Conical motor for use with pump

Abstract

A conical motor for use with a pump is disclosed. Examples disclosed herein include an electric motor including a conical rotor, a first end of the conical rotor having a first diameter and a second end of the conical rotor having a second diameter different from the first diameter, and a conical stator aligned with the conical rotor.

Description

Technical Field

[0001] The present disclosure relates generally to fluid pumps, and more particularly, to improved, more efficient pump design and operation. Background Art

[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 a lubrication system that lubricates components of the engine, an engine cooling system that provides cooling air to engine components, an environmental control system that provides cooled air to the cabin of the aircraft, etc. Thus, during operation of these accessory systems, heat is added or removed from the fluid (e.g., oil, air, etc.). BRIEF DESCRIPTION OF THE DRAWINGS

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

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

[0005] Figure 3 is a schematic diagram of an example thermal management system for transferring heat between fluids.

[0006] Figure 4 is a schematic diagram of an example heat transfer bus pump.

[0007] Figure 5 A first example pump system according to the teachings disclosed herein is shown.

[0008] Figure 6 A second example pump system according to the teachings disclosed herein is shown.

[0009] Figure 7 A third example pump system according to the teachings disclosed herein is shown.

[0010] Figure 8 A fourth example pump system according to the teachings disclosed herein is shown.

[0011] Fig. 9 is an example diagram of a first example process for controlling current provided to an example electric motor.

[0012] Fig.10 is an example diagram of a second example process for controlling current provided to an example electric motor.

[0013] Fig.11 is an example diagram of a third example process for controlling current provided to an example electric motor.

[0014] Fig.12 is an example diagram of a fourth example process for controlling current provided to an example electric motor.

[0015] Fig.13 is an example processor circuit that can be executed to implement Figure 9-12 Example machine readable instructions for processing or a flowchart of example operations.

[0016] Fig.14 is a block diagram of an example processing platform including a processor circuit structured to perform Fig.13 Example machine readable instructions and / or example operations.

[0017] The drawings are not drawn to scale. In general, the same reference numbers will be used throughout the drawings and accompanying written description to refer to the same or like parts. DETAILED DESCRIPTION

[0018] "Include" and "comprising" (and all their forms and tenses) are used as open-ended terms herein. Thus, whenever a claim adopts any form of "include" or "comprising" (e.g., includes, comprises, has, etc.) as 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.

[0019] As used herein, the phrase "at least" when used as a transitional term, such as in the preamble of a claim, is open ended in the same manner as the terms "comprising" and "including" are open ended. The term "and / or," when used, for example, in a form such as A, B, and / or C, refers to any combination or subset of A, B, 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 embodiments that include any of (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 embodiments that include any of (1) at least one A, (2) at least one B, or (3) at least one A and at least one B.

[0020] As used herein in the context of describing the performance or execution of processes, instructions, actions, activities, and / or steps, the phrase "at least one of A and B" is intended to refer to embodiments that include any of (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 performance or execution of processes, instructions, actions, activities, and / or steps, the phrase "at least one of A or B" is intended to refer to embodiments that include any of (1) at least one A, (2) at least one B, or (3) at least one A and at least one B.

[0021] As used herein, singular references (e.g., "a", "a", "first", "second", etc.) do not exclude the plural. As used herein, the term "a" or "an" object refers to one or more of the object. The terms "a" (or "a"), "one or more", and "at least one" are used interchangeably herein. In addition, although listed separately, multiple devices, elements, or method actions can be implemented by, for example, the same entity or object. In addition, although individual features may be included in different examples or claims, these may be combined, and the inclusion of different examples or claims does not mean that the combination of features is not feasible and / or disadvantageous.

[0022] As used herein, unless otherwise indicated, connection references (e.g., attached, coupled, connected, and joined) may include intermediate members between the elements referred to by the connection reference and / or relative movement between those elements. Thus, a connection reference does not necessarily infer that two elements are directly connected and / or are in fixed relation to each other. As used herein, stating that any part is "in contact with" another part is defined to mean that there is no intermediate part between the two parts.

