner supports the weight of the impeller shaft 736. As the second angular velocity of the impeller shaft 736 increases, the air pressure between the impeller shaft 736 and the spring-loaded foil liner increases. As the second angular velocity continues to increase, the air pressure also increases to a point where the air pressure pushes the spring-loaded foil liner outward from the axis of rotation. An example air gap formed in the radial pump bearing 740 between the impeller shaft 736 and the sleeve of the radial pump bearing 740 then supports the weight of the impeller shaft 736.

[0175] The example radial pump bearing 740 does not use fluid lubrication (e.g., oil lubricant) that could contaminate the fluid. However, the example radial pump bearing 740 (e.g., foil bearing) cannot support the axial loads generated by the driven wheel 734 and / or impeller shaft 736. An example pump 702 of the pump system 700 includes a thrust shaft 742 for interfacing with the thrust bearing 744. Figure 7 The example pump housing 735 and coupling housing 716 shown frame a thrust bearing 744 such that the thrust bearing 744 supports the thrust load generated by the thrust shaft 742. The example thrust shaft 742 is fixed to the impeller shaft 736 and / or otherwise rigidly extends from the impeller shaft 736 perpendicular to its axis of rotation. As the impeller shaft 736 rotates and transmits axial and / or thrust loads to the thrust shaft 742, the thrust bearing 744 counteracts the axial loads from the thrust shaft 742 while allowing the impeller shaft 736 to rotate with limited (e.g., less than 1%) energy loss. Although in Figure 7 The diagram shows two thrust shafts 742 and one thrust bearing 744, but the pump system 700 may have two or more thrust shafts 742 and / or one or more thrust bearings 744. In some examples, the thrust bearing 744 may be a thrust ball bearing, a cylindrical thrust roller bearing, a tapered roller thrust bearing, a spherical roller thrust bearing, a magnetic bearing, etc.

[0176] This document discloses a radially coupled pump system 700. Examples disclosed herein include an electric motor 704 to drive a pump 702 via a drive wheel 722, the drive wheel 722 being axially connected to an electric motor shaft 708 via a magnetic coupling 720. Examples disclosed herein further include a driven wheel 734, the driven wheel 734 being radially coupled to the drive wheel 722 via a gear mechanism or belt. Examples disclosed herein further include a driven wheel 734 axially connected to an impeller shaft 736. Examples disclosed herein further include the drive wheel 722 having a first diameter and the driven wheel 734 having a second diameter smaller than the first diameter. Therefore, examples disclosed herein further include the drive wheel 722 rotating at a first angular velocity and the driven wheel 734 rotating at a second angular velocity greater than the first angular velocity. Examples disclosed herein allow the electric motor 704 to be mounted above or below a portion of the pump 702, such that the pump system 700 is relative to an axially coupled and aligned pump system (e.g., Figure 4 The pump 400 saves space in the axial direction. The examples disclosed herein are relative to… Figure 4 Example pump 400 operates motor 704 more efficiently, increases the lifespan of motor 704, increases the power density of pump system 700, and increases the maximum angular velocity of impeller 738 because motor 704 can output less mechanical power than motor 410 to achieve the same angular velocity as impeller 406.

[0177] Figure 8 This is a flowchart illustrating an example process or operation 800, as disclosed herein, of pump system 500 ( Figure 5 ), 600 Figure 6 ), 700 Figure 7 This can be followed in the example procedure or operation 800 to transmit the bus in the thermal management system (e.g., Figure 2 The pressurized fluid (e.g., heat exchange fluid, such as a supercritical fluid (e.g., supercritical carbon dioxide (SCO2) etc.)) is in the heat transfer bus 202. Although the main reference is to the use of the heat transfer bus in the thermal management system. Figure 5-7 Operation 800 is described in terms of pumping fluids in pump systems 500, 600, and 700, but operation 800 can be used to pump fluids in any other closed-loop transport bus.

[0178] At block 802, motors 504, 604, and 704 generate a first torque and a first speed on rotor shafts 508, 608, and 708. For example, current is supplied to the electromagnets of stators 506, 606, and 706 to induce a magnetic field perpendicular to the rotational axes of rotors 508, 608, and 708. The electromagnets of stators 506, 606, and 706 are sequentially charged with current flowing in varying directions, thereby activating a change in the polarity of the magnetic field to attract the permanent magnets in rotors 508, 608, and 708. The magnetic force between the electromagnets in stators 506, 606, and 706 and the permanent magnets in rotors 508, 608, and 708 provides the first torque and the first angular velocity to rotor shafts 508, 608, and 708.

[0179] At block 804, depending on the position and / or configuration of the magnetic couplings 526, 626, 720 in the pump systems 500, 600, 700, process or operation 800 proceeds to block 806 or block 808. If the rotor shafts 508, 608, 708 and drive wheels 518, 618, 722 are connected via magnetic couplings 526, 626, 720, then process or operation 800 proceeds to block 806, wherein the rotors 508, 608, 708 directly transmit the first torque and the first angular velocity to the drive wheels 518, 618, 722 via magnetic couplings 526, 626, 720. If the rotor shafts 508, 608, 708 and the drive wheels 518, 618, 722 are not connected via magnetic couplings 526, 626, 720, then process or operation 800 proceeds to block 808, where the rotors 508, 608, 708 directly transmit the first torque and the first angular velocity to the drive wheels 518, 618, 722 via a first mechanical connection (e.g., bolts, pins, adhesives, interference fits, etc.).

[0180] At block 810, depending on the design, structure, and / or construction of the drive wheels 518, 618, 722 and the driven wheels 520, 620, 734, process or operation 800 proceeds to block 812 or block 814. If both drive wheels 518, 618, 722 and driven wheels 520, 620, 734 are radially connected gears via interlocking teeth, process or operation 800 proceeds to block 812, where the first torque and first angular velocity of the drive wheels 518, 618, 722 are converted into a second torque and a second angular velocity of the driven wheels 520, 620, 734 via the interlocking teeth. One or more teeth of the drive wheels 518, 618, 722 apply force to one or more teeth of the driven wheels 520, 620, 734. The force is transmitted to the driven wheels 520, 620, 734, generating a second torque and a second angular velocity.

[0181] At box 814, if the drive wheels 518, 618, 722 and the driven wheels 520, 620, 734 are not gears radially connected via interlocking teeth, then the first torque and first angular velocity of the drive wheels 518, 618, 722 are converted into a second torque and a second angular velocity of the driven wheels 520, 620, 734 via a belt coupling between the drive wheels 518, 618, 722 and the driven wheels 520, 620, 734. The belt is designed and / or assembled to have anti-slip contact with the drive wheels 518, 618, 722 and the driven wheels 520, 620, 734. The drive wheels 518, 618, 722 apply tension to the belt, and the tension is transmitted to the areas on the driven wheels 520, 620, 734 where the belt contacts the driven wheels 520, 620, 734. The transmission of tension generates a second torque and a second angular velocity in the driven wheels 520, 620, and 734.

[0182] At block 816, depending on the position and configuration of the magnetic couplings 526, 626, 720 in the pump systems 500, 600, 700, process or operation 800 proceeds to block 818 or block 820. If the driven wheels 520, 620, 734 and impeller shafts 524, 624, 736 are connected via magnetic couplings 526, 626, 720, process or operation 800 proceeds to block 818, wherein the driven wheels 520, 620, 734 directly transmit the second torque and second angular velocity to the impeller shafts 524, 624, 736 via magnetic couplings 526, 626, 720 and / or connecting shafts 522, 622, 718. If the driven wheels 520, 620, 734 and impeller shafts 524, 624, 736 are not connected via magnetic couplings 526, 626, 720, then process or operation 800 proceeds to block 820, where the driven wheels 520, 620, 734 directly transmit the second torque and second angular velocity to the impeller shafts 524, 624, 736 via a second mechanical connection (e.g., bolts, pins, adhesives, interference fits, etc.).

[0183] At box 822, impellers 528, 628, and 738, connected to impeller shafts 524, 624, and 736, generate fluid kinetic energy based on the rotational kinetic energy of the impellers 528, 628, and 738. Since impellers 528, 628, and 738 are axially connected and / or connected to impeller shafts 524, 624, and 736, they also rotate at a second angular velocity. The rotational kinetic energy of impellers 528, 628, and 738 is based on their second angular velocity and inertial torque. This rotational energy is converted into fluid kinetic energy based on the law of conservation of energy and the design of the impellers 528, 628, and 738.

[0184] In some examples, pump systems 500, 600, and 700 include a device for rotation. For example, the device for rotation may be... Figure 5 , 6 The motors 504, 604, and 704, stators 506, 606, and 706, and / or rotor shafts 508, 608, and 708 are implemented. In some examples, the means for rotation may include motors such as DC motors, AC motors, brushed DC motors, brushless DC motors, etc.

[0185] In some examples, pump systems 500, 600, and 700 include a device for acceleration. For example, the device for acceleration may be... Figure 5-8 Impellers 528, 628, 738 and / or impeller shafts 524, 624, 736 are implemented. In some examples, the means for adding the impeller may include an electric motor, an impeller shaft, and / or an impeller.

[0186] In some examples, pump systems 500, 600, and 700 include a device for conversion. For example, the device for conversion may be... Figure 5-7 The drive wheels 518, 618, 722 and / or driven wheels 520, 620, 734 are implemented. In some examples, the means for conversion may include gears that contact via interlocking wheel teeth or pulleys that contact the drive belt.

[0187] In some examples, pump systems 500, 600, and 700 include means for connection. For example, the means for connection may be... Figure 5-7 The magnetic coupling elements 526, 626, and 720 are implemented. In some examples, the means for connection may include a magnetic coupling element, an inner hub, an outer hub, a connecting shaft, and / or a permanent magnet.

[0188] In some examples, pump systems 500, 600, and 700 include means for framing. For example, the means for framing may be... Figure 5 , 6 The motor housings 512, 612, 712, coupling housings 516, 616, 716, and / or pump housings 615, 735 are implemented. In some examples, the device for framing may include housings, shells, support structures, etc., manufactured via additive manufacturing (e.g., binder jetting, directed energy deposition, powder bed infusion, direct metal laser sintering, etc.).

[0189] Integrated bearing system for shafts in dynamic support pump systems

[0190] Some example fluid pump systems and centrifugal fluid pump systems operate as described in the reference above. Figure 4The electric motor (e.g., motor 410) described is axially connected to the impeller (e.g., impeller 406) via the impeller shaft (e.g., impeller shaft 466). Figure 4 The example rotor shaft 438 shown is connected to the example impeller shaft 466 via a first magnetic coupling 450 and a second magnetic coupling 460. In some examples, the rotor shaft is directly connected to the impeller in the pump system without a magnetic coupling to connect the rotor shaft and the impeller shaft. In some examples, foil bearings are used to support the radial loads generated on the rotor shaft during operation of the pump system. A foil bearing is a type of air bearing that uses spring-loaded foils between the shaft and the journal liner to support the shaft at low start-up speeds. Once the shaft rotates at a sufficiently high rate (depending on the foil bearing's architecture), a working fluid (e.g., air, nitrogen, argon, etc.) is drawn into the foil bearing due to the viscous effect of the working fluid. Therefore, the working fluid pressure increases in the foil bearing, pushing the foils axially outward and supporting the radial loads generated on the shaft, resulting in a frictionless bearing without liquid lubricant. Since foil bearings do not use liquid lubricants, airtight seals (e.g., magnetic couplings) can be omitted to prevent lubricant contamination of the fluid pressurized by the pump system (e.g., heat exchange fluids, such as supercritical fluids (e.g., sCO2, etc.)).

[0191] In some examples, the foil bearings used to support the radial loads generated by the rotor shaft experience wear during pump system startup and shutdown. More specifically, the spring-loaded foils supporting the weight of the rotor shaft at lower speeds (start-up and shutdown speeds) deteriorate over time due to frictional erosion. In the examples disclosed herein, the integrated bearing system includes foil bearings, rolling element bearings, and a disengaged swashplate clutch to support the rotor shaft in the pump system. The example swashplate clutch engages the rolling element bearings before the pump system is operated and at lower operating speeds, such that the rolling element bearings support the weight of the rotor shaft (e.g., total weight and / or most of the weight) during the pump system's startup and shutdown speeds. In the examples disclosed herein, when the pump system reaches a first operating speed range (e.g., the foil bearing lift-off speed (e.g., a tangential speed of 10 to 50 m / s for the foil bearings)), the swashplate clutch disengages from the rolling element bearings, and the foil bearings support the weight of the rotor shaft. Therefore, the examples disclosed herein reduce the radial load supported by the foil bearing during the start-up and shutdown of the pump system, reduce foil bearing wear due to less frictional erosion, and increase foil bearing life (e.g., service life).

[0192] For the accompanying drawings disclosed herein, the same numbers indicate the same elements throughout the drawings. Figure 9 A method for pressurization systems (e.g., is shown) Figure 3A cross-sectional view of a pump system 900 for a fluid (e.g., a heat exchange fluid, such as a supercritical fluid (e.g., SO2)) in a thermal management system 200. In some examples, pump system A100 is used to pump SO2 through an aircraft (e.g., Figure 1 The aircraft 10) and / or gas turbine engine (e.g., Figure 2 The thermal management system on the gas turbine engine 100. For example... Figure 9 As shown, the pump system 900 includes an impeller 902, a rotor shaft 904, a rotor 905, a stator 906, a thrust bearing 908, a radial shaft 909, a first integrated bearing system 910, a first slant clutch 912, a first bearing housing 913, a first rolling element bearing 914, a first foil bearing 916, a second integrated bearing system 918, a second slant clutch 920, a second bearing housing 921, a second rolling element bearing 922, and a second foil bearing 924.

[0193] Figure 9 The example pump system 900 shown includes an impeller 902 to pressurize the system (e.g., Figure 3 The fluid (e.g., CO2) in the thermal management system 200. An example impeller 902 is a component of the pump system 900, connected to the rotor shaft 904, and rotating at the same speed as the rotor shaft 904. In some examples, the impeller 902 is the same as or similar to the impeller used in a centrifugal pump and includes blades and / or vanes to deflect the inlet fluid flow radially outward into the outlet flow line. The example impeller 902 converts the mechanical power of an electric motor (e.g., rotor shaft 904 and stator 906) into the hydrodynamic power of the fluid flow.

[0194] Figure 9The example pump system 900 shown includes a stator 906 to apply torque to a rotor 905 coupled to a rotor shaft 904. Since the example rotor 905 is connected to the rotor shaft 904 (e.g., via bolts, adhesives, interference fits, etc.), the stator 906 causes the rotor shaft 904 to rotate while the stator 906 remains stationary. The example stator 906, example rotor 905, and example rotor shaft 904 are included as parts of an electric motor familiar to those skilled in the art. In some examples, the stator 906 includes field magnets (e.g., electromagnets or permanent magnets) that generate a magnetic field based on a current (e.g., direct current or alternating current) passing through various electromagnets in the stator 906. The example stator 906 generates a first set of magnetic fields that apply a force (e.g., Lorentz force) to a second set of magnetic fields generated by the rotor 905. The example rotor 905 generates the second set of magnetic fields via permanent magnets or electromagnets. Since the example stator 906 is stationary and fixed in place, the force causes the example rotor 905 to rotate and generate torque. Because the example rotor shaft 904 is connected to the example rotor 905, the rotor shaft 904 generates the same torque and rotates at the same angular velocity as the rotor 905.

[0195] Figure 9 The example pump system 900 shown includes a thrust bearing 908 to support the thrust load (axial load) generated by the rotor shaft 904 during operation. Figure 9 The example thrust bearing 908 shown is a foil bearing, comprising spring-loaded foils and a journal liner, similar to the foil bearing architecture described above. An example rotor shaft 904 is connected to two or more radial shafts 909, which are positioned perpendicular to the axis of rotation of the rotor shaft 904. In some examples, the radial shafts 909 are connected to the rotor shaft via bolts, adhesives, interference fits, etc. Figure 9 The example pump system 900 shown includes two radial shafts 909; however, more radial shafts 909 may be connected to the rotor shaft 904. In some examples, the thrust bearing 908 includes a liner that interfaces with the radial shafts 909 and spring-loaded foils. In some examples, the radial shafts 909 are discs that are connected to the rotor shaft 904 and interact directly with the spring-loaded foils of the thrust bearing 908.

[0196] Figure 9 An example pump system 900 includes a first integrated bearing system 910 to support radial loads on the rotor shaft 904 during operation of the pump system 900. The example first integrated bearing system 910 includes a first brace clutch 912, a bearing housing 913, a first rolling element bearing 914, and a first foil bearing 916. Figure 9The example pump system 900 also includes a second integrated bearing system 918 to similarly support the radial load on the rotor shaft 904. The second integrated bearing system 918 includes a second brace clutch 920, a second rolling element bearing 922, and a second foil bearing 924. In some examples, the pump system 900 includes one integrated bearing system. In some examples, the pump system 900 includes one or more integrated bearing systems. Figure 9 The example first integrated bearing system 910 and example second integrated bearing system 918 of the example pump system 900 shown are substantially similar. Therefore, references and descriptions to the first integrated bearing system 910 (“bearing system 910”), the first swashplate clutch 912 (“swashplate clutch 912”), the first bearing housing 913 (“bearing housing 913”), the first rolling element bearing 914 (“rolling element bearing 914”), and the first foil bearing 916 (“foil bearing 916”) can also be applied to the second integrated bearing system 918, the second swashplate clutch 920, the second bearing housing 921, the second rolling element bearing 922, and the second foil bearing 924, respectively.

[0197] Figure 9 The example pump system 900 shown includes a swashplate clutch 912 to engage and disengage the rolling element bearing 914 and the foil bearing 916 during operation of the pump system 900. The example swashplate clutch 912 is a disengageable swashplate clutch, similar to a rolling element bearing, but comprising a non-rotating asymmetrical swashplate element instead of a rotating symmetrical cylinder, ball, etc. The example swashplate clutch 912 includes an inner ring and an outer ring, with the swashplate element properly positioned between the inner and outer rings. The example swashplate clutch 912 also includes a spring band to generate a preloaded spring force on the swashplate element, thereby engaging the swashplate clutch with the inner and outer rings during non-operational periods. Due to the asymmetrical figure-eight geometry of the swashplate element, frictional forces between the components of the swashplate clutch 912 cause the inner ring to rotate at the same angular velocity as the outer ring when the swashplate element rotates and weds between the outer and inner rings. When the example wedge clutch 912, its inner and outer rings rotate within a first operating speed range, the wedge element of the wedge clutch 912 remains engaged with the outer and inner rings due to the preloaded spring force and the resulting spring torque. When the example wedge clutch 912, its inner and outer rings rotate within a second operating speed range, the wedge element of the wedge clutch 912 disengages from the outer and inner rings due to centrifugal force and the resulting centrifugal torque, which cancels out and exceeds the spring torque. A further description of the example wedge clutch 912 and its operation is provided below.

[0198] Figure 9The example pump system 900 shown includes a rolling element bearing 914 to support radial loads on the rotor shaft 904 within a first operating speed range. Some examples of the first operating speed range include a first tangential speed range of the rotor shaft 904 and / or foil bearing 916 from 0 m / s to 50 m / s, a first fluid flow velocity range exiting the pump system 900 from 0 m / s to 10 m / s, etc. The example rolling element bearing 914 includes an inner ring, an outer ring, and rolling elements (e.g., balls, spheres, cylinders, etc.). The inner and outer rings of the example rolling element bearing 914 are rotatable in either direction. In some examples, the rolling element bearing 914 includes a liquid lubricant (e.g., oil, grease, etc.) to reduce friction within the rolling element bearing 914 and increase its lifespan. If the example pump system 900 uses a liquid lubricant for the rolling element bearing 914, an example oil separator may be included in the pump system 900 to help ensure that the fluid is not contaminated. Some examples of oil separators that can be used in the examples disclosed herein are described in further detail below. In some examples, the rolling element bearing 914 includes an inorganic grease (e.g., silicone grease, bentonite, polyurea, etc.) as a lubricant. Figure 9 The example rolling element bearing 914 shown uses a solid lubricant (such as a silver coating, graphite, molybdenum disulfide, etc.) to reduce friction in the rolling element bearing 914 and increase its lifespan, while eliminating the risk of fluid contamination by the liquid lubricant. The rolling element bearing 914 can be one of many rolling element bearings familiar to those skilled in the art, such as cylindrical rolling element bearings, angular contact ball bearings, hybrid ceramic bearings, tapered rolling element bearings, deep groove single ball bearings, double ball bearings, spherical ball bearings, or any combination thereof. In some examples, the rolling element bearing 914 is hermetically sealed away from the example fluid via one or more hermetically sealed seals (e.g., piston seals, epoxy seals, ceramic-metal seals, etc.). Depending on the type of rolling element bearing, the type of lubricant, and / or the effectiveness of the hermetically sealed seals, the example rolling element bearing 914 can have a lifespan of 1000 hours or longer. In some examples, the rolling element bearing 914 is hermetically sealed away from fuel, oil, air, and / or fuel via a flow path from the rolling element bearing 914. Figure 2 The heat transfer bus 202 conducts heat exchange and is cooled externally. Alternatively or additionally, an evaporative cooling system may be used to cool the example rolling element bearing 914.

[0199] Figure 9The example pump system 900 shown includes a foil bearing 916 to support radial loads on the rotor shaft 904 within a second operating speed range. Some examples of the second operating speed range include a second tangential speed range for the rotor shaft 904 and / or the foil bearing 916 from 50 m / s to 200 m / s, and a second fluid flow velocity range exiting the pump system 900 from 10 m / s to 100 m / s, etc. The example foil bearing 916 includes an inner liner, spring-loaded foils, and a journal liner as described above. The inner liner and journal liner of the example foil bearing 916 are rotatable in either direction. The example foil bearing 916, the example rolling element bearing 914, the example brace clutch 912, and, generally, the example integrated bearing system 910 are described in more detail below.

[0200] Figure 9 The example pump system 900 shown includes a bearing housing 913 to support a rolling element bearing 914 and a foil bearing 916. In some examples, the bearing housing 913 is an additively manufactured portion designed to fit the dimensions of the rolling element bearing 914 and the foil bearing 916. In some examples, the bearing housing 913 is manufactured via subtractive manufacturing to fit the dimensions of the rolling element bearing 914 and the foil bearing 916. In some examples, the bearing housing 913 securely supports the rolling element bearing 914 and the foil bearing 916 via bolts, pins, fasteners, and / or interference fits.

[0201] Figure 10 An enlarged view 1000 of an example integrated bearing system 910 of a pump system 900 is shown, which supports the radial load generated on the rotor shaft 904 during operation of the pump system 900. Figure 10 As shown, the enlarged view 1000 includes a rotor shaft 904, an integrated bearing system 910, a brace clutch 912, a bearing housing 913, a rolling element bearing 914, a foil bearing 916, a brace element 1002, a first inner ring 1004, a first outer ring 1006, a second inner ring 1008, and a second outer ring 1010. As previously described, Figure 10 Example components of the integrated bearing system 910 shown can be included Figure 9 The example shown is the second integrated bearing system 918. Figure 10 Example enlarged view 1000 shows the same as the previous reference. Figure 9 The rotor shaft 904, integrated bearing system 910, brace clutch 912, bearing housing 913, rolling element bearing 914, and foil bearing 916 are described.

[0202] like Figure 10The example integrated bearing system 910 shown includes a bracing element 1002 to engage a first inner ring 1004 and a first outer ring 1006, such that the first inner ring 1004 and the first outer ring 1006 rotate simultaneously and have the same torque output. Although in Figure 10 Two bracing elements 1002 are shown, but the example integrated bearing system 910 may include two or more bracing elements 1002. As previously described, the example bracing elements 1002 are asymmetrically shaped such that when the bracing elements 1002 rotate about the axis of rotation in a first direction, the bracing elements wedge between the first inner ring 1004 and the first outer ring 1006, and friction is generated between the components. The friction generated by the example bracing elements 1002 occurs between the bracing elements 1002 and the first inner ring 1004, and between the bracing elements 1002 and the first outer ring 1006. The friction generated by the bracing elements 1002 causes the first inner ring 1004 and the first outer ring 1006 to rotate at the same angular velocity. As previously described, when the bracing elements 1002 rotate about the axis of rotation in a second direction opposite to the first direction, the asymmetrical shape of the bracing elements 1002 also allows the first inner ring 1004 and the first outer ring 1006 to rotate freely in either direction. The following describes the bracing element 1002 and its operation in more detail.

[0203] like Figure 10 The example integrated bearing system 910 shown includes a first inner ring 1004 to engage with the bracing element 1002 and the rolling element bearing 914 at a first operating speed range (e.g., the tangential speed range of the rotor shaft 904 and / or the foil bearing 916 from 0 m / s to 50 m / s, the fluid flow rate range leaving the pump system 900 from 0 m / s to 10 m / s, etc.). Figure 10 The example shown has a first inner ring 1004 that is a hollow shaft surrounding a rotor shaft 904 and is connected to a second inner ring 1008 of a rolling element bearing 914 via bolts, adhesives, interference fits, etc. In some examples, the first inner ring 1004 is manufactured (e.g., subtractive or additive manufacturing) as the same portion as the second inner ring 1008. The example first inner ring 1004 is longer than the second inner ring 1008 and the second outer ring 1010, such that the first inner ring 1004 interfaces with the second inner ring 1008 and the bracing element 1002.

[0204] like Figure 10 The example integrated bearing system 910 shown includes a first outer ring 1006 to engage with the bracing element 1002 and the foil bearing 916 at a second operating speed range (e.g., the tangential speed range of the rotor shaft 904 and / or the foil bearing 916 from 50 m / s to 200 m / s, the fluid flow velocity range leaving the pump system 900 from 10 m / s to 100 m / s, etc.). Figure 10The example first outer ring 1006 shown is a shaft that is connected to the rotor shaft 904 via bolts, adhesives, interference fits, etc. In some examples, the first outer ring 1006 is manufactured (e.g., subtractive or additive manufacturing) as the same part as the rotor shaft 904. The example first outer ring 1006 is designed such that the first outer ring 1006 interfaces with the bracing element 1002 and the liner of the example foil bearing 916.

[0205] Figure 11 Example rolling element bearings for engaging and / or disengaging are shown (e.g., Figure 9 and / or 10 rolling element bearings 914) and / or example foil bearings (e.g., Figure 9 Example integrated bearing system 910 (and / or 10 foil bearings 916) Example of a separate diagonal brace clutch 1100 (e.g., Figure 9 And / or 10 (slant-braced clutch 912). Figure 11 The example slant clutch 1100 shown is illustrated from both equidistant viewpoint 1102 and frontal viewpoint 1104. Figure 11 The example bracing clutch 1100 shown includes a bracing element 1106 (e.g., Figure 10 The diagonal bracing element 1002), inner ring 1108, and outer ring 1110. Although twenty-six diagonal bracing elements 1106 are shown from a frontal viewpoint 1104 of the example diagonal bracing clutch 1100, it is possible to see more of these elements. Figure 11 Example of a slant-braced clutch 1100 and / or Figure 9 The example of the 10-brace clutch 912 includes more or fewer than twenty-six brace elements.

[0206] Figure 11The example swashplate clutch 1100 shown includes an inner ring 1108 and an outer ring 1110. The example inner ring 1108 is annular and includes a groove formed to fit the bottom portion of the swashplate element 1106. The example outer ring 1110 is also annular and includes a groove formed to fit the upper portion of the swashplate element 1106. The grooves included in the example inner ring 1108 and the example outer ring 1110 are designed such that the asymmetrical figure-eight shape of the swashplate element 1106 hooks into the groove. The example swashplate element 1106, the inner ring 1108, and the outer ring 1110 are also designed such that the top and bottom surfaces of the swashplate element 1106 project outward from the outer ring 1110 and inward from the inner ring 1108. In some examples, the inner ring 1108 and / or the outer ring 1110 are connected to the bracing element 1106 via rods, pins, screws, etc., to hold the bracing element 1106 in position between an inner ring (e.g., a first inner ring 1004) and an outer ring (e.g., a first outer ring 1006). In some examples, the inner ring 1108 and / or the outer ring 1110 hold the bracing element 1106 in position without fasteners (e.g., bolts, pins, rods, etc.). In some examples, the bracing element 1106, the inner ring 1108, and / or the outer ring 1110 are manufactured separately and assembled together to form the bracing clutch 1100. In some examples, the bracing element 1106, the inner ring 1108, and / or the outer ring 1110 are manufactured separately as parts to be assembled or as manufacturing assemblies via additive manufacturing (such as direct metal laser sintering). In some examples, the swashplate clutch 1100 includes a spring band to apply a preloaded spring force to the swashplate element 1106, such that the swashplate element 1106 engages with the inner ring 1108 and the outer ring 1110 before operation, and simultaneously the example pump system 900 operates within a first operating speed range.

[0207] Figure 12A An example engagement state 1200A of an example brace element 1202 (e.g., one of brace element 1002 and / or brace element 1106) is shown. The example engagement state 1200A shown in Figure 12 illustrates a brace element 1202 with a brace rotation axis 1204 about which it rotates. In some examples, the brace rotation axis 1204 is also the location of the center of gravity (CG) of the brace element 1202. The example brace element 1202 engages with the inner ring 1206 (e.g., inner ring 1004) and the outer ring 1208 (e.g., outer ring 1006) prior to operation of the pump system 900 due to the preloaded spring force acting on the brace element 1202. In some examples, a spring band is included in a brace clutch (e.g., brace clutch 1100) to relative to... Figure 12AThe orientation shown applies a preloaded spring force to the left side of the brace element 1202 above the axis of rotation 1204. The preloaded spring force acting on the brace element 1202 generates a spring torque 1210. Example: The spring torque 1210 causes the brace element 1202 to wedge and / or lock between the inner ring 1206 and the outer ring 1208 before operation of the pump system 900. When the pump system 900 begins operation, the outer ring 1208 is in a counter-clockwise direction (relative to...). Figure 12A The example spring band rotates in the orientation shown, and generates friction between the brace element 1202, the outer ring 1208, and the inner ring 1206, causing the inner ring 1206 to rotate counterclockwise at the same rate as the outer ring 1208. The example spring band is designed to generate a sufficiently large spring torque 1210 to counteract the frictional torque acting counterclockwise on the brace element 1202, opposite to the spring torque 1210. At this point in the operation of the example pump system 900, the contact point between the brace element 1202 and the outer ring 1208 is to the right of the brace rotation axis 1204 and the CG of the brace element 1202. The example contact point is also the location where the frictional force and the resulting frictional torque act on the brace element 1202. During operation of the example pump system 900 in the first operating speed range, centrifugal force acts on the brace element 1202 at the brace rotation axis 1204 and / or the CG of the brace element 1202. Since the CG of the brace rotation axis 1204 and / or the brace element 1202 is to the left of the contact point in the first operating speed range, the centrifugal force generates a first centrifugal torque that acts in the same direction as the spring torque and opposite to the frictional torque. Therefore, when the example shaft (e.g., rotor shaft 904) drives the outer ring 1208 to rotate via mechanical connections (e.g., bolts, adhesives, interference fits, etc.) in the first operating speed range, the brace element 1202 remains engaged with both the outer ring 1208 and the inner ring 1206, causing the inner ring 1206 to rotate at the same speed as the outer ring 1206. Due to the design, shape, structure, materials, etc. of the example spring band, as long as the outer ring 1208 continues to rotate at an angular velocity within a first operating speed range (e.g., less than the foil bearing liftoff speed (e.g., the tangential velocity of the rotor shaft 904 and / or foil bearing 916 from 10 m / s to 50 m / s)), the example brace element 1202 remains engaged with the inner ring 1206 and the outer ring 1208.

[0208] Figure 12B An example separated state 1200B of an example bracing element 1202 (e.g., one of bracing element 1002 and / or bracing element 1106) is shown. Figure 12B The example separation state 1200B shown illustrates the same bracing element 1202, which has the same bracing rotation axis 1204 and / or CG about which the bracing element 1202 rotates. Figure 12B The example separation state 1200B shown includes with Figure 12A The same inner ring 1206 and the same outer ring 1208. Figure 12B In the illustrated separation state 1200B, the outer ring 1208 (e.g., outer ring 1006) is connected to the example shaft (e.g., rotor shaft 904) and rotates at a rate within a second operating speed range (e.g., greater than the foil bearing starting speed (e.g., a tangential speed of 10 m / s to 50 m / s)). Once the outer ring 1208 and the shaft (e.g., rotor shaft 904) rotate at a rate within the second operating speed range, the bracing element 1202 separates from the outer ring 1208 and the inner ring 1206 and rotates in the opposite direction in a counterclockwise direction. As the example pump system 900 increases its operating speed to closer to the lower limit of the second operating speed range, the frictional force and frictional torque acting on the bracing element 1202 increase. The frictional torque acting on the bracing element 1202 counteracts the spring torque 1210. Once the operating speed of the pump system 900 reaches the lower limit of the second operating speed range, the frictional torque is sufficient to counteract the spring torque 1210, causing the CG of the brace rotation axis 1204 and / or the brace element 1202 to move to the right of the contact point between the brace element and the outer ring 1208. Once the contact point shifts to the left of the CG of the brace rotation axis 1204 and / or the brace element 1202, the first centrifugal torque reverses direction and becomes a second centrifugal torque 1212, which supplements the frictional torque and is opposite to the spring torque 1210. Once the sum of the frictional torque and the second centrifugal torque 1212 exceeds the spring torque 1210, the brace element 1202 separates from the inner ring 1206 and the outer ring 1208. Therefore, in response to the example shaft (e.g., rotor shaft 904) driving the outer ring 1208 to rotate at a second operating speed range via mechanical connections (e.g., bolts, adhesives, interference fits, etc.), the bracing element 1202 separates from the outer ring 1208 and the inner ring 1206, allowing the inner ring 1206 to rotate freely from the outer ring 1208.

[0209] Figure 13 An example integrated bearing system 1300 is shown (e.g., Figure 9 and 10 The integrated bearing system 910 and the integrated bearing system 1300 are used in example pump systems (e.g., Figure 9 Example load paths supported at different points during operation of the pump system 900. Example integrated bearing system 1300 includes shaft 1302 (e.g., Figure 9 and / or 10 rotor shafts 904), bearing housing 1304 (e.g., Figure 9 and / or 10 bearing housings 913), slant clutch 1306 (e.g., Figure 9and / or 10 inclined strut clutch 912), inner ring 1308 (e.g., Figure 10 Inner ring 1004 and / or Figure 12A And / or the inner ring 1206 of 12B), the outer ring 1310 (e.g., Figure 10 Outer ring 1006 and / or Figure 12A And / or 12B outer ring 1208), rolling element bearing 1312 (e.g., Figure 9 And / or 10 rolling element bearings 914), foil bearings 1314 (e.g., Figure 9 (and / or 10 foil bearings 916), first load path 1316 and second load path 1318. Example first load path 1316 and example second load path 1318 are representations of forces acting on example inner ring 1308 and example outer ring 1310, respectively, rather than physical objects.

[0210] As mentioned above and Figure 9 As shown in example 10, the example outer ring 1310 is connected to the example shaft 1302 via mechanical fasteners (e.g., bolts, screws, pins, adhesives, interference fits, etc.). Similarly, as previously described, the example bearing housing 1304 securely supports the example rolling element bearing 1312 and the example foil bearing 1314 in place during operation via mechanical fasteners (e.g., bolts, screws, pins, adhesives, interference fits, etc.). When the example shaft 1302 rotates at a first angular velocity associated with a first tangential velocity that does not satisfy the foil bearing starting speed (e.g., a tangential velocity of 10 m / s to 50 m / s), the example brace clutch 1306 engages with the example outer ring 1310 and the example inner ring 1308. In response to the example swashplate clutch 1306 engaging with the inner ring 1308 and outer ring 1310 within a first operating speed range, shaft 1302 generates an example first load path 1316 acting on the inner ring 1308 and the rolling element bearing 1312. Therefore, within the first operating speed range, the example rolling element bearing 1312 supports the weight of shaft 1302.

[0211] As mentioned above and Figure 12A and 12BAs shown, the example swashplate clutch 1306 disengages from the inner race 1308 and the outer race 1310 at a second angular velocity, which is associated with a second tangential velocity that satisfies the starting speed of the foil bearing (e.g., a tangential velocity of 10 m / s to 50 m / s). In response to the swashplate clutch 1306 disengaging from the inner race 1308 and the outer race 1310 at the second tangential velocity, the shaft 1302 generates an example second load path 1318 acting on the inner and outer races 1310 and the foil bearing 1314. Therefore, within the second operating speed range, the example foil bearing 1314 supports the weight of the shaft 1302. In some examples, the first load path 1316 and the second load path 1318 have the same force value sufficiently similar to the weight of the shaft 1302.

[0212] Figure 14 This is a flowchart illustrating an example process or operation 1400, as disclosed herein, whereby the integrated bearing system 910 can follow the example process or operation 1400 to dynamically support the rotor shaft 904 in the pump system 900. Although the primary reference is to dynamically support... Figure 9 Operation 1400 is described primarily with reference to the rotor shaft 904 in the pump system 900, but operation 1400 can be used to support another rotating shaft in another pump system using the integrated bearing system 910. Although operation 1400 is primarily described with reference to dynamically supporting the rotor shaft 904 using the integrated bearing system 910, another integrated bearing system (e.g., integrated bearing system 918) can use operation 1400 to dynamically support the rotor shaft 904 or another rotor shaft.

[0213] At block 1402, pump system 900 begins to pressurize the fluid flowing through the heat management system (e.g., heat exchange fluid, supercritical fluid, supercritical carbon dioxide (sCO2), etc.) and increases the flow rate of the fluid leaving pump system 900. For example, current is supplied to the stator 906 of the motor in pump system 900, causing electromagnets in stator 906 to generate one or more magnetic fields whose polarities alternate over time based on the direction of the current flowing through stator 906. The generated magnetic field is perpendicular to the axis of rotation of rotor 905 in the motor. Rotor 905 is attached to rotor shaft 904 and includes permanent magnets that are attracted and / or repelled by the alternating polarities of the electromagnets in stator 906. As rotor shaft 904 rotates at an increased angular velocity, impeller 902 coupled to rotor shaft 904 also rotates at an increased angular velocity. Impeller 902 includes blades or vanes that increase fluid pressure and flow rate.

[0214] At block 1404, the integrated bearing system 910 of the pump system 900 engages with the inner ring 1004 attached to the rolling element bearing 914 and the outer ring 1006 attached to the rotor shaft 904. For example, the swashplate clutch 912 of the integrated bearing system 910 includes a swashplate element 1002 (e.g., Figure 11 The diagonal bracing element 1106 engages with the inner ring 1004 and the outer ring 1006 due to the preloaded spring force acting on the diagonal bracing element 1002. When the diagonal bracing element 1002 wedges between the outer ring 1006 and the inner ring 1004, a reaction force and friction are generated, which causes the inner ring 1004 to rotate at the same rate as the outer ring 1006.

[0215] At block 1406, the integrated bearing system 910 of the pump system 900 supports the rotor shaft 904 via the inner ring 1004. For example, the outer ring 1006 rotates at the same rate as the rotor shaft 904, the swashplate clutch 912 engages with the outer ring 1006 and the inner ring 1004, the inner ring 1004 rotates at the same rate as the outer ring 1006 and the rotor shaft 904, and the rolling element bearing 914 supports the radial load on the rotor shaft 904 via the inner ring 1004.

[0216] At block 1408, the pump system 900 increases the operating speed of the electric motor. For example, current is supplied to the stator 906 at a greater rate, causing the electromagnets in the stator 906 to alternate polarities at a greater rate. As the electromagnets in the stator 906 alternate polarities at a greater rate, the angular velocity of the rotor 905 increases at the same rate. As the angular velocity of the rotor 905 and the connected rotor shaft 904 increases, the tangential velocity of the rotor shaft 904 and the outer ring 1006 also increases.

[0217] At block 1410, if the tangential velocity of the rotor shaft A104 and / or the outer ring 1006 meets the foil bearing starting speed (e.g., 10 m / s to 50 m / s), operation 1400 proceeds to block 1412. If the tangential velocity of the rotor shaft A104 and / or the outer ring 1006 does not meet the foil bearing starting speed, operation 1400 returns to block 1406, where the rolling element bearing 914 continues to support the weight of the rotor shaft 904 via the inner ring 1004.

[0218] At box 1412, the integrated bearing system 910 is separated from the inner ring 1004 and the outer ring 1006. For example, once the tangential speed of the rotor shaft A104 and / or the outer ring 1006 is high enough to meet the starting speed of the foil bearing, the centrifugal force and friction acting on the bracing element 1002 of the bracing clutch 912 cancel each other out and exceed the spring torque, causing the bracing element 1002 to rotate in the opposite direction and separate from the inner ring 1004 and the outer ring 1006.

[0219] At box 1414, the integrated bearing system 910 supports the radial load generated by the rotor shaft A104 via the outer ring 1006. For example, once the bracing element 1002 separates from the outer ring 1006 and the inner ring 1004, the foil bearing 916 supports the total weight and / or most of the weight of the rotor shaft A104 via the outer ring 1006, which is connected to and interacts with the rotor shaft 904. As long as the foil bearing's starting speed is met, the foil bearing 916 continues to support the total radial load and / or most of the radial load on the rotor shaft A104.

[0220] At block 1416, if the tangential velocity of rotor shaft A104 and / or foil bearing 916 continues to meet the foil bearing starting speed, operation 1400 returns to block 1414, where the integrated bearing system 910 continues to support the radial load of rotor shaft 904 via outer ring 1006. If the operating speed of pump system 900 slows down, causing the tangential velocity of rotor shaft 904 and / or foil bearing 916 to no longer meet the foil bearing starting speed, operation 1400 proceeds to block 1418.