[0023] Unless otherwise specifically stated, descriptors such as "first," "second," "third," etc., used herein do not confer or otherwise indicate any meaning of priority, physical order, arrangement in a list, and / or ordering in any manner, but are merely used as labels and / or arbitrary names to distinguish elements to facilitate understanding of the disclosed examples. In some examples, the descriptor "first" may be used to refer to an element in the detailed description, while a different descriptor (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 elements that may, for example, otherwise share the same name.

[0024] As used herein throughout the specification and claims, approximating language is applied to modify any quantitative expression that can be permitted to vary without resulting in a change in the basic function to which it is associated. Thus, a value modified by one or more terms such as "approximately," "approximately," and "substantially" is not limited to the precise value specified. In at least some cases, approximate language may correspond to the precision of an instrument used to measure a value, or the precision of a method or machine used to construct or manufacture a component and / or system. For example, approximate language may refer to within a ten percent margin.

[0025] The terms "front" and "rear" refer to relative positions within a gas turbine engine, pump, or vehicle, and refer to the normal operating attitude of the gas turbine engine, pump, or vehicle. For example, with respect to a gas turbine engine, the front refers to a position closer to the engine inlet, while the rear refers to a position closer to the engine nozzle or exhaust. In addition, with respect to a pump, the front refers to a position closer to the pump inlet, while the rear refers to a position closer to the end of the pump opposite the inlet.

[0026] The terms "upstream" and "downstream" refer to relative directions relative to flow in a path. For example, with respect to fluid flow, "upstream" refers to the direction from which the fluid is flowing, while "downstream" refers to the direction toward which the fluid is flowing.

[0027] As used herein, the term "substantially orthogonal" in the context of describing the position and / or orientation of a first object relative to a second object 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 of no more than five degrees (5°) from orthogonal. For example, a first axis that is substantially orthogonal to a second axis is positioned and / or oriented relative to the second axis at an absolute angle of no more than five degrees (5°) from orthogonal.

[0028] As used herein, "radial" is used to refer to one or more points along a radial vector originating from a central axis of a rotating body and pointing perpendicularly outward from the central axis. In some examples, the fluid is said to be accelerated radially outward from the impeller, meaning that the fluid flows outward from the central axis (axis of rotation) of the impeller in a direction substantially orthogonal to the central axis.

[0029] A centrifugal fluid pump moves a fluid (e.g., fuel, water, oil, supercritical carbon dioxide (sCO2), etc.) through a system (e.g., a waste heat recovery (WHR) system) by converting the rotational kinetic energy of an impeller into the fluid kinetic energy of the flowing fluid. In other words, the angular velocity of the impeller is proportional to the flow rate of the flowing fluid leaving the pump. The impeller is provided with a change in the rotational kinetic energy from an electric motor, which applies mechanical work to an impeller shaft coupled to the impeller and the rotor of the electric motor. The rotor is provided with a change in mechanical work (e.g., mechanical power) over a period of time from a stator in the electric motor, which applies an electromagnetic force to the rotor in the form of torque. When the electric motor supplies a constant amount of electrical energy to the stator, the rotor supplies a constant amount of mechanical energy to the impeller.

[0030] During operation of the pump, the rotation of the impeller shaft and the associated impeller causes the impeller shaft to vibrate radially within the pump's housing. A radial bearing (e.g., a hydrodynamic bearing, a foil bearing, a rolling element bearing, etc.) is framed within the pump housing to support the radial load (e.g., weight) of the impeller shaft and dampen the vibration.

[0031] In addition, during operation of the pump, the impeller shaft may be subjected to axial loads acting generally parallel to the central axis of the pump and / or impeller shaft. The axial load acting on the impeller may be unbalanced, meaning that the front axial load (e.g., an axial load acting toward the front of the pump) and the rear axial load (e.g., an axial load acting toward the rear portion of the pump) may be unequal and produce an axial thrust of the impeller shaft. The forward or rearward axial thrust may cause the impeller shaft to move along the central axis and cause parts coupled to the impeller shaft (e.g., an impeller, a rotor shaft, a motor armature, etc.) to contact the housing, the motor, and / or other internal parts of the pump. The pump housing includes axial bearings (e.g., hydrodynamic bearings, foil bearings, etc.) that support the axial thrust of the impeller shaft and reduce, prevent, and / or inhibit such movement.

[0032] In some examples, the fluid (e.g., sCO2, oil, liquid helium, etc.) pressurized in the system by the pump can be used to lubricate radial and / or axial bearings to reduce friction between rotating elements within these bearings. For example, the pump can include a flow line from the pump outlet to the axial bearing to provide and / or transmit the pressurized fluid to the thrust bearing.

[0033] As used herein, “streamline” may refer to a path of a fluid (eg, flow path, flow direction, etc.) and / or a structure (eg, pipe, housing, etc.) used to enclose (eg, guide, direct, etc.) a fluid.

[0034] The pressurized fluid flows between the thrust disc, the front thrust pad, and the rear thrust pad of the thrust bearing device, system, and / or assembly. The thrust disc is coupled to the impeller shaft and protrudes radially outward from the impeller shaft, and the thrust pad is coupled to the pump housing and protrudes radially inward toward the impeller shaft. In addition, the pump may include an ejector vane to drive the fluid from the inner portion of the pump housing to the pump outlet. In some examples, the ejector vane protrudes from the rear side of the impeller and plays a similar role to the impeller vane. That is, the fluid approaches the ejector vane along the central axis and is accelerated radially outward from the ejector vane. Therefore, the streamlines and ejector vanes can implement a lubrication circuit from the pump outlet to the axial bearing and back to the ejector vane to provide a continuous fluid flow to the axial load bearing.

[0035] During operation of the pump, the axial thrust of the impeller shaft may act in the forward or aft direction based on the interaction between the impeller vanes / displacer vanes and the fluid. The fluid enters through the pump inlet along the center / rotational / shaft axis toward the impeller, which includes impeller vanes to accelerate the fluid radially outward into the pump outlet, chamber, streamline, housing, etc. The fluid pressure on the front side, end, face, etc. of the impeller may transfer a rear axial load to the impeller shaft in the aft direction.

[0036] Similarly, fluid in the pump housing flows forward along the rotational axis of the impeller shaft and builds pressure on the back side, end, face, etc. of the impeller (e.g., displacer). The fluid pressure on the back side of the impeller can transfer a front load to the impeller shaft in the forward direction.

[0037] When the forward and rearward axial loads are equal in value and act in opposite directions, the pump is said to be "thrust balanced". As used herein, "forward thrust" refers to the unbalanced thrust acting in the forward direction on the impeller shaft due to the forward axial load exceeding the rearward axial load. As used herein, "rearward thrust" refers to the unbalanced thrust acting in the rearward direction on the impeller shaft due to the rearward axial load exceeding the forward axial load.

[0038] In some examples, when the pump is operated at a relatively low rotational speed, angular velocity, operating speed, etc. (e.g., 500, 1000, 2500 revolutions per minute (rpm), etc.), the fluid pressure at the pump inlet exceeds the fluid pressure within the pump housing. Thus, at relatively low operating speeds ("slow speed"), a back thrust of the impeller shaft is induced.

[0039] In some examples, when the pump is operated at a relatively high rotational speed, angular velocity, operating speed, etc. (e.g., 5000, 10000, 25000 rpm, etc.), the fluid pressure in the pump housing exceeds the fluid pressure at the pump inlet. Thus, at relatively high operating speeds ("high speed"), a forward thrust of the impeller shaft is induced.