[0221] At block 1418, the integrated bearing system 910 of the pump system 900 engages with the inner ring 1004 attached to the rolling element bearing 914 and the outer ring 1006 attached to the rotor shaft 904. For example, the spring torque acting on the bracing element exceeds the opposing frictional and centrifugal forces, and the bracing clutch 912 of the integrated bearing system 910 engages with both the inner and outer rings 1004 and 1006. At block 1420, the integrated bearing system 910 supports the radial load of the rotor shaft 904 via the inner ring 1004. For example, the bracing clutch 912 of the integrated bearing system 910 engages with the inner ring 1004 attached to the rolling element bearing 914, and the rolling element bearing 912 supports the total radial load and / or most of the radial load of the rotor shaft 904 via the inner ring 1004. Operation 1400 continues at block 1420 until the pump system 900 stops operating, at which point... Figure 14 The operation ended at 1400.

[0222] In some examples, the pump system 900 includes devices for increasing kinetic energy. For example, the devices for increasing kinetic energy may be comprised of… Figure 9 The impeller 902, rotor shaft 904, rotor 905, and / or stator 906 are implemented. In some examples, the means for adding the impeller may include a motor, impeller shaft, and impeller.

[0223] In some examples, the pump system 900 includes means for providing torque. For example, the means for providing torque may be... Figure 9 The stator 906 and / or rotor 905 are implemented. In some examples, the means for providing the device may include an electric motor.

[0224] In some examples, the pump system 900 includes means for a first support. For example, the means for the first support may be... Figure 9 And / or 10 of the first integrated bearing systems 910, Figure 9 The second integrated bearing system 918 Figure 9 and / or 10 first rolling element bearings 914, Figure 9 The second rolling element bearing 922, Figure 13 Integrated bearing system 1300 and / or Figure 13 The rolling element bearing 1312 is implemented. In some examples, the means for the first support may include angular contact ball bearings, hybrid ceramic bearings, tapered roller bearings, deep groove single ball bearings, double ball bearings, and / or spherical bearings.

[0225] In some examples, the pump system 900 includes means for a second support. For example, the means for the second support may be... Figure 9 And / or 10 of the first integrated bearing systems 910, Figure 9 The second integrated bearing system 918 Figure 9 and / or 10 of the first foil bearings 916, Figure 9 The second foil bearing 924, Figure 13 Integrated bearing system 1300, and / or Figure 13 The foil bearing 1314 is implemented. In some examples, the means for the second support may include an air foil bearing and / or a fluid static foil bearing.

[0226] In some examples, the pump system 900 includes a means for engagement. For example, the means for engagement may be... Figure 9 And / or 10 of the first integrated bearing systems 910, Figure 9 The second integrated bearing system 918 Figure 9 and / or the first inclined strut clutch 912 of 10, Figure 10 The second oblique support clutch 920 Figure 10 diagonal bracing element 1002, Figure 11 1100 inclined strut clutch Figure 11 diagonal bracing element 1106 Figure 12A-12B diagonal bracing element 1202, and / or Figure 13 The F506 is implemented using a slant-braced clutch. In some examples, the means for engagement may include a clutch and / or one or more rotating elements of asymmetrical shape.

[0227] In some examples, the pump system 900 includes a device for separation. For example, the device for separation can be implemented by an oil separator. A further description of an example oil separator in which the device for separation can be implemented is discussed in more detail below.

[0228] This document discloses an example integrated bearing system for a shaft in a dynamically supported pump system. The example integrated bearing system disclosed herein includes a swashplate clutch, an inner ring attached to a rolling element bearing, and an outer ring attached to a foil bearing and a rotor shaft. The example integrated bearing system disclosed herein includes a swashplate clutch that engages with both the inner and outer rings in a first operating speed range (e.g., a tangential speed range from 0 m / s to 10 m / s and / or 50 m / s). Therefore, the example rolling element bearing supports the radial load generated when the example rotor shaft operates within the first operating speed range. The example integrated bearing system disclosed herein also includes a swashplate clutch that disengages from both the inner and outer rings in a second operating speed range (e.g., a tangential speed range from 10 m / s and / or 50 m / s to 200 m / s) due to centrifugal forces acting on the swashplate elements of the swashplate clutch. Therefore, the example foil bearing supports the radial load generated when the example rotor shaft operates within the second operating speed range. The example integrated bearing system disclosed herein reduces wear on foil bearings in example pump systems (compared to example pump systems without an integrated bearing system) because the rolling element bearings support most and / or the total radial load on the rotor shaft during the pump system's start-up and shutdown speeds. The example integrated bearing system disclosed herein allows the foil bearings to operate for extended periods without damage and / or maintenance (compared to foil bearings in pump systems without an example integrated bearing system) because the example foil bearings utilize air pressure within the foil bearing (which does not contain spring-loaded foils) to support most and / or the total radial load on the rotor shaft while operating at a second operating speed range.

[0229] Layered barrier tank for magnetic coupling components and its manufacturing method

[0230] In some known pumps, in order to reduce the barrier tank (e.g., Figure 4 The barrier tank 452) is for magnetic coupling elements (e.g., Figure 4 Due to the influence of the magnetic field generated by the first magnetic coupling element 450 and the second magnetic coupling element 460, the barrier tank uses a non-metallic material. For example, the barrier tank may include plastic. However, plastic barrier tanks include a large thickness to provide sufficient structural strength, and are still often not strong enough to withstand high pressures (e.g., pressures exceeding 1,000 pounds per square inch absolute (PSIA)). Additionally, non-metallic materials may deform at higher temperatures. Therefore, the use of a non-metallic material for the barrier tank limits the potential operating pressure and / or temperature of the associated pump. Consequently, a non-metallic barrier tank limits the rate at which fluid can be driven through the heat transfer bus 202, and in turn limits the rate at which heat energy can be transferred between the fluid and the working fluid.

[0231] In some pumps, the barrier tank is made of titanium to enable it to withstand increased pressures (e.g., pressures exceeding 1,000 PSI). However, the titanium barrier tank can introduce eddy current losses between the magnetic field generated by the magnetic coupler. Furthermore, these eddy current losses increase when the titanium barrier tank includes a greater thickness to withstand higher pressures. Therefore, the titanium barrier tank can limit the rate at which the magnetic coupler can rotate while maintaining magnetic coupling. Consequently, the titanium barrier tank can affect the torque transmitted between the motor shaft and the impeller shaft. Additionally, to overcome eddy current losses, the titanium barrier may require larger magnets for the magnetic coupler, increasing the pump size and / or cost, necessitating a larger motor to drive the rotation of the magnetic coupler, and / or requiring cooling arrangements to dissipate the heat generated by the magnetic coupler during rotation.

[0232] Figure 15 A first example shield 1500 (e.g., a barrier tank) is shown, which can be used for a heat transfer bus pump 400 (e.g., Figure 4 Barrier tank 452) Figure 5 Pump system 500 (e.g., Figure 5 Barrier jar 536), Figure 6 Pump system 600 (e.g., Figure 6 Barrier jar 636) Figure 7 The pump system 700 and / or any other pump system disclosed herein that uses a barrier tank or shield to contain the fluid flow. Figure 15 In the example shown, the shroud 1500 includes an inner shell layer 1502, an outer shell layer 1504, and a core shell layer 1506 (e.g., a metal core shell layer, a metal core layer, etc.), with the core shell layer 1506 positioned between the inner shell layer 1502 and the outer shell layer 1504. The shroud 1500 defines a cavity 1508. Therefore, when the shroud 1500 is implemented in the heat transfer bus pump 400, a magnetic coupling element (e.g., Figure 4 The second magnetic coupling element 460 can be positioned in cavity 1508, and another magnetic coupling element (e.g., Figure 4 The first magnetic coupling element 450 can be positioned around the shield 1500. Thus, the inner shell 1502 can contact the first fluid (e.g., a heat exchange fluid, such as a supercritical fluid (e.g., sCO2, etc.)) and the outer shell 1504 can contact the second fluid (e.g., air, hydrogen, etc.).

[0233] exist Figure 15In the example shown, the inner surface 1510 of the core shell 1506 is in complete contact with the inner shell 1502. Similarly, the outer surface 1512 of the core shell 1506 is in complete contact with the outer shell 1504. Specifically, the inner shell 1502 and the outer shell 1504 provide an insulating layer surrounding the core shell 1506. As a result, the continuous surface contact between the core shell 1506 and the inner shell 1502 and the outer shell 1504 helps the core shell 1506 dissipate heat generated due to the core shell 1506 encountering a rotating magnetic field. Specifically, the inner shell 1502 can transfer thermal energy between the first fluid and the core shell 1506. Further, the outer shell 1504 can transfer thermal energy between the second fluid and the core shell 1506. The heat transfer bus pump 400 can recirculate the first fluid to increase the rate at which thermal energy is transferred between the core shell 1506 and the first fluid through the inner shell 1502. In addition, the vent 461 ( Figure 4 This allows the second fluid to flow through the connecting housing 424. Figure 4 The fluid circulates within the core shell 1506 and the second fluid. In some examples, a fan drives a second fluid into and / or out of the coupling housing to increase the rate at which heat is transferred between the outer shell layer 1504 and the second fluid. In some other examples, the coupling housing 424 and / or the motor housing 412 ( Figure 4 The housing 424 is filled with a second fluid, which allows the second fluid to circulate and cool the shield 1500 when the housing 424 does not include the vent 461.

[0234] exist Figure 15 In this configuration, the shroud 1500 may include a thickness between 0.090 inches (in) and 0.125 inches. In some examples, the inner shell layer 1502 includes a first thickness (e.g., between 0.005 inches and 0.040 inches), the outer shell layer 1504 includes a first or second thickness (e.g., between 0.005 inches and 0.040 inches), and the core shell layer 1506 includes a third thickness (e.g., between 0.005 inches and 0.090 inches). In some examples, the third thickness is greater than the first and second thicknesses. However, the third thickness may alternatively be less than, or approximately equal to, the first and / or second thicknesses. The thickness of the shroud 1500, and more specifically, the thicknesses of the inner shell layer 1502, outer shell layer 1504, and core shell layer 1506, may be based on the pressure encountered during operation of the associated pump (e.g., a heat transfer bus pump 400). For example, when the pump 400 operates at a first maximum pressure, the shield 1500 may include a first thickness (e.g., 0.125 in), and when the pump 400 operates at a second maximum pressure less than the first maximum pressure, the shield 1500 may include a second thickness (e.g., 0.090 in).

[0235] exist Figure 15In the example shown, the inner shell layer 1502, the outer shell layer 1504, and the core shell layer 1506 each have a uniform thickness. In some examples, the inner shell layer 1502, the outer shell layer 1504, and / or the core shell layer 1506 each have a non-uniform thickness, as discussed in further detail below.

[0236] The inner shell 1502 and outer shell 1504 comprise non-metallic materials, such as ceramic materials, polymeric materials, and / or composite materials. In some examples, the ceramic materials are alumina (I) (Al2O), alumina (II) (AlO) (e.g., alumina monoxide), alumina (III) (Al2O3) (e.g., alumina, aluminum oxide), zirconia (e.g., zirconia-toughened alumina), and / or silicon carbide. In some examples, the polymeric materials and / or composite materials comprise carbon fiber composites and / or polyimides (e.g., T650-35, PMR-15, MVK-14 standard modulus, etc.). Carbon fiber composites may comprise short carbon fibers, long carbon fibers, and / or endless carbon fibers. Thus, the inner shell 1502 defines a first non-metallic layer of the shield 1500, and the outer shell 1504 defines a second non-metallic layer of the shield 1500. In some examples, both the inner shell 1502 and the outer shell 1504 comprise ceramic materials. In some examples, both the inner shell 1502 and the outer shell 1504 comprise polymers. In some examples, both the inner shell 1502 and the outer shell 1504 comprise composite materials. In some examples, the inner shell 1502 comprises a first material, such as a ceramic material, and the outer shell 1504 comprises a second material different from the first material, such as a polymer or composite material. Further, the core shell 1506 comprises nickel and / or cobalt. Additionally or alternatively, the core shell 1506 may comprise different metals.

[0237] exist Figure 15 In the middle, the protective cover 1500 includes a flange portion 1514. In Figure 4 In this structure, the inner shell layer 1502, the outer shell layer 1504, and the core shell layer 1506 extend circumferentially outward to form a flange portion 1514. Therefore, Figure 4 The O-ring 459 can be positioned around the flange portion 1514. Further, the flange portion 1514 can be positioned via... Figure 4 The barrier tank retainer 454 and bolt 458 are pressed against Figure 4 On the rear end of the front bearing housing 428. When the inner shell layer 1502 and the outer shell layer 1504 surround the core shell layer 1506, the O-ring 459 presses against the outer shell layer 1504 so that the shield 1500 can airtightly seal the rear end of the front bearing housing 428.

[0238] The inner shell 1502 can be formed via molding and / or slurry-based processing techniques (such as additive manufacturing (e.g., thermal spraying, cold spraying, etc.) and / or sintering). In some examples, when the inner shell 1502 is formed via thermal spraying and / or cold spraying, an initial mandrel is present, the inner shell 1502 is sprayed onto the initial mandrel, and subsequently separated from it. In some examples, when the inner shell 1502 is formed via thermal spraying and / or cold spraying, an initial portion (e.g., an inner or outer portion) of the inner shell 1502 can be formed via another manufacturing technique (such as slurry-based processing), and the remaining portion of the inner shell 1502 can be sprayed onto the initial portion. Further, the initial portion of the inner shell 1502 can be machined to a certain thickness prior to thermal spraying and / or cold spraying. In some examples, the inner shell 1502 can be formed via other manufacturing techniques (such as casting (e.g., slip casting, tape casting, etc.) and / or pressing).

[0239] Furthermore, the core shell layer 1506 is electroformed (e.g., electrodeposited) onto the outer surface 1516 of the inner shell layer 1502. That is, the inner shell layer 1502 serves as a mandrel on which the core shell layer 1506 is formed. Advantageously, the electroformed core shell layer 1506 allows for a reduction in thickness compared to the thickness achievable by conventional manufacturing techniques for forming metals.

[0240] Furthermore, the outer shell layer 1504 can be formed on the core shell layer 1506 via thermal spraying or cold spraying. Therefore, the electroformed layer of the core shell layer 1506 can serve as a bonding coating for the outer shell layer 1504. In some examples, the inner shell layer 1502 can be formed via other manufacturing techniques such as composite layup (e.g., composite layer layup), molding (e.g., injection molding), slip casting, pressing, and / or casting.

[0241] For example, the inner shell 1502 can be molded, the core shell 1506 can be electroformed onto the inner shell 1502, and the outer shell 1504 can be thermally sprayed onto the core shell 1506. In some examples, the core shell 1506 is electroformed onto the inner surface of the outer shell 1504, rather than the outer surface of the inner shell 1502. Furthermore, the inner shell 1502 can be thermally or cold-sprayed onto the core shell 1506. Additionally, the shield 1500 can be machined or ground to maintain the thickness of the shield 1500 within certain tolerances and define a uniform profile along the inner surface of the inner shell 1502 and / or the outer surface of the outer shell 1504.

[0242] Advantageously, the core shell layer 1506 enables the first example shroud 1500 to withstand increased pressure without rupturing, and consequently, allows the heat transfer bus pump 400 to drive fluid at higher pressures. Specifically, the first example shroud 1500 allows the speed of the motor 410 to be increased to increase the output (e.g., volumetric flow rate) generated by the impeller 406. As a result, the heat transfer bus pump 400 can deliver fluid to higher pressures in a shorter time. Figure 1 aircraft 10 and / or Figure 2 The gas turbine engine 100 provides more fluid to the area so that the fluid interacts with... Figure 1 Heat transfer between the working fluids in the aircraft 10 and / or gas turbine engine 100 can occur at a faster rate. Furthermore, the geometry of the inner shell 1502, outer shell 1504 and / or core shell 1506 can be non-cylindrical to increase the stiffness of the first shield 1500 and, consequently, increase the pressure that the shield 1500 can withstand.

[0243] Furthermore, the electroformed core shell layer 1506 allows for a reduced thickness that cannot be produced using conventional manufacturing techniques. As a result, when the first shield 1500 is implemented in the heat transfer bus pump 400, the core shell layer 1506 causes reduced eddy current losses compared to known barrier tanks that include metal. Therefore, the reduced eddy current losses allow for a reduction in the size of the motor 410, the first magnetic coupling element 450, and the second magnetic coupling element 460. Furthermore, the reduced eddy current losses reduce the impact of… Figure 4 The rotating magnetic field generated by the first magnetic coupling element 450 and the second magnetic coupling element 460 generates heat energy from the core shell layer 1506. Therefore, the electroformed core shell layer 1506 eliminates the need for a cooling sleeve surrounding the connecting housing 424. Additionally, the core shell layer 1506 increases the temperature range that the shroud 1500 can withstand.

[0244] Similarly, thermal spraying allows the inner shell layer 1502 and / or outer shell layer 1504 to have a reduced thickness. Therefore, the overall thickness of the first shield 1500 is minimized or otherwise reduced, which allows the gap between the first magnetic coupling member 450 and the second magnetic coupling member 460 to be minimized or otherwise reduced. Thus, smaller magnets and / or smaller motors can be used to more efficiently transmit torque between the motor shaft 438 and the impeller shaft 466, reducing the size and / or cost of the heat transfer bus pump 400. Additionally, the reduced thickness of the inner shell layer 1502 and / or outer shell layer 1504 and / or the continuous surface contact of the core shell layer 1506 with the inner shell layer 1502 and outer shell layer 1504 allows the inner shell layer 1502 and / or outer shell layer 1504 to more efficiently transfer heat between the encountered fluid and the core shell layer 1506. Therefore, the inner shell layer 1502 and / or the outer shell layer 1504 can help the core shell layer 1506 dissipate heat. Furthermore, the reduced eddy current losses caused by the shield 1500 and the reduced thickness of the shield 1500 allow for increased separation between the shield 1500 and the magnetic couplers 450, 460, enabling fluid to flow between the shield 1500 and the magnetic couplers 450 at an increased flow rate, thereby increasing the rate of heat transfer between the shield 1500 and the fluid.

[0245] Furthermore, reducing the thickness of the first shield 1500 and reducing eddy current losses caused by the shield 1500 allows the rotation of the first magnetic coupler 450 and the second magnetic coupler 460 to remain interlocked at higher speeds. Therefore, the first shield 1500 enables the heat transfer bus pump 400 to drive fluid at increased flow rates and / or increased pressures.

[0246] Figure 16 It shows that it can be used Figure 15 The first example shield 1500 (e.g., Figure 15 Another example of an inner shell 1600 in the inner shell 1502). Figure 16 In this design, the inner shell 1600 includes a base portion 1602 and ribs 1604 (e.g., ridges) projecting radially from the base portion 1602. Specifically, the ribs 1604 extend away from a cavity 1606 (e.g., cavity 1508) defined by the base portion 1602. Thus, a first portion of the inner shell 1600 includes a first thickness defined by the base portion 1602, and a second portion of the inner shell 1600 includes a second thickness defined by the base portion 1602 and the ribs 1604. In some examples, the second thickness is between 0.75 inches and 1.0 inch. Advantageously, the ribs 1604 cause... Figure 15 The shield 1500 can provide increased structural stiffness, and thus increase the maximum pressure that the shield 1500 can withstand.

[0247] exist Figure 16In the example shown, ribs 1604 are spaced apart along the periphery of the base portion 1602. Furthermore, the circumferentially spaced ribs 1604 extend along the base portion 1602 in the axial direction A defined by the inner shell layer 1600. Figure 16 In the example shown, rib 1604 extends in a straight line along the axial direction A. However, it should be understood that rib 1604 can extend along the base in any shape to increase... Figure 15 The rigidity of the protective shell 1500. For example, rib 1604 can extend from the base portion 1602 in a straight line not defined by an axial direction (e.g., where the circumferential position of the first end of the ridge is different from the circumferential position of the second end of the ridge). In some examples, rib 1604 extends helically along the base portion 1602 in the axial direction A. In some examples, rib 1604 extends along the base portion 1602 in the circumferential direction C defined by the inner shell 1600. In some examples, rib 1604 includes a wave-like portion such that as rib 1604 extends along the base portion 1602 in the axial direction A, the position of rib 1604 varies in the circumferential direction C.

[0248] also, Figure 15 The core shell layer 1506 can be electroformed onto the inner shell layer 1600. Therefore, Figure 15 The core shell layer 1506 is stacked on the base portion 1602 and rib 1604 of the inner shell layer 1600. As a result, Figure 15 The core shell layer 1506 may include a first portion fixed to the base portion 1602 and a second portion fixed to the rib 1604. Therefore, Figure 15 The first portion of the core shell layer 1506 may include a first inner diameter and a first outer diameter, and the second portion of the core shell layer 1506 may include a second inner diameter and a second outer diameter, wherein the second inner diameter and the second outer diameter are larger than the first inner diameter and the first outer diameter. Furthermore, the geometry of the core shell layer 1506 can further increase the structural stiffness of the shield 1500.

[0249] Figure 17A -C illustrates the steps of an example manufacturing process for forming the first shield 1500. Specifically, Figure 17A -C shows that the first shield 1500 includes Figure 15 The first inner shell 1502 and Figure 16 The manufacturing process steps for the second inner shell layer 1600. Figure 17A In this process, inner shell layers 1502 and 1600 are formed. For example, inner shell layers 1502 and 1600 can be formed via molding, thermal spraying, and / or cold spraying. Figure 17B In the middle, the core shell layer 1506 is electroformed onto the inner shell layers 1502 and 1600. Figure 17C In the middle, the outer shell layer 1504 is thermally sprayed or coldly sprayed onto the core shell layer 1506.

[0250] Figure 18 This indicates the manufacture of barrier containers (such as...) Figure 15 A flowchart of an example method 1800 (and / or shield 1500 of 17C). In some examples, at least a portion of example method 1800 represents example machine-readable instructions that can be executed and / or instantiated by processor circuitry communicating with manufacturing equipment to manufacture shield 1500. Additionally or alternatively, Figure 18 Method 1800 may use application-specific integrated circuits (ASICs) and / or field-programmable gate arrays (FPGAs), which are constructed such that the operation corresponding to method 1800 is performed by manufacturing equipment.

[0251] Figure 18 Example method 1800 begins at block 1802, where inner shell layers 1502, 1600 are formed. For example, inner shell layers 1502, 1600 may be formed via molding and / or slurry-based manufacturing techniques (such as additive manufacturing (e.g., thermal spraying or cold spraying) and / or sintering).

[0252] At box 1804, a core shell layer 1506 is formed on inner shell layers 1502 and 1600. For example, the core shell layer 1506 can be electroformed onto the outer surface of the inner shell layers 1502 and 1600. Thus, the inner shell layers 1502 and 1600 serve as the mandrel for the electroformed core shell layer 1506. As a result, the inner surface of the core shell layer 1506 is in complete contact with the inner shell layers 1502 and 1600.

[0253] At box 1806, an outer shell layer 1504 is formed on the core shell layer 1506. For example, the outer shell layer 1504 may be thermally sprayed and / or cold-sprayed onto the core shell layer 1506. In some examples, the outer shell layer 1504 is thermally sprayed and / or cold-sprayed onto a portion (e.g., an edge) of the inner shell layer 1502, such that the outer shell layer 1504 and the inner shell layer 1502 encapsulate the core shell layer 1506. As a result, the outer surface of the core shell layer 1506 is in complete contact with the outer shell layer 1504.

[0254] In some examples, the shield 1500 includes a first means for insulation. For example, the first means for insulation may be made of... Figure 15 and 17A -C inner shell 1502 or Figure 16 and 17A-C inner shell layer 1600 is implemented. In some examples, the first device for insulation may include ceramic, polymer or composite material. For example, the first device for insulation may include alumina (I) (Al2O), alumina (II) (AlO) (e.g., alumina monoxide), alumina (III) (Al2O3) (e.g., alumina, aluminum oxide), zirconium oxide (e.g., zirconium oxide toughened alumina) and / or silicon carbide.

[0255] In some examples, the shield 1500 includes a second means for insulation. For example, the second means for insulation may be provided by... Figure 15 and 17A -C is implemented with a shell layer 1504. In some examples, the second device for insulation may include ceramic, polymer, or composite material. For example, the first device for insulation may include alumina (I) (Al2O), alumina (II) (AlO) (e.g., alumina monoxide), alumina (III) (Al2O3) (e.g., alumina, aluminum oxide), zirconium oxide (e.g., zirconium oxide toughened alumina), and / or silicon carbide.

[0256] In some examples, the shield 1500 includes means for supporting the first means for insulation and the second means for insulation. The means for support may fill the region defined between the first means for insulation and the second means for insulation. For example, the means for support may be implemented by a core shell layer 1506. In some examples, the means for support includes nickel, cobalt, and / or one or more other metals.

[0257] In some examples, the shield 1500 includes means for reinforcement. For example, the means for reinforcement may be made of... Figure 16 and 17A The inner shell 1600 at -17°C is implemented with ribs 1604 and / or a core shell 1506 positioned around ribs 1604.

[0258] This document discloses an example layered magnetic coupling shield or barrier canister. The example layered magnetic coupling shield or barrier canister may include an inner shell layer, an outer shell layer, and a metal core shell layer between the inner and outer shell layers. The inner or outer shell layer can serve as a mandrel on which the metal core shell layer is formed. Compared to other manufacturing techniques, the electroformed metal core shell layer allows for a reduction in its thickness (e.g., as small as 2 mils). Furthermore, the metal core shell layer can induce less eddy current loss between magnetic coupling elements positioned within and around the layered shield or barrier canister, while providing structural support capable of withstanding higher pressures (e.g., pressures greater than 6,400 PSI). Additionally, the inner and outer shell layers can insulate the metal core shell layer from fluids to prevent oxidation and / or exposure to extreme temperatures. Moreover, the inner and / or outer shell layers can be formed via thermal spraying and / or cold spraying to further reduce the thickness of the barrier canister, thereby enabling the barrier canister or shield to induce less eddy current loss and / or allowing for a reduction in the size of the magnetic coupling elements.

[0259] High-voltage magnetic coupling shield and its manufacturing method

[0260] Figure 19 Another example shield 1900 is shown (e.g., a barrier tank), which can be used for a heat transfer bus pump 400 (e.g., Figure 4 Barrier tank 452) Figure 5 Pump system 500 (e.g., Figure 5 Barrier jar 536) Figure 6 Pump system 600 (e.g., Figure 6 Barrier jar 636) Figure 7 Pump system 700 (e.g., Figure 7 The barrier tank 728) and / or any other pumping system disclosed herein that uses a barrier tank or shield to contain fluid flow. Figure 19 In the example shown, the shield 1900 includes an outer shell layer 1902 (e.g., an outer layer) and an inner shell layer 1904 (e.g., a liner) attached to the outer shell layer 1902.

[0261] exist Figure 19In this design, the thickness of the outer shell layer 1902 is between 25 mils and 150 mils. The outer shell layer 1902 comprises a composite material to provide structural strength and withstand the stress encountered by the shield 1900. The composite material may include carbon fiber, graphite fiber, and / or epoxy resin. The epoxy resin may bond the fibers at a location and / or in a direction to increase the structural strength of the outer shell layer 1902. Furthermore, the outer shell layer 1902 can provide the structural strength of a metallic material with reduced weight. Moreover, the use of a composite material in the outer shell layer 1902, in contrast to a metallic material, improves (e.g., reduces) the eddy current losses encountered between the first magnetic coupler 450 and the second magnetic coupler 460. Advantageously, the reduced eddy current losses resulting from the use of the outer shell layer 1902 increase the maximum speed at which the magnetic couplers 450, 460 can operate while maintaining rotational interlocking, and improve the efficiency of torque transmission between the first magnetic couplers 450. Further, the reduced eddy current losses enable… Figure 4 The size of the first magnetic coupling element 450, the second magnetic coupling element 460, and / or the motor 410 can be reduced. Additionally, the reduced eddy current losses eliminate the need for a cooling jacket around the coupling housing 424, as the heat generated by the rotation of the first magnetic coupling element 450 and the second magnetic coupling element 460 is reduced.

[0262] exist Figure 19 In this configuration, carbon fibers and / or graphite fibers are positioned in more than one orientation, as discussed in further detail below. For example, the fibers may be positioned in a first orientation, a second orientation, a third orientation, and a fourth orientation, where the second orientation differs from the first orientation, the third orientation differs from both the first and second orientations, and the fourth orientation differs from all three. In some examples, the first orientation is located in the axial direction A defined by the shield 1900, and the second orientation is located in the circumferential direction C defined by the shield 1900. Therefore, the first and second orientations are substantially orthogonal. The third orientation may be approximately 45° to the first and second orientations in a first direction. The fourth orientation may be approximately 45° to the first and second orientations in a second direction substantially orthogonal to the first direction. Therefore, the third and fourth orientations are substantially orthogonal.

[0263] exist Figure 19 In the example shown, the composite material forming the outer shell layer 1902 is porous. Therefore, the inner shell layer 1904 covers the inner surface of the outer shell layer 1902 to prevent fluid from escaping through the pores of the outer shell layer 1902, and consequently, allows the shield 1900 to hermetically seal the front bearing housing 428 and prevent fluid contamination. The thickness of the inner shell layer 1904 can be as small as 2 mils. The inner shell layer 1904 comprises a thermoplastic composite material and / or a metallic material. In some examples, the inner shell layer 1904 includes... Advantageously, when the inner shell 1904 is only 5 mils thick, compared with The associated temperature and structural strength properties enable the shield 1900 to achieve 6,400 PSIA. Additionally, given... Excluding metal materials, This allows the inner shell 1904 to minimize or otherwise reduce eddy current losses caused by the shield 1900. In some examples, the inner shell 1904 includes, in addition to Other thermoplastic composite materials, such as polyetheretherketone (PEEK). In some examples, the inner shell 1904 comprises a nickel-based alloy to maximize or otherwise increase the pressure that the shield 1900 can withstand. For example, the inner shell 1904 may comprise a nickel-chromium-based alloy, such as a nickel-chromium-molybdenum alloy (e.g., INCO718).

[0264] exist Figure 19 In this process, the outer shell layer 1902 is formed via a composite layup process. For example, the composite layup process may include laying composite layers layer by layer, such that a first composite layer of the outer shell layer 1902 is formed on a second composite layer, a second composite layer is formed on a third composite layer, and so on. Therefore, the composite layers comprise carbon fibers and / or graphite fibers in an epoxy resin. The carbon fibers and / or graphite fibers are laminated with the epoxy resin at certain locations and / or orientations, and thermosetting can be used to allow the epoxy resin to bond the fibers in place. Specifically, the fibers are laminated on top of each other in a first, second, third, and fourth orientation. For example, a first group of fibers may be positioned in the first orientation, a second group of fibers may be positioned in the second orientation on top of the first group of fibers (e.g., around a circumference defined by the first group of fibers), a third group of fibers may be positioned in the third orientation on top of the second group of fibers, and a fourth group of fibers may be positioned in the fourth orientation on top of the third group of fibers. Furthermore, the layers of the first, second, third, and fourth groups of fibers may be stacked such that the fibers define a certain thickness. For example, the thickness may be based on an associated pump (e.g., Figure 4 The heat transfer bus pump 400 will operate at the pressure. Additionally, multiple groups of fibers can be stacked in another arrangement or in multiple arrangements. For example, the outer shell layer 1902 may include a third group of fibers stacked on top of the first group of fibers, a second group of fibers stacked on top of the third group of fibers, and a fourth group of fibers stacked on top of the second group of fibers. Further, the multiple groups of fibers in the first group may be stacked in a different arrangement than the multiple groups of fibers in the second group positioned around the first group. Additionally, the inner shell layer 1904 may include short fibers for structural reinforcement.

[0265] Therefore, the outer shell layer 1902 can be formed via a composite layup process, such that the outer shell layer 1902 includes a first thickness. In some examples, the inner surface 1905 of the outer shell layer 1902 can be machined downwards to give the outer shell layer 1902 a second thickness, which provides space for the inner shell layer 1904 while maintaining the shield 1900 within a certain thickness range. In some examples, the thickness of the outer shell layer 1902 can be as high as 0.125 inches.

[0266] exist Figure 19 In this process, when the inner shell 1904 is to include a nickel-based alloy, the inner shell 1904 is formed on the inner surface 1905 of the outer shell 1902 by electroforming. For example, when the inner shell 1904 is to include... Or, in the case of another thermoplastic composite material (e.g., PEEK), the inner shell 1904 can be via... Alternatively, a PEEK machining rod may be formed. Furthermore, the outer shell layer 1902 may be laminated onto the outer surface 1907 of the inner shell layer 1904. In some examples, the flange portion 1906 of the shield 1900 is formed entirely via the outer shell layer 1902.

[0267] Figure 20A -D indicates Figure 19 Example orientation of the fibers in the outer shell layer 1902. Figure 20A In -D, the composite layer can be laid layer by layer along direction 2001, where direction 2001 is perpendicular to... Figure 19 The inner composite layer of the inner shell 1904 and / or the outer shell 1902.

[0268] Figure 20A An example first fiber (e.g., a first set of fibers) of the outer shell layer 1902 positioned on the first orientation 2002 is shown, the first orientation 2002 being along the direction of the outer shell layer 1902. Figure 19 The protective shield 1900 extends in the circumferential direction C defined by it. Therefore, the fibers in the first fiber circumferentially surround the shield. Figure 19 The shroud 1900 defines the cavity. Further, the fibers in the first fiber travel along the... Figure 19 The protective cover is spaced apart in the axial direction A defined by 1900.

[0269] Figure 20B An example of a second fiber (e.g., a second set of fibers) is shown positioned on a shell layer 1902 in a second orientation 2004, the second orientation 2004 being along the direction of the outer shell layer 1902. Figure 19 The shield 1900 extends in the axial direction A defined by the shield. Therefore, the second fiber extends in the axial direction A and surrounds the shield. Figure 19The rear end of the cavity defined by the shield 1900. In other words, the second fiber surrounds the cavity in a U-shape. Therefore, the second orientation 2004 is substantially orthogonal to the first orientation 2002. Furthermore, the fibers in the second fiber are spaced apart along the circumferential direction C defined by the shield 1900. Thus, the corresponding ends of the fibers in the second fiber are directly positioned opposite each other across the cavity of the shield 1900 (e.g., at 180° to each other).

[0270] Figure 20C An example third fiber (e.g., a third set of fibers) is shown positioned on a shell layer 1902 in a third orientation 2006, which extends approximately 45° between the first orientation 2002 and the second orientation 2004 in a first direction. Therefore, the third fiber is positioned on a shell layer 1902 in a third orientation 2006. Figure 19 The protective shield 1900 extends in both the axial direction A and the circumferential direction C. In other words, the third fiber surrounds the shield in a rectangular shape. Figure 19 The cavity defined by the 1900 shield. Furthermore, the fibers in the third fiber run along the... Figure 19 The protective cover is spaced apart in the axial direction A defined by 1900.

[0271] Figure 20D An example fourth fiber (e.g., a fourth group of fibers) is shown positioned on a fourth orientation 2008, which extends approximately 45° in a second direction between the first and second orientations. Specifically, the fourth orientation 2008 is substantially orthogonal to the third orientation 2006. That is, the fourth orientation 2008 is positioned on a third orientation 2006. Figure 19 The protective shield 1900 extends in both the axial direction A and the circumferential direction C. Therefore, the fourth fiber surrounds the shield in a rectangular shape. Figure 19 The cavity defined by the 1900 shield. Furthermore, the fibers in the fourth fiber run along the... Figure 19 The protective cover is spaced apart in the axial direction A defined by 1900.

[0272] Figure 21 It shows that in such Figure 19 An example cover layer of carbon fibers and / or graphite fibers positioned on the first orientation 2002, the second orientation 2004, the third orientation 2006, and the fourth orientation 2008 in a portion 1908 of the outer shell layer 1902 identified in the diagram. Figure 21 In the outer shell layer 1902, there are first fibers 2102 on a first orientation 2002, second fibers 2104 on a second orientation 2004, third fibers 2106 on a third orientation 2006, and fourth fibers 2108 on a fourth orientation 2008. Specifically, the first fibers 2102 surround the outer shell layer 1902. Figure 19 The cavity defined by the shield 1900 extends in the circumferential direction C. Further, the second fiber 2104 is formed by... Figure 19The protective cover 1900 extends substantially orthogonally to the first fiber 2102 in the axial direction A defined by the cover 1900. The third fiber 2106 extends at approximately 45° between the first fiber 2102 and the second fiber 2104. Furthermore, the fourth fiber 2108 extends substantially orthogonally to the third fiber 2106.

[0273] Figure 22A This indicates the manufacture of barrier containers (such as...) Figure 19 A flowchart of the first example method 2200 of the shield 1900 is provided. In some examples, at least a portion of the example method 2200 represents example machine-readable instructions that can be executed and / or instantiated by processor circuitry communicating with manufacturing equipment to manufacture the shield 1900. Additionally or alternatively, Figure 22A Method 2200 may use application-specific integrated circuits (ASICs) and / or field-programmable gate arrays (FPGAs), which are configured such that the manufacturing operations corresponding to method 2200 are performed by manufacturing equipment.

[0274] Figure 22A Example method 2200 begins at box 2202, where the outer shell layer 1902 is formed. Figure 19-21 For example, the outer shell layer 1902 can be formed via a composite lay-up process and / or a thermosetting process. Specifically, in the epoxy resin, the first fiber 2102 ( Figure 21 ) was positioned in the first orientation 2002 ( Figure 20A and 21 On the second fiber 2104 () Figure 21 ) was positioned in the second orientation 2004 ( Figure 20B and 21 On the first fiber 2002, the second orientation 2004 is basically orthogonal to the first orientation 2002, and the third fiber 2106 ( Figure 21 ) was located in the third orientation 2006 ( Figure 20C and 21 On, and the fourth fiber 2108 ( Figure 21 It was positioned in the fourth orientation 2008 ( Figure 20D and 21 Furthermore, the first fiber 2102, the second fiber 2104, the third fiber 2106, and the fourth fiber 2108 may alternate in the respective layers. These layers further define the thickness of the outer shell layer 1902. In some examples, the respective layers of fibers 2102, 2104, 2106, and 2108 may be thermosetting, such that the epoxy resin holds the fibers 2102, 2104, 2106, and 2108 on their respective orientations 2002, 2004, 2006, and 2008.

[0275] At box 2204, the inner surface of the outer shell layer 1902 is machined. For example, the inner surface of the outer shell layer 1902 can be ground or machined to reduce the thickness of the outer shell layer 1902. Therefore, machining the outer shell layer 1902 to a reduced thickness can reduce the thickness of the inner shell layer 1904. Figure 19 This provides space so that the second magnetic coupling element 460 does not contact the inner shell layer 1904.

[0276] At box 2206, an inner shell layer 1904 is formed on the inner surface of an outer shell layer 1902. For example, when the inner shell layer 1904 comprises a metallic material, it can be formed on the inner surface of the outer shell layer 1902 via electroforming. Further, when the inner shell layer 1904 comprises a thermoplastic composite material (such as...) When using (and / or PEEK), the inner shell layer 1904 can be formed on the inner surface of the outer shell layer 1902 via additive manufacturing. Therefore, forming the inner shell layer 1904 via additive manufacturing or electroforming allows the inner shell layer 1904 to have a reduced thickness, which is achieved by the shield 1900 (and / or PEEK). Figure 19 The defined cavity provides space for the second magnetic coupling element 460, while sealing the inner surface of the outer shell layer 1902.

[0277] Figure 22B This indicates the manufacture of barrier containers (such as...) Figure 19 A flowchart of a second example method 2250 for the shield 1900 is provided. In some examples, at least a portion of example method 2250 represents example machine-readable instructions that can be executed and / or instantiated by processor circuitry communicating with manufacturing equipment to manufacture the shield 1900. Additionally or alternatively, Figure 22B Method 2250 may use application-specific integrated circuits (ASICs) and / or field-programmable gate arrays (FPGAs), which are configured such that the manufacturing operations corresponding to method 2250 are performed by manufacturing equipment.

[0278] Figure 22B Example method 2250 begins at box 2252, where the inner shell 1904 is formed. Figure 19 For example, the inner shell 1904 can be obtained from... Alternatively, the rod may be made of another thermoplastic composite material (e.g., PEEK) and machined. In some examples, when the inner shell 1904 comprises a metallic material, the inner shell 1904 is electroformed onto the mandrel and subsequently separated from the mandrel.

[0279] At box 2254, outer shell layer 1902 ( Figure 19-21The outer shell layer 1902 is laminated onto the inner shell layer 1904. For example, the outer shell layer 1902 can be formed via a composite lay-up process. Specifically, the first layer of the outer shell layer 1902, comprising at least one set of fibers 2102, 2104, 2106, 2108, can be laminated onto the outer surface 1907 of the inner shell layer 1904. Figure 19 Furthermore, a second layer comprising at least one set of fibers 2102, 2104, 2106, 2108, of the outer shell layer 1902 may be laminated on the first layer. In some examples, the first layer is thermoset before the second layer is applied. Thus, the outer shell layer 1902 forms multiple layers on the inner shell layer 1904.

[0280] This document discloses an example layered magnetic coupling shield or barrier canister. The example layered magnetic coupling shield or barrier canister may include an outer shell layer to provide structural support capable of withstanding higher pressures (e.g., at least 6,400 PSI). Furthermore, the example layered magnetic coupling shield or barrier canister may include an inner shell layer formed on the inner surface of the outer shell layer to prevent fluid leakage through the pores of the outer shell layer. Advantageously, when used... When the inner shell 1904 is formed using another thermoplastic (e.g., PEEK), no eddy current losses occur. Furthermore, when the inner shell comprises a metallic material, the ratio of eddy current losses (in kilowatts (kW)) to the inner shell thickness (in mils (e.g., thousandths of an inch)) can be less than 0.06. As a result, the example layered magnetic coupling shield and / or barrier tank allows the magnetic coupling elements to maintain magnetic engagement and, consequently, be rotated and interlocked at higher angular velocities. Therefore, the example layered magnetic coupling shield or barrier tank allows the impeller in the associated pump to be driven at higher angular velocities to increase the pressure and / or flow rate of the fluid (e.g., a heat exchange fluid, such as a supercritical fluid (e.g., sCO2, etc.)), thereby enabling the fluid to transfer more thermal energy to and / or from the working fluid in the associated aircraft and / or engine.