[0040] When forward thrust or backward thrust is applied to the impeller shaft, despite the axial support of the thrust bearing, it may occur that the impeller shaft is axially displaced (e.g., in a forward or backward direction) by a certain amount (e.g., 0.001, 0.005, 0.010 inches (in), etc.) from the initial position. At some operating speeds of the pump, the axial thrust acting on the impeller shaft may oscillate between the forward direction and the backward direction. At such speeds, the thrust may oscillate at a frequency that known thrust bearings cannot adaptively and / or dynamically support or cannot support quickly, effectively and / or sufficiently. Example thrust bearings that cannot balance pressures may not maintain proper spacing between thrust pads, spacers, thrust disks, etc. In this case, damage to the thrust pads, thrust disks, impeller shaft or other pump components may result.

[0041] The example motor disclosed herein can adjust (e.g., increase or decrease) the torque output of the example pump to mitigate the axial movement of the impeller shaft. The examples disclosed herein utilize conical rotors and conical stators to increase the available torque at the impeller shaft. For example, the axial component of the electromagnetic force between the conical rotor and the conical stator can balance the axial load on the impeller shaft of the example pump. The electromagnetic force generated due to the interaction (e.g., magnetic field) between the conical rotor and the conical stator causes the conical rotor and the rotor shaft to move forward in the pump. This forward movement of the rotor and the rotor shaft can offset the backward movement of the pump during operation.

[0042] In addition, the examples disclosed herein can detect positioning data, operating conditions, environmental conditions, etc. of the example pump to control the current of the example motor. The examples disclosed herein can increase the current of the example motor in response to the axial displacement of the impeller shaft. Additionally or alternatively, the examples disclosed herein can adjust the current of the example motor in response to the operating conditions (e.g., rotational speed, ambient temperature, etc.) of the example impeller shaft. In some examples, increasing the current of the example motor can increase the synthetic electromagnetic force between the example rotor and the example stator, which in turn offsets the forward thrust or backward thrust caused by the impeller shaft. In addition, the example system disclosed herein can improve the operating efficiency of the pump (e.g., a centrifugal sCO2 pump) by minimizing or otherwise reducing the friction energy loss associated with the axial impeller shaft movement. In addition, the example system disclosed herein can increase the time between maintenance services for repairing and / or replacing components of thrust bearings, motors, pumps, etc.

[0043] For the drawings disclosed herein, the same numerals indicate the same elements throughout the drawings. Referring now to the drawings, Figure 1 is a side view of an example aircraft 10. Figure 1As shown, aircraft 10 includes a fuselage 12 and a pair of wings 14 (one shown) extending outwardly from fuselage 12. In the example shown, a gas turbine engine 100 (also referred to as "engine 100") is supported on each wing 14 to propel the aircraft through the air during flight. In addition, aircraft 10 includes vertical stabilizers 16 and a pair of horizontal stabilizers 18 (one shown). However, in some examples, aircraft 10 includes Figure 1 Illustrative examples of engines of different types and / or in different locations.

[0044] Additionally, the aircraft 10 may include a thermal management system 200 for transferring heat between fluids that support the operation of the aircraft 10. More specifically, the aircraft 10 may include one or more accessory systems that are configured to support the operation of the aircraft 10. For example, such accessory systems include a lubrication system that lubricates components of the engine 100, a cooling system that provides cooling air to components of the engine 100, an environmental control system that provides cooled air to a cabin of the aircraft 10, and the like. In such examples, the thermal management system 200 is configured to transfer heat from one or more fluids that support the operation of the aircraft 10 (e.g., oil of a lubrication system, air of a cooling system and / or environmental control system, and the like) to one or more other fluids that support the operation of the aircraft 10 (e.g., fuel supplied to the engine 100). However, in some other examples, the thermal management system 200 is configured to transfer heat between another fluid or component that supports the operation of the aircraft 10.

[0045] Although the examples disclosed herein are reference Figure 1 The aircraft 10 is described in detail, but the examples disclosed herein may be applicable to aircraft 10 used with Figure 1-3 The thermal management system 200 may be substantially similar to the thermal management system of another type or configuration of aircraft. Thus, the present subject matter may be readily adapted for use in another aircraft and / or another heat transfer application associated with another type of vehicle.