[0281] Oil-lubricated supercritical fluid pump with oil separator

[0282] As described above, in order to transfer heat energy between a fluid (e.g., a heat exchange fluid, such as a supercritical fluid (e.g., sCO2, etc.)) and a working fluid without negatively impacting the components of the aircraft 10 and / or the gas turbine engine 100, the fluid should be free from contamination by foreign substances in the area where the fluid will transfer heat energy. That is, the fluid must be free from contamination by foreign substances in the area where it passes through the working fluid. Figure 2 The heat source heat exchanger 206 and the radiator heat exchanger 208 should not be contaminated by oil, water (e.g., steam) and / or ambient air.

[0283] As discussed above, the rolling element bearings 440, 448 supporting the shaft 438 of the motor 410 require non-fluid oil lubrication. Furthermore, Figure 4 The barrier tank 452 separates the fluid from the motor housing 412 to prevent contamination by the oil lubrication of the rolling element bearings 440, 448 in the pump 400. However, using separate housings, such as the motor housing 412, the rear bearing housing 418, the intermediate bearing housing 420, and the connecting housing 424, increases the size, weight, and / or cost of the pump 400. Furthermore, the rotation of the impeller 406 driven via the magnetic couplings 450, 460 can cause eddy current losses, which limit the rotational speed at which the magnetic couplings 450, 460 can drive the impeller 406.

[0284] This document discloses an example oil separator that enables a fluid to mix with and subsequently separate from oil. Thus, the example oil separator allows fluid to flow through an oil-lubricated bearing used to mount an electric motor shaft (e.g., Figure 4 The housing of shaft 438. As a result, the oil separator makes Figure 3 The size, weight, and / or cost of pump 204 are reduced. Additionally, the oil separator allows for a reduction in the number of components in pump 204. For example, by enabling fluid to mix with oil, the oil separator eliminates the barrier tank (e.g., [missing information]) that separates the oil-lubricated parts from the fluid. Figure 4 Barrier tank 452), magnetic coupling element (e.g., Figure 4 The magnetic coupling elements (450, 460) and / or different housings are required. Furthermore, the example oil separator enables pump 204 to drive the impeller without the magnetic coupling element, which increases the rotational speed at which the impeller can operate, thereby increasing the maximum pressure and / or flow rate at which pump 204 can drive fluid through heat transfer bus 202.

[0285] Specifically, the example pump system for a fluid (e.g., a heat exchange fluid, such as a supercritical fluid (e.g., sCO2, etc.)) within a pressurized closed-loop transmission bus (e.g., heat transfer bus 202) includes a pump housing and piping fluidly connected to the pump housing. During operation of the example pump system, a first section of the piping comprises a mixture of oil and the supercritical fluid (e.g., supercritical carbon dioxide), and a second section of the piping comprises the supercritical fluid itself. Therefore, a separator (e.g., an oil separator) is positioned in a third section of the piping between the first and second sections, such that the separator can separate the oil from the supercritical fluid in the mixture. Thus, the separator allows the supercritical fluid to flow within the pump housing and mix with oil from lubricating bearings, for example, the shaft of the motor that mounts and / or supports the drive impeller.

[0286] In some examples, the pump system includes more than one separator. Example separators can be static (e.g., stationary) or dynamic (e.g., movable, rotatable, etc.). In some examples, a dynamic or rotatable separator includes a rotatable shaft and impellers or ridges extending radially outward from the rotatable shaft. In some examples, a rotatable separator includes a rotatable conical shell. In some such examples, the conical shell includes an open axial end and a slot facing the surrounding pipe. In some examples, the conical shell is positioned about the rotatable shaft. In some such examples, the rotatable shaft can rotate in a first direction, and the conical shell can be stationary or rotate in a second direction opposite to the first direction.

[0287] Therefore, as the impeller and / or conical shell rotate, oil molecules in the mixture experience more centrifugal force than supercritical fluid particles because oil has a higher density compared to supercritical fluid. Consequently, the greater centrifugal force causes oil particles to adhere to the inner surface of the shell, to the surrounding pipes, to be driven through the pores in the shell, and / or to be driven through the oil recirculation flow path, which guides the oil back to pump 204 or the oil supply unit (e.g., the oil tank). Furthermore, the reduced centrifugal force encountered by the supercritical fluid particles as the oil is driven radially outward allows the supercritical fluid to flow in the middle section of the pipe and / or through the conical shell.

[0288] In some examples, the static or stationary separator includes an oil-absorbing material. For example, the oil-absorbing material may include polymers (e.g., polyurethane, polypropylene, polyethylene, cross-linked polymers, etc.) and / or powders (e.g., talc, aluminum starch, rice starch, silica, etc.). In some examples, the stationary separator includes baffles that eliminate or otherwise reduce any straight flow path of the supercritical fluid through a third part of the conduit. Specifically, the baffles include oil-absorbing material. As a result, the baffles bring oil particles mixed with the supercritical fluid into contact with the stationary separator and are subsequently absorbed by the oil-absorbing material. Thus, the stationary separator acts as a filter that collects oil and allows the supercritical fluid to pass through it. Furthermore, the higher density of the oil and the pressure of the fluid flowing through the stationary separator cause the oil to fall through the pores (e.g., pore channels) in the baffles, allowing oil particles to enter the oil recirculation flow path.

[0289] The baffle can be formed in various shapes with different thicknesses and / or porosities to allow for control of the pressure drop encountered by the supercritical fluid in the third section of the pipe. In some examples, the baffle structure can be formed from sheet metal and / or via additive manufacturing. Example static separators can be installed horizontally or vertically in the third section of the pipe.

[0290] In some examples, the static oil separator includes a first conduit (e.g., a main conduit) fluidly connected to a second conduit (e.g., an oil collection conduit) positioned below the first conduit. In some examples, the second conduit is fluidly connected to the first conduit at multiple different locations. Because oil has a higher density than supercritical fluid, it can flow from the first conduit into the second conduit. Further, the first conduit may include a baffle that causes the mixture of supercritical fluid and oil to flow downwards at the point where the first conduit is fluidly connected to the second conduit. The downward velocity and higher density of the oil cause oil particles to fall from the first conduit into the second conduit. Further, the baffle formed by the first conduit can cause the mixture to flow upwards towards the connection point between the conduits, causing the first conduit to change the fluid velocity in the mixture from downward to upward. Therefore, because supercritical fluid has a lower density, it is easier for it to change from downward to upward velocity. As a result, the oil content in the first conduit decreases at each connection point where the first conduit is fluidly connected to the second conduit. Furthermore, the oil can be completely separated from the supercritical fluid in the first pipe at or before the final connection point between the pipes. Additionally, the second pipe can form an oil recirculation flow path or be fluidly connected to an oil recirculation flow path.

[0291] Figure 23 An example pump system 2300 is shown, which includes a first example separator 2302 (e.g., a first static separator, cartridge filter, etc.) to separate a supercritical fluid (e.g., supercritical carbon dioxide) from oil in a conduit 2304 (e.g., an exhaust conduit). The supercritical fluid is driven through the conduit 2304 (e.g., at the inlet of the exhaust conduit). Figure 2 (Prior to the heat transfer bus 202 or within the heat transfer bus 202 prior to heat exchangers 206 and 208). Figure 23 In the example shown, the pump system 2300 includes a pump housing 2306. Specifically, the pump housing 2306 is formed by an electric motor housing 2308, a back plate 2310, and a compressor collector 2312, which are connected together via bolts 2314. The pump housing 2306 further includes a cover 2316, which is fixedly connected to the rear end of the electric motor housing 2308 via bolts 2318. The pump housing 2306 is fluidly connected to a conduit 2304, allowing fluid to flow through the electric motor housing 2308, the back plate 2310, the compressor collector 2312, and the conduit 2304.

[0292] exist Figure 23 In the example shown, the pump system 2300 includes a motor 2320, which is positioned within a motor housing 2308. Figure 23In this configuration, the rotor 2322 of the electric motor 2320 is fixed to the shaft 2324 (e.g., the motor shaft). Therefore, the electric motor 2320 drives the rotation of the shaft 2324. The pump system 2300 further includes a cooling jacket 2315 surrounding the motor housing 2308 to prevent the electric motor 2320 from overheating.

[0293] Shaft 2324 is supported by a first rolling element bearing 2325 (e.g., a rear rolling element bearing) and a second rolling element bearing 2327 (e.g., a front rolling element bearing), both of which are lubricated with oil. Figure 23 In the example shown, the oil lubricating the first rolling element bearing 2325 and the second rolling element bearing 2327 is mixed with additives. Specifically, the additives increase the viscosity of the oil, thereby improving the cohesive and adhesive properties associated with the oil.

[0294] exist Figure 23 In the example shown, the rear end of shaft 2324 extends beyond the rear end of motor housing 2308. Therefore, cover 2316 includes a notch or cavity 2317 in which the rear end of shaft 2324 is disposed. A first rolling element bearing 2325 is positioned within a bearing cup 2326 disposed within motor housing 2308. Specifically, bearing cup 2326 can be press-fitted into bearing housing 2326 and is supported by a shoulder 2328 of motor housing 2308. To aid in interlocking the first rolling element bearing 2325 onto shaft 2324, the first rolling element bearing 2325 includes a clamp 2330 extending from the rear side of the first rolling element bearing 2325 and clamping around shaft 2324. Additionally, a preloaded spring 2332 is positioned between bearing cup 2326 and the front side of the first rolling element bearing 2325 to help maintain the position of the first rolling element bearing 2325 within bearing cup 2326. Furthermore, the sub-cap 2334 is connected to the rear end of the bearing cup 2326 via screws 2336. Therefore, the sub-cap 2334 includes an opening through which the shaft 2324 extends.

[0295] The second rolling element bearing 2327 is press-fitted in the back plate 2310. To maintain the position of the second rolling element bearing 2327 on the shaft 2324, the second rolling element bearing 2327 includes a clamp 2337 extending from the front side of the second rolling element bearing 2327 and clamping around the shaft 2324. The rear end of the second rolling element bearing 2327 is positioned against the shoulder 2338 of the back plate 2310 and the ridge 2339 in the shaft 2324.

[0296] exist Figure 23In the example shown, impeller 2340 is coupled to the front end of shaft 2324 such that impeller 2340 rotates together with shaft 2324 to pump fluid through pipe 2304. Specifically, to coupled impeller 2340 to shaft 2324, a portion of the rear end of impeller 2340 is wedged into and secured to an internal groove in shaft 2324. Alternatively, the rear end of impeller 2340 may include a groove, and shaft 2324 may extend into the groove of impeller 2340 to rotatably connect shaft 2324 and impeller 2340. Additionally, the rear end of impeller 2340 is coupled to support plate 2342. In some examples, support plate 2342 is screwed to shaft 2324 to further increase the connection strength between impeller 2340 and shaft 2324.

[0297] Therefore, both the impeller 2340 and the rotor 2322 of the motor 2320 are mounted on the shaft 2324. As a result, the size of the pump system 2300 and / or the number of components used to drive the impeller 2340 are minimized or otherwise reduced. Furthermore, the output of the pump system 2300 (e.g., the output pressure and / or flow rate of the fluid leaving the pump system 2300) can be increased because the rotation of the impeller 2340 is independent of the magnetic coupling elements that encounter increased eddy current losses at higher speeds.

[0298] During operation, a supercritical fluid (e.g., sCO2, etc.) flows through the inlet 2344 of the pump system 2300 and is driven by the impeller 2340. Specifically, the impeller 2340 drives the supercritical fluid toward the conduit 2304. When the supercritical fluid encounters higher pressure, a portion of the supercritical fluid escapes into the motor housing 2308. For example, the supercritical fluid may flow between the support plate 2342 and the back plate 2310. Furthermore, the supercritical fluid may pass through the second rolling element bearing 2327, where it mixes with the oil lubricating the second rolling element bearing 2327 before dispersing throughout the motor housing 2308. Thus, the supercritical fluid can further mix with the oil lubricating the first rolling element bearing 2325. As a result, a mixture of supercritical fluid and oil is formed in the motor housing 2308. Moreover, as the supercritical fluid continues to flow into the motor housing 2308, the pressure increases, and the mixture is pushed back into the compressor collector 2312. In some examples, the mixture flows through a groove 2345 in shaft 2324, which aligns with a groove 2346 in impeller 2340, so that the mixture can flow into compressor collector 2312 and be driven into pipe 2304 by impeller 2340. Additionally or alternatively, the mixture may flow into compressor collector 2312 between support plate 2342 and back plate 2310.

[0299] exist Figure 23In response to being pumped into pipe 2304, the mixture of supercritical fluid and oil encounters the first separator 2302. Figure 23 In this design, separator 2302 is a cartridge filter comprising an inner cylinder 2347 and an outer cylinder 2348. Specifically, the first separator 2302 comprises interconnected concentric cylinders 2347 and 2348, at least partially formed of an oil-absorbing material. In some examples, the oil-absorbing material comprises at least one powder, such as talc, aluminum starch, rice starch, silica, etc. In some examples, the oil-absorbing material comprises at least one polymer, such as polyurethane, polypropylene, polyethylene, cross-linked polymer, etc. The inner cylinder 2347 and outer cylinder 2348 may include baffles to increase the rate at which oil in the mixture contacts the surface of separator 2302. For example, separator 2302 is manufactured via sheet metal forming and / or additive manufacturing.

[0300] In some examples, separator 2302 includes a first conduit and a second conduit. For example, the first conduit may be positioned above and fluidly connected to the second fluid conduit. Furthermore, the first fluid conduit may include a baffle, and the second fluid conduit may include an oil-absorbing material, as discussed in further detail below.

[0301] In some examples, the first separator 2302 includes separate cylindrical filters positioned in series or parallel within the conduit 2304. For example, the first separator 2302 may include a first cylindrical filter positioned above a second cylindrical filter.

[0302] As the mixture of supercritical fluid and oil flows through separator 2302, separator 2302 absorbs the oil. Consequently, pipe 2304 carries only the supercritical fluid into heat transfer bus 202. Figure 1 In this configuration, the rear end of separator 2302 is positioned against plate 2350. Specifically, plate 2350 includes a recess in which separator 2302 is positioned. Further, plate 2350 is connected to the exterior of motor housing 2308 via one or more bolts 2352. Additionally or alternatively, plate 2350 may be connected to conduit 2304. When operation of pump system 2300 is stopped or paused, plate 2350 can be removed to allow cleaning and / or replacement of separator 2302.

[0303] Furthermore, the oil separated from the supercritical fluid by the first separator 2302 can fall into a secondary conduit 2354 (e.g., an oil collection conduit), which is located below the first separator 2302. The secondary conduit 2354 is in fluid connection to an inlet 2356 in the motor housing 2308. Thus, the oil can return to the motor housing 2308, thereby providing lubrication for the first and second rolling element bearings 2325, 2327.

[0304] As a result, the first separator 2302 allows the supercritical fluid to mix with the oil without affecting the supercritical fluid's heat transfer capability. Consequently, the number of components in the pump system 2300, the size of the pump system 2300, and / or the cost of the pump system 2300 can be minimized or otherwise reduced. Furthermore, the first separator 2302 enables the motor 2320 to directly drive the impeller 2340 via the shaft 2324, allowing the impeller 2340 to operate at a higher rotational speed, thereby increasing the pressure and / or flow rate of the supercritical fluid driven through the heat transfer bus 202. Therefore, the first separator 2302 can increase the rate at which the supercritical fluid will be transferred through the heat transfer bus, thereby increasing the rate of heat transfer between the supercritical fluid and the working fluid.

[0305] Figure 24 Another example pump system 2400 is shown, which includes a second example separator 2402 (e.g., a second static separator, a cone filter, etc.). Figure 24 In the middle, the second separator 2402 includes a tapered geometry instead of Figure 23 The first separator 2302 has an oil-absorbing material with a cylindrical geometry. Depending on the position of the heat transfer bus 202 relative to the pipe 2304, the second separator 2402 can be positioned horizontally or vertically within the pipe 2304. Figure 2 In order to maintain the position of the second separator 2402, the flange 2404 of the second separator 2402 is press-fitted into the conduit 2304. Alternatively, the second separator 2402 may be connected to the conduit 2304 via screws and / or any other means for connection.

[0306] exist Figure 24 In response to the mixing of supercritical fluid with oil lubricating the first and second rolling element bearings 2325, 2327 in the motor housing 2308, impeller 2340 drives the mixture through a second separator 2402. The second separator 2402 absorbs the oil in the mixture while allowing the supercritical fluid to enter the heat transfer bus 202. Therefore, the second separator 2402 enables conduit 2304 to supply only supercritical fluid to the heat transfer bus 202, even though the supercritical fluid was previously contaminated by oil from the first and second rolling element bearings 2325, 2327.

[0307] and Figure 23Similar to the first example separator 2302, the second separator 2402 includes a baffle over which the mixture flows. Therefore, the baffle prevents the mixture from having a straight flow path through the second separator 2402, thereby ensuring that the oil in the mixture contacts the oil-absorbing material in the baffle. In some examples, an oil collection conduit is positioned below the second separator 2402 so that the oil can return to the oil supply section and / or the motor housing 2308 via inlet 2356 in the motor housing 2308. Specifically, the density of the oil causes it to fall through the baffle in the second separator 2402 and enter the oil collection conduit, as discussed in further detail below.

[0308] Figure 25 Another example pump system 2500 is shown, which includes a second example separator 2402 and a third example separator 2502 (e.g., a dynamic separator, a rotary separator, a cyclone separator, etc.) positioned in a conduit 2304. Figure 25 In this configuration, the third separator 2502 is positioned in series with the second separator 2402 in the conduit 2304. Specifically, the third separator 2502 is positioned upstream (e.g., forward) of the second separator 2402 in the conduit 2304, thereby encountering the mixture of supercritical fluid and oil before the second separator 2402.

[0309] exist Figure 25 In this configuration, the third separator 2502 includes a motor 2504 and a hydrocyclone 2506. Further, the hydrocyclone 2506 is mounted on a rolling element bearing 2508 connected to the conduit 2304. In some examples, the rolling element bearing 2508 includes a solid lubricant (e.g., silver coating, graphite, molybdenum disulfide, etc.) to avoid adding oil to the mixture. In some examples, the hydrocyclone 2506 is mounted via a foil bearing or any other bearing that allows the hydrocyclone to rotate without the use of lubricant.

[0310] Therefore, the motor 2504 drives the rotation of the hydrocyclone 2506. The rotation of the hydrocyclone 2506 then causes the oil droplets in the mixture to encounter centrifugal force. Specifically, because oil has a higher density than supercritical fluid, the rotation of the hydrocyclone 2506 causes the oil droplets in the mixture to encounter increased centrifugal force compared to supercritical fluid. Furthermore, the hydrocyclone 2506 includes holes or orifices facing the periphery of the pipe 2304, as discussed in further detail below. As a result, the third separator 2502 causes the oil droplets to move towards the inner surface of the hydrocyclone 2506 and / or the periphery of the pipe 2304, while the supercritical fluid remains within the middle portion of the pipe 2304. Furthermore, the third separator 2502 can cause the oil droplets to adhere to the inner surface of the pipe 2304. In some examples, the oil droplets contact and lubricate the rolling element bearing 2508. In some examples, the third separator 2502 is implemented in the pipe 2304 without the second separator 2402. In this example, the third separator 2502 removes the oil itself from the mixture.

[0311] exist Figure 25 In the process, oil droplets advancing through the third separator 2502 in pipe 2304 are absorbed by the second separator 2402. Advantageously, the shape of the second separator 2402 facing the periphery of pipe 2304 provides a larger surface area for the oil-absorbing material. Therefore, the higher centrifugal force encountered by the oil droplets drives them into the outer portion 2510 of the second separator 2402, which is larger than the tip portion 2512 of the second separator 2402. As a result, the tip portion 2512 remains relatively unobstructed, which reduces the influence of the second separator 2402 on the flow properties of the supercritical fluid when it enters the heat transfer bus 202.

[0312] Figure 26 Another example pump system 2600 is shown, which includes a second example separator 2402. Additionally or alternatively, the pump system 2600 may include a first separator 1902 and / or a third separator 2502. Figure 26 In this system, pump system 2600 includes a first shaft 2602 (e.g., a motor shaft) connected to the rotor 2322 of motor 2320. The first shaft 2602 is mounted in the motor housing via a first rolling element bearing 2325 and a second rolling element bearing 2604 (e.g., an intermediate rolling element bearing). Figure 26 In the middle, the second rolling element bearing 2604 is positioned in the bearing cage 2606, and the bearing cage 2606 is fixed inside the motor housing 2308.

[0313] Further, the pump system 2600 includes a carrier shaft 2608, which is coupled to the front end of a first shaft 2602 extending through a second rolling element bearing 2604. Specifically, the rear end of the carrier shaft 2608 is concentrically positioned about the front end of the first shaft 2602. The carrier shaft 2608 may be coupled to the first shaft 2602 via a clamp, press fit, or any other means for coupling. Further, the front end of the carrier shaft 2608 extends through a gearbox 2609 (e.g., a planetary gearbox). The gearbox 2609 includes the carrier shaft 2608, planetary gears 2610, ring gears 2612, and sun gears 2614, as coupled... Figure 27 Further discussion is needed.