[0046] Figure 2 is a schematic cross-sectional view of an example gas turbine engine 100. In the example shown, the engine 100 is configured as a high bypass turbofan engine. However, in some examples, the engine 100 is configured as a propfan engine, a turbojet engine, a turboprop engine, a turboshaft gas turbine engine, etc.

[0047] In general, 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 at least partially surrounded 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 regard, the fan blades 114 are circumferentially spaced and extend radially outward from the fan rotor 112. In addition, 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, which allows the LP spool 106 to rotate the fan blades 114. In addition, a plurality of outlet guide vanes or struts 116 are circumferentially spaced from each other and extend radially between a casing 118 surrounding the LP and HP spools 106, 108 and the nacelle 110. As such, struts 116 support nacelle 110 relative to outer shell 118 such that outer shell 118 and nacelle 110 define a bypass airflow passage 120 positioned therebetween.

[0048] Casing 118 generally surrounds or encloses a compressor section 122 , a combustion section 124 , a turbine section 126 , and an exhaust section 128 in serial flow order.

[0049] In some examples, the compressor section 122 includes a low pressure (LP) compressor 130 of the LP spool 106 and a high pressure (HP) compressor 132 of the HP spool 108 positioned downstream of the LP compressor 130 along the axial centerline 102. Each compressor 130, 132 may in turn include one or more rows of compressor stator vanes 134 interdigitated with one or more rows of compressor rotor blades 136. Thus, the compressors 130, 132 define a compressed air flow path 133 extending therethrough.

[0050] Additionally, in some examples, the turbine section 126 includes a high pressure (HP) turbine 138 of the HP spool 108 and a low pressure (LP) turbine 140 of the LP spool 106 positioned downstream of the HP turbine 138 along the axial centerline 102. Each turbine 138, 140 may in turn include one or more rows of turbine stator vanes 142 interdigitated with one or more rows of turbine rotor blades 144.

[0051] In addition, the LP spool 106 includes a low pressure (LP) shaft 146, and the HP spool 108 includes a high pressure (HP) shaft 148 positioned concentrically about the LP shaft 146. In such an example, the HP shaft 148 rotatably couples 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 shaft 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. In addition, the LP shaft 146 is coupled to the fan 104 via a gearbox 150. In this regard, 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.

[0052] In some examples, the engine 100 generates thrust to propel the aircraft. More specifically, during operation, air 152 enters an inlet portion 154 of the engine 100. The fan 104 supplies a first portion 156 of the air 152 to the bypass airflow passage 120 and a second portion 158 of the air 152 to the compressor section 122. The second portion 158 of the air 152 first flows through the LP compressor 130, where the compressor rotor blades 136 gradually compress the second portion 158 of the air 152. Next, the second portion 158 of the air 152 flows through the HP compressor 132, where the compressor rotor blades 136 continue to gradually compress the second portion 158 of the air 152. The compressed second portion 158 of the air 152 is then delivered to the combustion section 124. In the combustion section 124, the second portion 158 of the air 152 is mixed with fuel and combusted to generate high temperature and high pressure combustion gases 160. Thereafter, the combustion gases 160 flow through the HP turbine 138, wherein turbine rotor blades 144 of the HP turbine 138 extract a first portion of kinetic and / or thermal energy from the combustion gases 160. This energy extraction rotates the HP shaft 148, which drives the HP compressor 132. The combustion gases 160 then flow through the LP turbine 140, wherein turbine rotor blades 144 of the LP turbine 140 extract a second portion of kinetic and / or thermal energy from the combustion gases 160. This energy extraction rotates the LP shaft 146, which drives the LP compressor 130 and the fan 104 via the gearbox 150. The combustion gases 160 then exit the engine 100 through the exhaust section 128.

[0053] As described above, the aircraft 10 may include a thermal management system 200 for transferring heat between fluids that support the operation of the aircraft 10. In this regard, the thermal management system 200 may be located within the engine 100. For example, Figure 2As shown, the thermal management system 200 is positioned within the housing 118 of the engine 100 . However, in some other examples, the thermal management system 200 is positioned at another location within the engine 100 .

[0054] Additionally, in some examples, the engine 100 defines a third stream flow path 170. Generally, the third stream flow path 170 extends from the compressed air flow path 133 defined by the compressor section 122 to the bypass air flow passage 120. In this regard, the third stream flow path 170 allows a portion of the second portion 158 of the air 152 from the compressor section 122 to bypass the combustion section 124. More specifically, in some examples, the third stream flow path 170 defines a concentric or non-concentric passage with respect to the compressed air flow path 133 downstream of one or more of the compressors 130, 132, or the fan 104. The third stream flow path 170 can be configured to selectively remove the second portion 158 of the air 152 from the compressed air flow path 133 via one or more variable guide vanes, nozzles, or other actuatable flow control structures.

[0055] Additionally, as will be described below, in some examples, the thermal management system 200 transfers heat to the air flowing through the third stream flow path 170. However, the pressure and / or flow rate of the fluid (e.g., a heat exchange fluid, such as a supercritical fluid (e.g., sCO2)) within the thermal management system 200 limits the rate at which thermal energy can be transferred between the air and the heat exchange fluid. Additionally, it is advantageous for the thermal management system 200 to generate the pressure and / or flow rate using a pump that supports the axial thrust of a shaft within the pump to increase the life and / or efficiency of the pump and the thermal management system 200.

[0056] Although the examples disclosed herein are reference Figure 2 The gas turbine engine 100 is described in detail, but the examples disclosed herein may be applicable to use with Figure 1-3 The thermal management system 200 may be substantially similar to the thermal management system of another type or configuration of an engine. Thus, the present subject matter may be readily adapted for use with another engine and / or another heat transfer application associated with another type of vehicle.

[0057] Figure 3 is a schematic diagram of an example implementation of a thermal management system 200 for transferring heat between fluids. In general, the thermal management system 200 is as described above and in Figure 1 and Figure 2 1 and 10. However, the thermal management system 200 may be implemented within another type of aircraft and / or another gas turbine engine of another configuration.

[0058] As shown, the thermal management system 200 includes a heat transfer bus 202. Specifically, in some 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 so that heat is added to the heat exchange fluid and / or removed from the heat exchange fluid. In this regard, the heat exchange fluid can be a working fluid, such as sCO2, oil, liquid helium, etc. In addition, in such an example, the thermal management system 200 includes a pump 204 configured to pump the heat exchange fluid through the heat transfer bus 202.

[0059] In addition, 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 regard, the heat source heat exchangers 206 are configured to transfer heat from a fluid supporting the operation of the aircraft 10 to the heat exchange fluid, which cools 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 .

[0060] The heat source heat exchangers 206 may correspond to heat exchangers of many configurations that cool fluids that support the operation of the aircraft 10. In some examples, at least one of the heat source heat exchangers 206 is a heat exchanger of a lubrication system of the engine 100. In such an example, the heat source heat exchangers 206 transfer heat from oil that lubricates the engine 100 to a heat transfer fluid. In some other examples, at least one of the heat source heat exchangers 206 is a heat exchanger of a cooling system of the engine 100. In such an example, the heat source heat exchanger 206 transfers heat from cooling air exhausted from the compressor section 122 (or compressor discharge plenum) of the engine 100 to a heat transfer fluid. However, in some other examples, the heat source heat exchangers 206 correspond to other types of heat exchangers that cool fluids that support the operation of the aircraft 10.