[0314] A support shaft 2608 extends radially outward from the first shaft 2602 and is rotatably connected to a planetary gear 2610 of a gearbox 2609. Therefore, the support shaft 2608 drives the rotation of the planetary gear 2610, which in turn causes the sun gear 2614 to rotate. Furthermore, a ring gear 2612 enables the planetary gear 2610 to transmit greater torque to the sun gear 2614. The ring gear 2612 is fixedly positioned within the motor housing 2308. For example, the ring gear 2612 may be integral with the motor housing 2308 or connected to the motor housing 2308 via press-fit, screws, or any other means of connection.

[0315] The sun gear 2614 is defined in the rear end of a second shaft 2616 (e.g., an impeller shaft), which is coupled to the impeller 2340. Figure 26 In this configuration, the second shaft 2616 is supported by a third rolling element bearing 2618 (e.g., a front rolling element bearing) positioned in the back plate 2310. For example, the third rolling element bearing 2618 may be clamped onto the second shaft 2616 and connected to the back plate 2310 via a press fit.

[0316] Therefore, the planetary gear 2610 drives the rotation of the impeller 2340. As a result, the bearing shaft 2608, planetary gear 2610, ring gear 2612, and sun gear 2614 provide gear reduction, which allows the impeller 2340 to be driven at a higher rotational speed than the first shaft 2602. Furthermore, the gearbox 2609 enables an increase in the flow rate output and / or pressure output of the pump system 2600, thereby improving the heat transfer between the supercritical fluid and the working fluid. Further, when the second separator 2402 and / or the first separator 2302 and / or the third separator 2502 are implemented in the pump system 2600, magnetic coupling elements can be avoided while still using rolling element bearings 2325, 2604, 2618, and consequently, the gearbox 2609 can provide gear reduction that allows the impeller 2340 to operate at a higher angular velocity.

[0317] Figure 27 It shows Figure 26 The cross-section AA of gearbox 2609. Figure 27 In this configuration, the support shaft 2608 is connected to the planetary gear 2610 via a corresponding bracket 2702 and a ring 2704, which are rotatably connected to the inner circumference of the planetary gear 2610. Therefore, the bracket 2702 and ring 2704 cause the planetary gear 2610 to rotate about the sun gear 2614. Furthermore, the planetary gear 2610 is rotatable relative to the corresponding ring 2704. Thus, while the support shaft 2608 causes the planetary gear 2610 to rotate about the sun gear 2614, the ring gear 2612 causes the planetary gear 2610 to rotate relative to the corresponding ring 2704. Figure 27 In this configuration, the ring gear 2612 is fixedly coupled to the inner surface of the motor housing 2308, so that it does not rotate within the motor housing 2308. For example, the ring gear 2612 may be fixed within the motor housing 2308 via press fit, screws, or any other means for coupling.

[0318] In some examples, the support 2702 and ring 2704 may be rotatably coupled to the bearing shaft 2608, and further, fixedly coupled to the planetary gear 2610. In this example, as the bearing shaft 2608 causes the planetary gear 2610 to move about the sun gear 2614, the support 2702 and ring 2704 rotate together with the planetary gear 2610.

[0319] During operation, Figure 26 The rotor 2322 of the electric motor 2320 drives the rotation of the first shaft 2602. Further, the first shaft 2602 drives the rotation of the bearing shaft 2608, which in turn causes the planetary gear 2610 to rotate. In turn, the planetary gear 2610 causes the sun gear 2614 to rotate. Furthermore, the engagement between the planetary gear 2610 and the ring gear 2612 allows the planetary gear 2610 to transmit more torque to the sun gear 2614 without slippage. Therefore, the gearbox 2609 enables... Figure 26 The impeller 2340 can rotate at a greater speed due to the gear reduction provided by the gearbox 2609.

[0320] Figure 28 Another example pump system 2800 is shown, which includes a second example separator 2402. Additionally or alternatively, pump system 2600 may include a first separator 2302 and / or a third separator 2502. Figure 28 In the pump system 2800, there are first bearing assembly 2802 and second bearing assembly 2804 to support shaft 2324 that drives the rotation of impeller 2340.

[0321] A first bearing assembly 2802 is positioned within a bearing cup 2326 and, consequently, supports the rear portion of the shaft 2324. The first bearing assembly 2802 includes a damper 2806 (e.g., a squeeze film damper) and a first rolling element bearing 2808 positioned between the damper 2806 and the shaft 2324. Specifically, the damper 2806 includes an outer ring 2810 coupled to the bearing cup 2326. For example, the outer ring 2810 may be coupled to the bearing cup 2326 via a press fit, screws, and / or any other means for coupling. Further, the damper 2806 includes an inner ring 2812 and a piston ring 2814 positioned between the outer ring 2810 and the inner ring 2812. Specifically, the piston ring 2814 includes a squeeze film to dampen movement of the inner ring 2812 relative to the outer ring 2810. Furthermore, the inner ring 2812 defines the outer portion of the first rolling element bearing 2808, which is connected to the shaft 2324. Additionally, the inner portion of the first rolling element bearing 2808 can be connected to the shaft 2324 via a clamp 2813 extending from the rear side of the first rolling element bearing 2808. Furthermore, the first rolling element bearing 2808 can be supported within the bearing cup 2326 via a preloaded disc spring 2815.

[0322] The second bearing assembly 2804 is positioned in a back plate 2817 connected to the motor housing 2308. The second bearing assembly 2804 includes a spring finger 2816, a squirrel cage 2818, and a second rolling element bearing 2820. Figure 28 In this configuration, the cylindrical rolling element of the cage portion 2818 contacts and thus supports the shaft 2324. Furthermore, a spring finger 2816 is connected to the back plate 2817 and the non-rotating portion of the cage portion 2818. Therefore, the spring finger 2816 provides damping for the non-rotating movement of the shaft 2324. A second rolling element bearing 2820 is positioned behind the cage portion 2818. Specifically, the non-rotating portion of the second rolling element bearing 2820 (e.g., the outer portion of the second rolling element bearing 2820) is connected to the non-rotating portion of the cage portion 2818. For example, the cage portion 2818 may be connected to the second rolling element bearing 2820 via a press fit, screws, and / or any other means for connection.

[0323] As a result, the first bearing assembly 2802 and the second bearing assembly 2804 provide damping support for the rear portion and the front portion of the shaft 2324, respectively. Therefore, the first bearing assembly 2802 and the second bearing assembly 2804 reduce the vibrational movement of the shaft 2324 that might otherwise be caused when the rotor 2322 drives the shaft 2324 at a higher speed.

[0324] Figure 29 It is by Figure 28 A schematic representation of the supports provided by the first bearing assembly 2802 and the second bearing assembly 2804. Figure 29 In this configuration, a first bearing assembly 2802 supports a portion of a shaft 2324 located behind the motor 2320 with a first stiffness. Further, a second bearing assembly 2804 supports a portion of the shaft 2324 between the motor 2320 and the impeller 2340 with a second stiffness less than the first stiffness. Specifically, the first bearing assembly 2802 provides support with greater stiffness to stabilize the rear end of the shaft 2324. Further, the second bearing assembly 2804 provides support to the shaft 2324 with a smaller centripetal force to minimize or otherwise reduce the resistance caused by the second bearing assembly 2804 relative to the rotational speed of the shaft 2324. Therefore, the first bearing assembly 2802 can function as a stabilizer, while the second bearing assembly 2804 functions as a guide for the shaft 2324. Thus, the first bearing assembly 2802 and the second bearing assembly 2804 provide support that dampens non-rotational movement of the shaft 2324 while also reducing resistance to the rotational speed of the shaft 2324.

[0325] Figure 30A -C shows that it is possible to Figure 25 An example implementation of a rotary separator (e.g., a third separator 2502) implemented in the pump system 2500 and / or any other heat transfer pump system.

[0326] Figure 30A A first example rotary separator 3002 (e.g., a first hydrocyclone) is shown positioned in pipe 3003 (e.g., pipe 2304). Figure 25 The third separator 2502). Figure 30A In this process, pipe 3003 is fluidly connected to secondary pipe 3004, which in turn connects to the oil supply unit, as discussed in further detail below. Figure 30AIn this design, the first rotary separator 3002 includes a shaft 3006 and impellers 3008 extending radially outward from the shaft 3006. During operation of the first rotary separator 3002, an electric motor (e.g., motor 2504) can drive the rotation of the shaft 3006 and the impellers 3008. As a result, the impellers 3008 cause the oil 3010 (e.g., oil droplets) to encounter increased centrifugal forces compared to the supercritical fluid 3012 (e.g., supercritical carbon dioxide) flowing through the conduit 3003. Therefore, when the first rotary separator 3002 allows the supercritical fluid 3012 to flow through the middle portion of the conduit 2304, the rotation of the impellers 3008 causes the oil 3010 to move toward the periphery of the conduit 3003. Thus, the first rotary separator 3002 separates the oil 3010 from the flow of the supercritical fluid 3012. Furthermore, the first rotary separator 3002 causes at least a portion of the oil 3010 to move into the secondary conduit 3004, where the oil 3010 can be collected and / or recirculated to lubricate bearings, such as... Figure 23-26 And / or the first and second rolling element bearings 2325, 2327, 2808, 2820 of 28. In some examples, the rotational speed of the first rotary separator 3002 is based on the flow rate and / or the pressure within the conduit 3003.

[0327] Figure 30B A second example rotary separator 3020 (e.g., a second hydrocyclone, a conical hydrocyclone) is shown positioned in pipe 3003. Figure 25 (e.g., the third separator 2502). The second rotary separator 3020 is a rotatable cone with an orifice 3022. Specifically, the axial end of the second rotary separator 3020 is open to allow the supercritical fluid 3012 to flow through the middle portion of the pipe 3003. As the second rotary separator 3020 rotates, the higher density of the oil compared to the supercritical fluid 3012 causes the oil 3010 to encounter a greater centrifugal force. As a result, the second rotary separator 3020 removes the oil 3010 from the flow path of the supercritical fluid 3012. Specifically, when the supercritical fluid 3012 flows through the second rotary separator 3020, the increased centrifugal force can cause the oil 3010 to adhere to the second rotary separator 3020. Additionally or alternatively, when the supercritical fluid 3012 flows through the second rotary separator 3020, the swirling velocity generated by the orifice 3022 due to the rotation of the second rotary separator 3020 can cause the oil 3010 to flow through the orifice 3022 in the second rotary separator 3020 and adhere to the conduit 3003 and / or flow through the secondary conduit 3004.

[0328] The size and / or shape of the orifice 3022 can be based on the flow rate to be encountered in the conduit 3003, the pressure to be encountered in the conduit 3003, the rotational speed of the second rotary separator 3020, the position of the corresponding orifice 3022 relative to the inner surface of the conduit 3003, and / or the position of the orifice 3022 relative to the secondary conduit 3004. Additionally or alternatively, the rotational speed of the second rotary separator 3020 can be based on the flow rate encountered in the conduit 3003 and / or the pressure encountered within the conduit 3003. For example, the size of the orifice 3022, the shape of the orifice 3022, and / or the rotational speed of the second rotary separator 3020 can increase the centrifugal force and swirling velocity encountered by the oil 3010, making it more likely that the oil 3010 will be driven into the secondary conduit 3004. Figure 30A Similar to the first rotary separator 3002, the second rotary separator 3020 can be driven by an electric motor (e.g., electric motor 2504).

[0329] Figure 30C A third example rotary separator 3040 (e.g., a third hydrocyclone) is shown positioned in pipe 3003. Figure 25 The third rotary separator 3040 includes a shaft 3042, a helical impeller 3044 extending from the shaft 3042, and a conical shell 3046 positioned around the shaft 3042. Similar to the second rotary separator 3020, the conical shell 3046 includes a bore 3048. Figure 30C In this configuration, shaft 3042 and consequently helical blade 3044 are rotatable. In some examples, conical shell 3046 is stationary. In some examples, conical shell 3046 rotates in a direction opposite to the direction of rotation of shaft 3042. That is, shaft 3042 is capable of rotating in a first direction (e.g., clockwise), and conical shell 3046 can be stationary or rotate in a second direction opposite to the first direction (e.g., counterclockwise).

[0330] exist Figure 30CIn this process, the rotation of shaft 3042, helical impeller 3044, and / or conical shell 3046, along with the density of oil 3010 relative to supercritical fluid 3012, causes oil 3010 to encounter a first centrifugal force, which is greater than a second centrifugal force encountered by supercritical fluid 3012. Furthermore, the orifice 3048 in the conical shell 3046 causes oil 3010 to encounter a swirling velocity. Therefore, the swirling velocity allows oil 3010 to pass through the orifice 3048 at a greater speed and thus adhere to the conduit 3003 with greater force. In some examples, the swirling velocity encountered by oil 3010 increases the likelihood of oil 3010 entering the secondary conduit 3004. For example, the greater velocity of oil 3010 caused by the swirling velocity can enable oil 3010 to move through the secondary conduit 3004 at a faster rate. Specifically, the size, shape, and / or number of orifices 3048 can allow oil 3010 to be directly driven into the secondary conduit 3004 along its path. In addition, the swirling velocity is minimized or otherwise reduced to minimize the movement of oil 3010 caused by the flow of supercritical fluid 3012 in pipe 3003.

[0331] Figure 31A -C indicates that it is possible to... Figure 23-25 Example implementations of static separators (e.g., first separator 2302, second separator 2402) implemented in pump systems 2300, 2400, 2500 and / or any other heat transfer pump system.

[0332] Figure 31A At least a portion of a first example static separator 3102 (e.g., a first example filter, a first separator 2302, a second separator 2402) is shown. The first static separator 3102 includes a baffle 3104 that defines at least one flow path through the first static separator 3102. The baffle 3104 may be formed via a metal sheet and / or additive manufacturing. The baffle 3104 includes an oil-absorbing material 3105, such as polyurethane, polypropylene, polyethylene, crosslinked polymers, talc, aluminum starch, rice starch, and / or silica.

[0333] exist Figure 31A In the example shown, baffle 3104 defines a first flow path 3106A and a second flow path 3106B through which a mixture of supercritical fluid 3012 and oil 3010 can flow. Specifically, the first flow path 3106A is defined between the first baffle 3104A and the second baffle 3104B. Further, the second flow path 3106B is defined between the second baffle 3104B and a third baffle 3104C. Figure 31AIn this process, the first flow path 3106A is adjacent to the second flow path 3106B in the circumferential direction defined by the first static separator 3102. Alternatively or additionally, the first flow path 3106A may be adjacent to the second flow path 3106B in the radial direction defined by the first static separator 3102. When oil 3010 contacts the baffle 3104, as the supercritical fluid 3012 continues to flow between the baffles 3104, the oil-absorbing material 3105 of the baffles 3104 causes the oil 3010 to adhere to the baffles 3104.

[0334] In some examples, the weight of the oil 3010 ultimately causes it to fall off the baffle 3104. For instance, as the oil 3010 accumulates in the baffle 3104, it can fuse together, increasing its weight and consequently causing it to fall off the baffle 3104. Specifically, the oil-absorbing material 3105 of the baffle 3104 may include additives that are mixed with the oil to make the oil 3010 more viscous. Additionally or alternatively, rolling element bearings using oil may include additives that make the oil 3010 more viscous. Thus, the baffle 3104 can improve the cohesive and adhesive properties associated with the oil 3010, increasing the likelihood that oil droplets 3010 will bind together in response to contact with the baffle 3104.

[0335] Therefore, one or more pipes (e.g., secondary pipes 3004) fluidly connected to the oil supply section and / or the motor housing 2308 can be positioned below the baffle 3104 to allow the oil 3010 to be reused. Furthermore, the position of the pipes can be based on the geometry of the baffle 3104 so that oil 3010 exiting the baffle 3104 falls directly into the pipes. For example, gravity can cause oil 3010 to accumulate in the baffle 3104 at one or more lower height points, and thus, oil 3010 can drip into the pipes from these lower height points. Additionally or alternatively, one or more different portions of the baffle 3104 may include oil-absorbing material 3105, and thus, the position of the pipes can be based on the location of the portion of the baffle 3104 that includes the oil-absorbing material 3105 and thus collects the oil 3010.

[0336] In some examples, when oil 3010 is to be collected and held in the first static separator 3102 until the first static separator 3102 requires maintenance or replacement, the oil-absorbing material of the baffle 3104 does not include additives that make the oil 3010 more viscous. In this example, the baffle 3104 reduces the likelihood of an increase in the weight of the oil droplets 3010, thereby minimizing or otherwise reducing the likelihood of the oil droplets 3010 falling from the baffle 3104. Furthermore, to prevent oil 3010 from escaping from the first static separator 3102, the first static separator 3102 may include an increased number of circumferential layers defined by the baffle 3104. Thus, the outer circumferential layer defined by the baffle 3104 can capture oil 3010 that attempts to fall from the corresponding inner circumferential layer of the baffle 3104. Additionally or alternatively, the collection container may be positioned at least partially around the outermost layer of the baffle 3104 (e.g., around the bottom portion of the outermost layer) such that the collection container can capture oil 3010 that passes through and falls from the baffle 3104. Thus, the first static separator 3102 can prevent oil 3010 from escaping.

[0337] Figure 31B Another example implementation of the first static separator 3102 is shown. Figure 31B In the first static separator 3102, a baffle 3104 is included, which is vertically oriented rather than horizontally oriented, such as... Figure 31A As shown. Baffle 3104 forms a flow path 3107, which prevents oil 3010 from flowing through the first static separator 3102 without contacting the oil-absorbing material 3105. Therefore, when the mixture of supercritical fluid 3012 and oil 3010 flows between baffles 3104, the oil-absorbing material 3105 absorbs the oil 3010. Furthermore, the weight of the oil 3010 and the vertical orientation of the baffles 3104 allow the absorbed oil 3010 to be collected at the bottom portion 3110 of the baffles 3104. Therefore, the position where the oil 3010 will fall from the baffles 3104 is limited by the size of the bottom portion 3110 of the baffles 3104. Furthermore, an oil collection conduit (e.g., a secondary conduit 3004) can be positioned below the bottom portion 3110 of the baffles 3104 to collect the oil 3010 falling from the baffles 3104. Therefore, the collected oil 3010 can be redirected to the oil reservoir for storage and / or redirected to the motor housing 2308 for lubrication, as follows: Figure 35 The subject of discussion.

[0338] Figure 31CA second example static separator 3120 is shown (e.g., a second filter, a first separator 2302, a second separator 2402). The second static separator 3120 includes a baffle 3122 forming a primary flow path 3124. Further, the second static separator 3120 includes an oil collection conduit 3126 forming a secondary flow path 3128 below the baffle 3122. The secondary flow path 3128 can be connected to an oil supply unit and / or can recirculate oil 3010 back to the motor housing 2308, allowing oil 3010 to return to... Figure 23-26 And / or 28 rolling element bearings 2325, 2327, 2808, 2820, for lubrication via oil lines, as follows: Figure 35 The subject of discussion.

[0339] exist Figure 31C In this configuration, connector conduit 3130 connects the secondary flow path 3128 to the primary flow path 3124. In some examples, the oil collection conduit 3126 is directly connected to one or more of the lowest height points of the baffle 3122. In this example, the second static separator 3120 does not require connector conduit 3130 to connect the secondary flow path 3128 to the primary flow path 3124.

[0340] exist Figure 31C In this process, a mixture of supercritical fluid 3012 and oil 3010 enters the inlet 3132 of the primary flow path 3124. A first portion 3134 of the baffle 3122 causes the mixture to flow downwards. Further, a second portion 3136 of the baffle 3122 causes the mixture to change from downward flow to horizontal flow. The second portion 3136 of the baffle 3122 includes the lowest point of the corresponding baffle 3122, from which the connector conduit 3130 extends. Furthermore, compared to the supercritical fluid 3012, the gravity and higher density of the oil 3010 cause the oil 3010 to continue flowing downwards through the second portion 3136 of the baffle 3122, while the supercritical fluid 3012 changes to horizontal flow. As a result, the oil 3010 flows through the connector conduit 3130 and into the oil collection conduit 3126, allowing the oil 3010 to be collected and / or reused. Furthermore, the third portion 3138 of the baffle 3122 allows the supercritical fluid 3012, separated from the oil 3010, to flow upwards. Although Figure 31C The example shown uses four baffles 3122, but given the operating parameters of the associated pump systems 2300, 2400, 2500, 2600, 2800, any number of baffles 3012 can be used to separate the supercritical fluid 3012 from the oil 3010.

[0341] Figure 32 It can be used Figure 23-26A schematic representation of a first example layout 3200 of pump systems 2300, 2400, 2500, 2600, and 2800, and / or 28. Figure 32 In this configuration, the supercritical fluid flowing through the pump inlet 3202 is driven by an impeller 3204 (e.g., a low-head impeller). A first portion of the supercritical fluid flows through the outlet 3206 of the compressor housing 3207 and into conduit 3209. Furthermore, an ejector 3211 facilitates the drawing of the supercritical fluid through conduit 3209 towards the downstream heat transfer bus (e.g., Figure 3 (Hot transfer bus 202).

[0342] Furthermore, a second portion of the supercritical fluid flows past impeller 3204, around shaft 3213, and into motor housing 3208. Thus, the second portion of the supercritical fluid flows through and mixes with oil used to lubricate rolling element bearings that support shaft 3213. Additionally, the second portion of the supercritical fluid flows through gas-gas seal 3210 before the gas-oil seal 3212 stops the flow. Subsequently, the mixture of supercritical fluid and oil collected from it exits through outlet 3214 of motor housing 3208 and merges with the first portion of the supercritical fluid in conduit 3209. Then, an oil separator 3216 (e.g., [missing information]) positioned in conduit 3209 [missing information]... Figure 23 First separator 2302, Figure 24-26 And the second separator 2402 of 28, Figure 25 The third separator Figure 30A -C's first, second, and third rotary separators 3002, 3020, 3040, and / or Figure 31A The first and second static separators 3102 and 3120 of -C separate the oil in the mixture from the supercritical fluid, allowing the supercritical fluid to continue through conduit 3209 toward the heat transfer bus 202 while trapping the oil. In some examples, another conduit may be positioned below oil separator 3216 to transfer the oil collected by oil separator 3216 back to the oil supply section and / or motor housing 3208, where it can be used to lubricate rolling element bearings, as described below. Figure 35 The subject of discussion.

[0343] Figure 33 It can be used Figure 23-26A schematic representation of a second example layout 3300 of pump systems 2300, 2400, 2500, 2600, and 2800. In the second example layout 3300, an oil separator 3216 is positioned in a return conduit 3302, which is fluidly connected to the motor housing 3208 and the compressor housing 3207 at the pump inlet 3202. Therefore, a mixture of a second portion of the supercritical fluid and oil flows through the return conduit 3302, where the oil separator 3216 separates the oil from the supercritical fluid. Thus, the supercritical fluid can flow back into the compressor housing 3207 and, consequently, be driven by the impeller 3204. Furthermore, a valve 3304 is positioned in the return conduit 3302 to prevent supercritical fluid entering through the inlet 3202 from flowing through the return conduit 3302.

[0344] Figure 34 yes Figure 23-26 A schematic representation of a third example layout 3400 of pump systems 2300, 2400, 2500, 2600, and 2800. In the third example layout 3400, the return pipe 3302 includes an oil tank 3402 upstream of the oil separator 3216. Therefore, as oil in the mixture flows through the oil tank 3402, the oil in the mixture can be drawn to the oil stored in the oil tank 3402. Specifically, the oil in the mixture can be mixed with the aforementioned additives (e.g., in a container that can be used to mount the shaft 3213). Figure 23-26 In the rolling element bearings 2325, 2327, 2808, 2820 (and / or 28), the additives increase the adhesive and cohesive properties of the oil. As a result, the increased adhesiveness and cohesiveness of the oil in the mixture allows the oil in the mixture to be drawn into the stored oil. Furthermore, the stored oil can be positioned below the return pipe 3302, so that gravity helps move the oil in the mixture into the oil tank 3402, while the second portion of the supercritical fluid continues to flow through the return pipe 3302.

[0345] Figure 35 yes Figure 23-26 A schematic representation of a fourth example layout 3500 of pump systems 2300, 2400, 2500, 2600, and 2800. In the fourth example layout 3500, oil separated from the supercritical fluid by an oil separator 3216 enters an oil conduit 3502 (e.g., Figure 31C (Secondary flow path 3128). Then, the oil passes through the oil filter 3504 and enters the oil supply section 3506. Further, the oil pump 3508 can pump the fluid from the oil supply section 3506 to the pump 3510, in which the bearings can be lubricated (e.g., ...). Figure 23-26And / or 28 rolling element bearings 2325, 2327, 2808, 2820). Furthermore, oil removal conduit 3512 can transport a portion of the mixture from pump 3510 to oil filter 3504. For example, oil removal conduit 3512 can be fluidly connected to oil collection conduit 3126 (…). Figure 31C ), to receive the flow through secondary flow path 3128 ( Figure 31C Oil. Additionally or alternatively, the oil removal conduit 3512 may be positioned to receive oil from the baffles 3104, 3104A, 3104B, 3104C of the first example static separator 3102. Figure 31A -B) Oil 3010 ( Figure 31A -C). As a result, oil can enter the oil supply section 3506. Additionally, a release conduit 3514 connected to the oil supply section 3506 allows any supercritical fluid entering the oil supply section 3506 to be released into the atmosphere. Specifically, the release conduit 3514 includes a release valve 3516, which allows fluid to be released in response to encountering a pressure greater than a pressure threshold.

[0346] In some examples, pump systems 2300, 2400, 2500, 2600, and 2800 include means for compressing fluids. For example, the means for compressing fluids may be... Figure 4 Impeller 406, Figure 23-26 And / or 28 impeller 2340, Figures 32-33 Impeller 3204 and / or any other impeller implementation described herein.

[0347] In some examples, pump systems 2300, 2400, 2500, 2600, and 2800 include means for housing a device for compression. For example, the means for housing may be... Figure 4 Compressor collector 408, Figure 23-26 And / or 28 pump housing 2306, Figure 23-4 and / or Figure 28 Motor housing 2308 Figures 32-33 Compressor housing 3207 and / or Figures 32-33 The motor housing 3208 is implemented.

[0348] In some examples, pump systems 2300, 2400, 2500, 2600, and 2800 include means for transferring fluid. For example, the means for transferring fluid may be... Figure 2 Hot transfer bus 202 Figure 4 Fluid conduit 402, Figure 23-26 And pipe 2304 of 28, Figure 30A -C pipe 3003, Figure 32 Pipeline 3209 Figures 33-34The implementation of piping 3302 and / or any other pump output piping disclosed herein.

[0349] In some examples, pump systems 2300, 2400, 2500, 2600, and 2800 include devices for separating supercritical fluids and oils. For example, the separation device may be... Figure 23 First separator 2302, Figure 24-26 And the second separator 2402 of 28, Figure 25 The third separator 2506 Figure 30A -C's first, second, and / or third rotary separators 3002, 3020, 3040, and / or Figure 31A -C is implemented with the first and / or second static separators 3102, 3120.

[0350] In some examples, pump systems 2300, 2400, 2500, 2600, and 2800 include means for rotating the device used for compression. For example, the means for rotation may be... Figure 23-26 and / or 28 electric motors 2320 and / or Figure 23-26 And / or 28 shafts 2324 implemented.

[0351] In some examples, pump systems 2300, 2400, 2500, 2600, and 2800 include means for increasing the angular velocity of the compression device relative to the rotational device. For example, the means for increasing the angular velocity of the compression device may be... Figure 26-27 The gearbox 2609 is implemented.

[0352] In some examples, pump systems 2300, 2400, 2500, 2600, and 2800 include a first device for radially supporting a means for rotation. The first device for radial support may include a first stiffness. For example, the first device for radial support may be composed of… Figure 28 The first bearing assembly 2802 of 29 is implemented.

[0353] In some examples, pump systems 2300, 2400, 2500, 2600, and 2800 include a second device for radially supporting the means for rotation. The second device for radial support may include a second stiffness different from (e.g., less than) the first stiffness. For example, the second device for support may be composed of… Figure 28 The second bearing assembly 2804 of 29 is implemented.

[0354] This document discloses an example oil-lubricated pump architecture with one or more oil separators. The example pump system disclosed herein includes an oil separator to allow a fluid (e.g., a heat exchange fluid, such as a supercritical fluid (e.g., sCO2, etc.)) to mix with and subsequently separate from the oil. The oil separator enables the fluid to mix with the oil while reducing the safety risks associated with heat transfer encountered by the fluid. Therefore, the oil separator allows the impeller to be directly driven by an electric motor without the need for a shield to separate the fluid from the motor. Furthermore, the oil separator allows for a reduction in the number and / or complexity of components in the pump system.

[0355] Axial flux motor driven pump system for pressurizing fluids in a closed-loop system

[0356] As referenced above Figure 4 The operation of some example fluid pump systems and centrifugal fluid pump systems includes an electric motor (e.g., motor 410) axially connected to an impeller (e.g., impeller 406) via an impeller shaft (e.g., impeller shaft 466). Figure 4 The example motor 410 shown includes a stator to generate torque on the rotor via magnetic force. The example stator includes copper wire windings called electromagnetic coils that surround a ferromagnetic core, poles, and / or rods oriented perpendicular to the rotor's axis of rotation. The electromagnetic coils are tightly wound around the poles such that they continue parallel to the rotor's axis of rotation. According to Faraday's law of induction, when current flows through the electromagnetic coils, a magnetic field is generated that flows around the electromagnetic coils perpendicular to the direction of current flow. Therefore, if the electromagnetic coils are wound parallel to the motor's axis of rotation, the magnetic field generated by the electromagnetic coils flows perpendicular to the motor's axis of rotation. Because the stator of the example motor 410 generates a magnetic field that operates perpendicular to or radially to the axis of rotation of the motor 410, the example motor 410 driving the rotor shaft 438 can be referred to as a radial flux motor.

[0357] In contrast to radial flux motors (e.g., motor 410), axial flux motors include electromagnetic coils and / or windings oriented perpendicular to the axis of rotation of the motor and / or rotor. The orientation of the electromagnetic coil windings causes the electromagnetic coils to generate a magnetic field flowing parallel to the axis of rotation of the motor and / or rotor. Because the flux direction is parallel to the axis of rotation, the stator and rotor in an axial flux motor are designed as discs, plates, etc., which increases the distance between the permanent magnets in the rotor and the axis of rotation, and also reduces the axial length of the axial flux motor. Radial flux motors use electromagnetic coils and permanent magnets that are axially longer than those in axial flux motors because radial flux motors rely on stronger magnetic forces to produce the same torque as axial flux motors. Because axial flux motors can apply magnetic forces to the rotor at a greater distance from the axis of rotation than radial flux motors, and because torque is the product of force and distance, axial flux motors can produce the same torque on the rotor as radial flux motors because the electromagnetic coils and permanent magnets are further away from the axis of rotation. This means that an axial flux motor can be shorter axially but larger radially than a radial flux motor, while still generating the same overall torque.

[0358] In the examples disclosed herein, an axial flux motor is used to drive a pump system that pressurizes a fluid in a closed-loop system. In some examples, the fluid is a supercritical fluid. In some examples, the supercritical fluid is supercritical carbon dioxide (sCO2). In some instances, the closed-loop system is a thermal management system (e.g., Figure 3 The thermal management system 200 uses CO2 in the heat exchanger (e.g., Figure 3The heat source heat exchanger 206 and / or radiator heat exchanger 208 transfer heat energy between them. In the example disclosed herein, the axial flux motor driven pump system for pressurizing fluid in a closed-loop system moves the center of gravity (CG) of the pump system closer to the mounting flange, which is used to mount the pump system to a mounting surface (e.g., a wall, beam, support structure, etc.), relative to the radial flux motor driven pump system (e.g., heat transfer bus pump 400). In the example disclosed herein, because the CG of the example axial flux motor driven pump system is closer to the mounting flange than that of the radial flux motor driven pump system, there is a smaller torque or moment of force acting on the pump system and the mounting flange due to gravity, which reduces the vibration and damage of the axial flux motor driven pump system over time compared to the radial flux motor driven pump system. In the examples disclosed herein, the axial flux motor pump system saves space in the axial direction within an example aircraft on which an example axial flux motor-driven pump system can be used. In the examples disclosed herein, the surface on which the axial flux motor-driven pump system is mounted (e.g., walls, structures, beams, etc.) can be thinner than the surface on which a radial flux motor-driven pump system is mounted due to the reduction in CG overhang. In the examples disclosed herein, the axial flux motor-driven pump system includes a pump housing, impeller, impeller shaft, etc., as a replaceable unit with separate piping to optimize the removal and / or maintenance of the pump, motor, and / or other components of the axial flux motor-driven pump system relative to the radial flux motor-driven pump system.

[0359] Throughout the accompanying drawings disclosed herein, the same numerals indicate the same elements. Figure 36 It shows a method for use in closed-loop systems (e.g., Figure 3 A cross-sectional view of an axial flux motor-driven pump system 3600 (“pump system 3600”) for pressurizing fluid (e.g., supercritical fluid (sCO2)) in a thermal management system 200. In some examples, the pump system 3600 is used to pump sCO2 through an aircraft (e.g., Figure 1 The aircraft 10) and / or gas turbine engine (e.g., Figure 2 The thermal management system on the gas turbine engine 100. For example... Figure 36 As shown, the pump system 3600 includes an impeller 3602, an impeller shaft 3604, a radial impeller bearing 3606, a pump housing 3608, housing bolts 3609, a magnetic coupling 3610, an inner hub 3612, an outer hub 3614, a barrier tank 3616, barrier tank bolts 3617, a connecting shaft 3618, a rotor shaft 3620, a spline interface 3622, a stator 3624, a rotor 3626, a radial motor bearing 3628, a motor housing 3630, and a mounting flange 3632. Some of the architectures included in the example pump system 3600 can be used in other pump systems described above, such as... Figure 9Pump system 900, Figure 23-26 Pump systems of 2300-2600 and 2800.

[0360] Figure 36 The example pump system 3600 shown includes an impeller 3602 to be used in the example closed-loop system (e.g., Figure 3 The example fluid (e.g., CO2) is pressurized in the thermal management system 200. An example impeller 3602 is a component of the pump system 3600, connected to an impeller shaft 3604, and rotates at the same speed as the impeller shaft 3604. In some examples, the impeller 3602 is the same as or similar to the impeller used in a centrifugal pump and includes impeller blades and / or blades to radially deflect the incoming fluid flow into the outlet flow line. The example impeller 3602 converts the mechanical power of an electric motor (e.g., stator 3624 and rotor 3626) into the hydrodynamic power of the flowing fluid.

[0361] Figure 36 The example pump system 3600 shown includes an impeller shaft 3604 to transmit torque from an electric motor (e.g., stator 3624, rotor 3626, and rotor shaft 3620) to the impeller 3602. In some examples, the impeller shaft 3604 is a hollow shaft to conserve mass and includes a central rod along the axis of rotation of the impeller shaft 3604 to maintain axial alignment of the impeller shaft 3604. In some examples, the impeller shaft 3604 is manufactured via additive and / or subtractive manufacturing to metallic materials (e.g., titanium, aluminum alloys, etc.) and / or composite materials (e.g., carbon fiber, etc.). (etc.) Manufacturing. Example impeller shaft 3604 is constructed as multiple parts included in the assembly; however, in some examples, impeller shaft 3604 is manufactured as a single part and / or a pre-assembled structure.

[0362] Figure 36 The example pump system 3600 shown includes a radial impeller bearing 3606 to support radial loads (e.g., weight, forced oscillations, etc.) on the impeller shaft 3604. Figure 36 The example radial impeller bearing 3606 shown is a rolling element bearing, which includes an inner ring, an outer ring, and rolling elements (e.g., balls, cylinders, etc.). Because... Figure 36The radial impeller bearing 3606 shown is a rolling element bearing, therefore the example radial impeller bearing 3606 can support the radial and thrust loads of the impeller shaft 3604. For example, the impeller shaft 3604 can be attached to the inner ring of the radial impeller bearing 3606 such that the impeller shaft 3604 cannot move too far in the axial direction (e.g., less than one millimeter (mm)). The example radial impeller bearing 3606 includes a dry lubricant (e.g., silver coating, graphite, molybdenum disulfide, etc.) to reduce friction between the inner ring, outer ring, and rolling elements without the risk of contaminating the fluid pressurized by the pump system 3600. In some examples, the radial impeller bearing 3606 includes a liquid lubricant (e.g., oil-based lubricant, water-based lubricant, silicone-based lubricant, etc.) to reduce friction between the inner ring, outer ring, and rolling elements, and the pump system 3600 includes an oil separator (e.g., Figure 32-35 An oil separator 3216 is used to remove liquid lubricant from the radial impeller bearing 3606 from a fluid (e.g., CO2).

[0363] In some examples, the radial impeller bearing 3606 is a foil bearing that supports the radial load of the impeller shaft 3604. In the example where the radial impeller bearing 3606 is a foil bearing, the radial impeller bearing 3606 includes a journal liner and spring-loaded foils. In the example where the radial impeller bearing 3606 is a foil bearing, the spring-loaded foils support the radial load of the impeller shaft 3604 during the start-up and shutdown of the pump system 3600. In the example where the radial impeller bearing 3606 is a foil bearing, as the angular velocity of the impeller shaft 3604 increases, the working fluid (e.g., air, nitrogen, argon, etc.) is drawn into the journal liner due to the viscous effect of the working fluid within the example radial impeller bearing 3606 and the increase in working fluid pressure. In the example where the radial impeller bearing 3606 is a foil bearing, once the working fluid pressure within the journal liner increases to a certain threshold (e.g., 100 pounds per square inch (psi)), the spring-loaded foil is pushed outward, and the working fluid pressure fully supports the radial load on the impeller shaft 3604. In the example where the radial impeller bearing 3606 is a foil bearing, the radial impeller bearing 3606 does not support the axial load on the impeller shaft 3604 and does not use a liquid lubricant. Therefore, if the example radial impeller bearing 3606 is a foil bearing, the example impeller shaft 3604 includes one or more shafts and / or one or more discs attached to the impeller shaft 3604, oriented perpendicular to the axis of rotation, and projecting radially outward from the impeller shaft 3604, similar to... Figure 5 , 6 And / or 7 thrust shafts 532, 632, 742. In some examples, if the radial impeller bearing 3606 is a foil bearing, then the example pump system 3600 includes a thrust bearing (e.g., Figure 5 , 6And / or 7 thrust bearings 534, 634, 744) to support the axial load of the impeller shaft via an interface with the example thrust shaft.

[0364] Figure 36 The example pump system 3600 shown includes a pump housing 3608 to support a radial impeller bearing 3606. The example pump housing 3608 prevents the radial impeller bearing 3606 from moving too far (e.g., less than 0.1 mm) in the radial or axial direction. Figure 36 In the example shown, the pump housing 3608 comprises three separate parts assembled together by fasteners (e.g., bolts, screws, adhesives, etc.). In some examples, the parts of the pump housing 3608 are manufactured separately via additive manufacturing and / or subtractive manufacturing prior to assembly. In some examples, the pump housing 3608 is a single part manufactured via additive manufacturing and / or subtractive manufacturing. The example pump housing 3608 is fastened to the example motor housing 3630 via housing bolts 3609. Although Figure 36 Two housing bolts 3609 are shown, but the pump system 3600 may include two or more housing bolts 3609.

[0365] Figure 36 The example pump system 3600 shown includes a magnetic coupling 3610 to connect the impeller shaft 3604 to the coupling shaft 3618. Figure 36 Example magnetic coupling element 3610 and Figure 5 , 6 The magnetic couplings 526, 626, and 720 shown in example 7 are the same as and / or similar, and transmit torque from the connecting shaft 3618 to the impeller shaft 3604 via magnetic force. In some examples, the inner hub 3612 of the magnetic coupling 3610 includes a first set of permanent magnets, and the outer hub 3614 of the magnetic coupling 3610 includes a second set of permanent magnets. The example first set of permanent magnets and the example second set of permanent magnets have alternating polarities about the axis of rotation of the impeller shaft 3604 and / or the connecting shaft 3618, and the attractive magnetic force between the first set of magnets and the second set of magnets causes the outer hub 3614 to drive the rotation of the inner hub 3612.

[0366] Figure 36 The example pump system 3600 shown includes a barrier tank 3616 to help prevent fluid from contacting the rotor 3626, stator 3624 and / or other parts and / or components that affect the operability of the motor. Figure 36 The example barrier can 3616 shown includes metallic and / or non-metallic materials and can be used with... Figure 5-7 Example barrier tanks 536, 636, 728, Figure 15 1500 and / or Figure 19The 1900 is the same as and / or similar to that of the pump housing 3608. Example barrier tank 3616 is fastened to pump housing 3608 via barrier tank bolts 3617. In some examples, barrier tank 3616 is connected to pump housing 3608 via barrier tank bolts 3617 and / or other fasteners (such as screws, pins, rods, pins, adhesives, magnets, interference fits, etc.).

[0367] Figure 36 The example pump system 3600 shown includes a coupling shaft 3618 to house the outer hub 3614 of a magnetic coupling element 3610, and transmits torque from the rotor shaft 3620 to the impeller shaft 3604 via the magnetic coupling element 3610. In some examples, the coupling shaft 3618 includes the outer hub 3614 and / or a second set of permanent magnets. Figure 36 Example coupling shaft 3618 interacts with rotor shaft 3620 via spline interface 3622. In some examples, coupling shaft 3618 and rotor shaft 3620 include physical interlocking to form splines (e.g., teeth, ridges, V-cuts, etc.) of spline interface 3622. Spline interface 3622 is a physical connection at which the splines of rotor shaft 3620 apply force to the splines of coupling shaft 3618, and thus, transmit torque from rotor shaft 3620 to coupling shaft 3618. Example spline interface 3622 causes coupling shaft 3618 to rotate at the same rate as rotor shaft 3620.

[0368] Figure 36The example pump system 3600 shown includes a stator 3624, a rotor 3626, and a radial motor bearing 3628 to provide mechanical power to the pump system 3600. The stator 3624, rotor 3626, and radial motor bearing 3628 of the example pump system 3600 are included in an axial flux motor of the system operating as previously described. In some examples, the stator 3624 includes an electromagnetic coil surrounding a core of ferrous material (e.g., soft iron, nickel, cobalt, etc.) such that the electromagnetic coil extends perpendicular to the axis of rotation and generates a magnetic flux parallel to the axis of rotation. The example stator 3624 supports and / or houses the example radial motor bearing 3628 such that the radial motor bearing 3628 does not move too far (e.g., less than 0.005 inches) from its intended position in the pump system 3600 due to the radial and / or axial forces generated by the rotor 3626 and / or rotor shaft 3620. Example rotor 3626 includes a first rotor disk positioned on the front side of stator 3624 and a second rotor disk positioned on the rear side of stator 3624. The example first rotor disk and example second rotor disk include permanent magnets, and the magnetic flux generated by example stator 3624 attracts and / or repels the permanent magnets. Example stator 3624 generates heat due to resistance in the electromagnetic coils. In some examples, cooling trenches, linings, tubes, sheaths, etc., with a flowing liquid coolant (e.g., water, oil, deionized water, suppressed glycol, dielectric fluid, heat exchange fluid such as supercritical fluids (e.g., sCO2, etc.)) are included in and / or surround stator 3624 to transfer heat to the liquid coolant. In some examples, cooling fins and / or vents are fixed to stator 3624 to transfer heat to ambient air.

[0369] The example rotor 3626 of the pump system 3600 is attached to the example rotor shaft 3620 via fasteners (e.g., bolts, pins, dowels, adhesives, magnets, interference fits, etc.). In some examples, the rotor 3626 is also attached to the inner and / or outer rings of the radial motor bearing 3628. Figure 36 The example pump system 3600 shown includes an example radial motor bearing 3628 to support radial loads (e.g., weight, forced oscillations, etc.) generated by the rotor shaft 3620. Figure 36The example radial motor bearing 3628 also supports the radial load of the rotor 3626 via a mechanical connection (e.g., fasteners, adhesives, magnets, interference fits, etc.) between the rotor 3626 and the rotor shaft 3620. The example radial motor bearing 3628 is a rolling element bearing that uses a liquid lubricant (e.g., oil-based lubricant, water-based lubricant, silicone-based lubricant, etc.) to reduce friction between the inner ring, outer ring, and / or rolling elements of the radial motor bearing 3628. The example rotor 3626 and / or the example rotor shaft 3620 generate the radial and axial loads supported by the radial motor bearing 3628. Additionally or alternatively, a thrust bearing may be used in an axial flux motor to support the axial loads generated by the rotor 3626 and / or the rotor shaft 3620. Additionally or alternatively, an axial flux motor may include a thrust bearing to support the axial loads generated by the rotor 3626 and / or the rotor shaft 3620.

[0370] Figure 36 The example pump system 3600 shown includes a motor housing 3630 to support the stator 3624 and / or pump housing 3608 of the pump system 3600. In some examples, the motor housing 3630 is an additively manufactured and / or subtractively manufactured portion to accommodate the stator 3624, rotor 3626, radial motor bearing 3628, rotor shaft 3620, connecting shaft 3618, barrier tank 3616, outer hub 3614, inner hub 3612, magnetic coupling 3610, a portion of the mounting flange 3632, and / or a portion of the pump housing 3608. Figure 36 In the example shown, the motor housing 3630 includes different parts that are manufactured separately (e.g., by additive manufacturing and / or subtractive manufacturing) and assembled together (e.g., via bolts, adhesives, pins, and / or interference fits) to accommodate a stator 3624, a rotor 3626, a radial motor bearing 3628, a rotor shaft 3620, a connecting shaft 3618, a barrier tank 3616, an outer hub 3614, an inner hub 3612, a magnetic coupling 3610, a portion of a mounting flange 3632, and / or a portion of a pump housing 3608 without interfering with the stator 3624, the rotor 3626, the radial motor bearing 3628, the motor housing 3630, and / or the mounting flange 3632.

[0371] Figure 36 The example pump system 3600 shown includes a mounting flange 3632 for mounting the example pump system 3600 to a surface (e.g., a wall, assembly rod, beam, etc.). The example mounting flange 3632 includes a hole through which fasteners (e.g., bolts, pins, clamps, etc.) can be fitted and attached to the mounting surface. Figure 36The mounting flange 3632 is made of a material (e.g., aluminum, steel, titanium, etc.) strong enough to withstand bending and / or shear stresses that may be applied to the mounting flange 3632 during operation and / or non-operation of the pump system 3600. The motor housing 3630 is connected to the mounting flange 3632 via one or more fasteners (e.g., bolts, adhesives, interference fits, etc.) and can be secured to the mounting flange 3632 before it is mounted to the mounting surface. In some examples, the motor housing 3630 and the mounting flange 3632 are the same part manufactured via additive manufacturing and / or subtractive manufacturing. In some examples, the mounting flange 3632 is not included in the pump system 3600, and the motor housing 3630 directly contacts the mounting surface. Additionally or alternatively, the example motor housing 3630 includes holes (e.g., threaded holes, clearance holes, etc.) in which one or more fasteners (e.g., bolts, pins, interference fits, etc.) can be fitted to attach the pump system 3600 to a mounting surface.

[0372] Figure 37 It shows a method for use in closed-loop systems (e.g., Figure 3 A cross-sectional view of an axial flux motor-driven pump system 3700 (“pump system 3700”) for pressurizing fluid (e.g., supercritical fluid (sCO2)) in a thermal management system 200. In some examples, the pump system 3700 is used to pump sCO2 through an aircraft (e.g., Figure 1 The aircraft 10) and / or gas turbine engine (e.g., Figure 2 The thermal management system on the gas turbine engine 100. For example... Figure 37 As shown, the pump system 3700 includes an impeller 3702, an impeller shaft 3704, a radial impeller bearing 3706, a pump housing 3708, housing bolts 3709, a piston seal 3710, a rotor shaft 3720, a spline interface 3722, a stator 3724, a rotor 3726, a radial motor bearing 3728, a motor housing 3730, and a mounting flange 3732.

[0373] Figure 37 The example pump system 3700 shown includes an impeller 3702 to be used in the example closed-loop system (e.g., Figure 3 The example fluid (e.g., CO2) is pressurized in the thermal management system 200. An example impeller 3702 is a component of the pump system 3700, connected to an impeller shaft 3704, and rotates at the same speed as the impeller shaft 3704. In some examples, the impeller 3702 is the same as or similar to the impeller used in a centrifugal pump and includes impeller blades and / or blades to radially deflect the incoming fluid flow into the outlet flow line. The example impeller 3702 converts the mechanical power of an electric motor (e.g., stator 3724 and rotor 3726) into the hydrodynamic power of the flowing fluid.

[0374] Figure 37 The example pump system 3700 shown includes an impeller shaft 3704 to transmit torque from an electric motor (e.g., stator 3724, rotor 3726, and rotor shaft 3720) to the impeller 3702. In some examples, the impeller shaft 3704 is a hollow shaft to conserve mass and includes a central rod along the axis of rotation of the impeller shaft 3704 to maintain axial alignment of the impeller shaft 3704. In some examples, the impeller shaft 3704 is manufactured via additive and / or subtractive manufacturing to metallic materials (e.g., titanium, aluminum alloys, etc.) and / or composite materials (e.g., carbon fiber, etc.). (etc.) Manufacturing. Example impeller shaft 3704 is constructed as multiple parts included in the assembly; however, in some examples, impeller shaft 3704 is manufactured as a single part and / or a pre-assembled structure.

[0375] Figure 37 The example pump system 3700 shown includes a radial impeller bearing 3706 to support radial loads (e.g., weight, forced oscillations, etc.) on the impeller shaft 3704. Figure 37 The example radial impeller bearing 3706 shown is a rolling element bearing, which includes an inner ring, an outer ring, and rolling elements (e.g., balls, cylinders, etc.). Because... Figure 37 The radial impeller bearing 3706 shown is a rolling element bearing, therefore the example radial impeller bearing 3706 can support the radial and thrust loads of the impeller shaft 3704. For example, the impeller shaft 3704 can be attached to the inner ring of the radial impeller bearing 3706 such that the impeller shaft 3704 cannot move too far in the axial direction (e.g., less than 0.005 inches). The example radial impeller bearing 3706 includes a dry lubricant (e.g., silver coating, graphite, molybdenum disulfide, etc.) to reduce friction between the inner ring, outer ring, and rolling elements without the risk of contaminating the fluid pressurized by the pump system 3700. In some examples, the radial impeller bearing 3706 includes a liquid lubricant (e.g., oil-based lubricant, water-based lubricant, silicone-based lubricant, etc.) to reduce friction between the inner ring, outer ring, and rolling elements, and the pump system 3700 includes an oil separator (e.g., Figure 32-35 An oil separator 3216 is used to remove liquid lubricant from the radial impeller bearing 3706 from a fluid (e.g., CO2).

[0376] In some examples, the radial impeller bearing 3706 is a foil bearing that supports the radial load of the impeller shaft 3704. In the example where the radial impeller bearing 3706 is a foil bearing, the radial impeller bearing 3706 includes a journal liner and spring-loaded foils. In the example where the radial impeller bearing 3706 is a foil bearing, the spring-loaded foils support the radial load of the impeller shaft 3704 during the start-up and shutdown of the pump system 3700. In the example where the radial impeller bearing 3706 is a foil bearing, as the angular velocity of the impeller shaft 3704 increases, the working fluid (e.g., air, nitrogen, argon, etc.) is drawn into the journal liner due to the viscous effect of the working fluid within the example radial impeller bearing 3706 and the increase in working fluid pressure. In the example where the radial impeller bearing 3706 is a foil bearing, once the working fluid pressure within the journal liner increases to a certain threshold (e.g., 100 pounds per square inch (psi)), the spring-loaded foil is pushed outward, and the working fluid pressure fully supports the radial load on the impeller shaft 3704. In the example where the radial impeller bearing 3706 is a foil bearing, the radial impeller bearing 3706 does not support the axial load on the impeller shaft 3704 and does not use a liquid lubricant. Therefore, if the example radial impeller bearing 3706 is a foil bearing, the example impeller shaft 3704 includes one or more shafts and / or one or more discs attached to the impeller shaft 3704, oriented perpendicular to the axis of rotation, and projecting radially outward from the impeller shaft 3704, similar to... Figure 5 , 6 And / or thrust shafts 532, 632, 742. In some examples, if the radial impeller bearing 3706 is a foil bearing, then the example pump system 3700 includes a thrust bearing (e.g., Figure 5 , 6 And / or 7 thrust bearings 534, 634, 744) to support the axial load of the impeller shaft via an interface with the example thrust shaft.

[0377] Figure 37 The example pump system 3700 shown includes a pump housing 3708 to support a radial impeller bearing 3706. The example pump housing 3708 prevents the radial impeller bearing 3706 from moving too far (e.g., less than 0.005 inches) in the radial or axial direction. Figure 37 In the example shown, the pump housing 3708 comprises three separate parts assembled together by fasteners (e.g., bolts, screws, adhesives, etc.). In some examples, portions of the pump housing 3708 are manufactured separately via additive and / or subtractive manufacturing prior to assembly. In some examples, the pump housing 3708 is a single part manufactured via additive and / or subtractive manufacturing. The example pump housing 3708 is fastened to the example motor housing 3730 via housing bolts 3709. Although Figure 37Two housing bolts 3709 are shown, but the pump system 3700 may include two or more housing bolts 3709.

[0378] Figure 37 The example pump system 3700 shown includes a piston seal 3710 to seal fluid away from an axial flux motor, which includes a stator 3724, a rotor 3726, a radial motor bearing 3728, a motor housing 3730, and / or a mounting flange 3732. In some examples, the piston seal 3710 prevents fluid from entering the axial flux motor and / or the motor housing 3730, and in some examples, the piston seal 3710 allows a very small amount of fluid (e.g., less than 0.01 fluid ounces) to enter the motor housing 3730 during operation of the example pump system 3700. In some examples, the piston seal 3710 of the example pump system 3700 is a single-acting piston seal that contains pressure on one side of the seal and prevents fluid from flowing from the high-pressure side to the low-pressure side. The example piston seal 3710 is located in and / or attached to a slot that cuts into the inner surface of the rotor shaft 3720. In some examples, the fluid is pressurized to at least 1,000 pounds per square inch (psi) of sCO2, and a piston seal 3710 is included in the rotor shaft 3720 to withstand the pressure difference between the fluid and the air pressure within the axial flux motor, and to prevent and / or prohibit the fluid from contacting the stator 3724 and / or the rotor 3726.

[0379] Figure 37 The example pump system 3700 shown includes a rotor shaft 3720 to transmit torque from an axial flux motor (e.g., rotor 3726) to an impeller shaft 3704 via a spline interface 3722. In some examples, the impeller shaft 3704 and rotor shaft 3720 include physical interlocking to form splines (e.g., teeth, keys, ridges, V-cuts, etc.) and / or serrations in the spline interface 3722. The spline interface 3722 is a physical connection at which the splines of the rotor shaft 3720 apply force to the splines of the impeller shaft 3704, and thus, transmit torque from the rotor shaft 3720 to the impeller shaft 3704. The example spline interface 3722 causes the impeller shaft 3704 to rotate at the same rate as the rotor shaft 3720.

[0380] Figure 37The example pump system 3700 shown includes a stator 3724, a rotor 3726, and a radial motor bearing 3728 to provide mechanical power to the pump system 3700. The stator 3724, rotor 3726, and radial motor bearing 3728 of the example pump system 3700 are incorporated into an axial flux motor of the system operating as previously described. In some examples, the stator 3724 includes an electromagnetic coil surrounding a core of ferrous material (e.g., soft iron, nickel, cobalt, etc.) such that the coil is aligned perpendicular to the axis of rotation and generates a magnetic flux parallel to the axis of rotation. The example stator 3724 supports and / or houses the example radial motor bearing 3728 such that the radial motor bearing 3728 does not move too far (e.g., less than 0.005 inches) from its intended position in the pump system 3700 due to the radial and / or axial forces generated by the rotor 3726 and / or rotor shaft 3720. Example rotor 3726 includes a first rotor disk positioned on the front side of stator 3724 and a second rotor disk positioned on the rear side of stator 3724. The example first rotor disk and example second rotor disk include permanent magnets, and the magnetic flux generated by example stator 3724 attracts and / or repels the permanent magnets. Example stator 3724 generates heat due to resistance in the electromagnetic coils. In some examples, cooling trenches, liners, tubes, sheaths, etc., with a flowing liquid coolant (e.g., water, oil, deionized water, suppressed glycol, dielectric fluid, heat exchange fluid such as supercritical fluids (e.g., sCO2, etc.)) are included in and / or surround stator 3724 to transfer heat to the liquid coolant. In some examples, cooling fins and / or vents are fixed to stator 3724 to transfer heat to ambient air.

[0381] The example rotor 3726 of the pump system 3700 is attached to the example rotor shaft 3720 via fasteners (e.g., bolts, pins, dowels, adhesives, magnets, interference fits, etc.). In some examples, the rotor 3726 is also attached to the inner and / or outer rings of the radial motor bearing 3728. Figure 37 The example pump system 3700 shown includes an example radial motor bearing 3728 to support radial loads (e.g., weight, forced oscillations, etc.) generated by the rotor shaft 3720. Figure 37The example radial motor bearing 3728 also supports the radial load of the rotor 3726 via a mechanical connection (e.g., fasteners, adhesives, magnets, interference fits, etc.) between the rotor 3726 and the rotor shaft 3720. The example radial motor bearing 3728 is a rolling element bearing that uses a liquid lubricant (e.g., oil-based lubricant, water-based lubricant, silicone-based lubricant, etc.) to reduce friction between the inner ring, outer ring, and / or rolling elements of the radial motor bearing 3728. The example rotor 3726 and / or the e...

Claims

1. A pump system for pressurizing fluid within a closed-loop transmission bus, characterized in that, The pump system includes: The pump includes an impeller; An electric motor, the electric motor including a rotor shaft connected to the impeller; A first bearing supports the rotor shaft within a first operating speed range and is connected to the inner ring. A second bearing supports the rotor shaft within a second operating speed range, and the rotor shaft is connected to the outer ring; and One or more bracing elements, said one or more bracing elements being configured to: Within the first operating speed range, the inner ring is engaged with the outer ring; and The inner ring is separated from the outer ring within the second operating speed range.

2. The pump system according to claim 1, characterized in that, The first bearing is a rolling element bearing, including at least one of angular contact ball bearings, hybrid ceramic bearings, tapered roller bearings, deep groove single ball bearings, double ball bearings, or spherical bearings.

3. The pump system according to claim 2, characterized in that, The first bearing is lubricated by an oil lubricant, and the system further includes a separator that separates the oil lubricant from the fluid, wherein a portion of the oil lubricant is mixed with the fluid.

4. The pump system according to claim 1, characterized in that, The second bearing is a foil bearing.

5. The pump system according to claim 1, characterized in that, In response to the rotor shaft rotating about the rotor axis in a first direction within the first operating speed range, the one or more bracing elements rotate about the bracing rotation axis in a second direction, which is different from the first direction.

6. The pump system according to claim 1, characterized in that, In response to the rotor shaft rotating about the rotor axis in a first direction within the second operating speed range, the one or more bracing elements rotate about the bracing rotation axis in a second direction, which is the same as the first direction.

7. The pump system according to claim 6, characterized in that, The one or more bracing elements are configured to rotate in the second direction in response to a centrifugal force acting on a portion of the one or more bracing elements, the centrifugal force being generated in response to the pump system operating within the second operating speed range.

8. The pump system according to claim 1, characterized in that, The one or more bracing elements include at least one of a solid lubricant or an oil mist lubricant, wherein the solid lubricant includes a silver coating.

9. An integrated bearing system for a shaft in a dynamic support pump system, characterized in that, The pump system pressurizes fluid within a closed-loop transmission bus, and the integrated bearing system includes: A shaft, which is connected to the impeller of the pump system; A first bearing supports the shaft within a first operating speed range and is connected to an inner ring. A second bearing, which supports the shaft within a second operating speed range, is connected to an outer ring; and One or more bracing elements, said one or more bracing elements being configured to: Within the first operating speed range, the inner ring is engaged with the outer ring; and The inner ring is separated from the outer ring within the second operating speed range.

10. The integrated bearing system according to claim 9, characterized in that, The first bearing is a rolling element bearing, including at least one of angular contact ball bearings, hybrid ceramic bearings, tapered roller bearings, deep groove single ball bearings, double ball bearings, or spherical bearings.

11. The integrated bearing system according to claim 9, characterized in that, The first bearing is lubricated by an oil lubricant, and the system further includes a separator that separates the oil lubricant from the fluid, wherein a portion of the oil lubricant is mixed with the fluid.

12. The integrated bearing system according to claim 9, characterized in that, The second bearing is a foil bearing.

13. The integrated bearing system according to claim 9, characterized in that, In response to the shaft rotating about the axis in a first direction within the first operating speed range, the one or more bracing elements rotate about the bracing rotation axis in a second direction, which is different from the first direction.

14. The integrated bearing system according to claim 9, characterized in that, In response to the shaft rotating about the rotor axis in a first direction within the second operating speed range, the one or more bracing elements rotate about the bracing rotation axis in a second direction, which is the same as the first direction.

15. The integrated bearing system according to claim 14, characterized in that, The one or more bracing elements are configured to rotate in the second direction in response to a centrifugal force acting on a portion of the one or more bracing elements, the centrifugal force being generated in response to the pump system operating within the second operating speed range.

16. The pump system according to claim 9, characterized in that, The one or more bracing elements include at least one of a solid lubricant or an oil mist lubricant, wherein the solid lubricant includes a silver coating.

17. A pump system for pressurizing fluid within a closed-loop supercritical transmission bus, characterized in that, The pump system includes: Device for increasing the kinetic energy of the fluid flowing through the pump system; Device for providing torque to the rotor shaft of the pump system; A first device for supporting the rotor shaft within a first operating speed range; A second device for supporting the rotor shaft in the second operating speed range; and A device for engaging the inner and outer rings within the first operating speed range.

18. The pump system according to claim 17, characterized in that, The device for engagement, in response to the rotor shaft rotating about the rotor axis in a first direction within the second operating speed range, separates the inner ring from the outer ring based on the centrifugal force generated by the rotor shaft.

19. The pump system according to claim 17, characterized in that, In response to the rotor shaft rotating about the rotor axis in a first direction within the second operating speed range, the engagement device rotates about the diagonal brace rotation axis in a second direction, which is the same as the first direction.

20. The pump system according to claim 17, characterized in that, It further includes means for separating one or more liquids from the fluid, the one or more liquids including oil.

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