[0061] In addition, the thermal management system 200 includes a plurality of radiator heat exchangers 208 arranged along the heat transfer bus 202. More specifically, the radiator heat exchangers 208 are fluidly coupled to the heat transfer bus 202 such that a heat exchange fluid flows through the radiator heat exchangers 208. In this regard, 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, which heats 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 3Two radiator heat exchangers 208 are shown, but the thermal management system 200 may include three or more radiator heat exchangers 208 .

[0062] The radiator heat exchangers 208 may correspond to many configurations of exchangers that heat fluids that support the operation of the aircraft 10. For example, at least one of the radiator heat exchangers 208 is a heat exchanger of a fuel system of the engine 100. In such an example, the radiator heat exchangers 208 transfer heat from a heat transfer fluid to the fuel supplied to the engine 100. In some other embodiments, at least one of the radiator heat exchangers 208 is a heat exchanger that contacts the first portion 156 of the air 152 flowing through the bypass airflow passage 120 of the engine 100. In such an example, the radiator heat exchangers 208 transfer heat from the heat transfer fluid to the first portion 156 of the air 152 flowing through the bypass airflow passage 120.

[0063] In some examples, one or more of the radiator heat exchangers 208 are configured to transfer heat to the air flowing through the third stream flow path 170. In such examples, the radiator heat exchangers 208 are connected to the air flowing through the third stream flow path 170 ( Figure 2 ) of the air of the third stream flow path 170. Therefore, the heat from the heat exchange fluid flowing through the heat transfer bus 202 can be transferred to the air flowing through the third stream flow path 170. Using the third stream flow path 170 as a radiator of the thermal management system 200 provides one or more technical advantages. For example, the third stream flow path 170 provides greater cooling than other bleed air sources because a larger volume of air flows through the third stream flow path 170 compared with other bleed air flow paths. In addition, the air flowing through the third stream flow path 170 is colder than the air flowing through other bleed air flow paths and the compressor bleed air. In addition, the air in the third stream flow path 170 is pressurized, which allows the radiator heat exchanger 208 to be smaller than the heat exchanger that relies on other radiators in the engine 100. In addition, in the example where the engine 100 is non-ducted, different from using ambient air (e.g., a heat exchanger in contact with the air flowing around the engine 100), using the third stream flow path 170 as a radiator will not increase the resistance on the engine 100. However, in some other examples, radiator heat exchanger 208 corresponds to other types of heat exchangers that heat fluids that support operations of aircraft 10 .

[0064] Additionally, in some examples, 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 adjust the temperature of the heat exchange fluid within the heat transfer bus 202. The flow of the example heat exchange fluid through the bypass conduits 210 is controlled to adjust 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 some other examples, other numbers of heat exchangers 206, 208 may have corresponding bypass conduits 210 as long as at least one bypass conduit 210 is present.

[0065] Additionally, in some 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 a 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 a heat exchange fluid through a bypass conduit 210 that bypasses the radiator heat exchanger 208. In this regard, each valve 212, 214 is fluidly coupled to the heat transfer bus 202 and a corresponding bypass conduit 210. Thus, each valve 212, 214 can be moved between fully and / or partially open and / or closed positions to selectively block heat exchange flow through its corresponding bypass conduit 210.

[0066] The valves 212, 214 are controlled based on the pressure of the heat exchange fluid within the heat transfer bus 202. More specifically, as indicated above, in some cases, 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 may cause accelerated wear. In this regard, when the pressure of the heat exchange fluid within the heat transfer bus 202 exceeds the maximum or otherwise increased pressure value, one or more heat source valves 212 are opened. In this example, 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 through the heat source heat exchanger 206, which reduces the temperature of the fluid and thus reduces the pressure of the fluid. In some examples, the maximum pressure value is between 3800 psi and 4000 psi or less. In some examples, the maximum pressure value is in the range between 2700 psi and 2900 psi, such as 2800 psi. In some other examples, the maximum pressure value is within a range between 1300 psi and 1500 psi, such as 1400 psi. Such a maximum pressure value substantially prevents the thermal management system 200 from causing accelerated wear.

[0067] In some examples, the maximum pressure value is set prior to and / or during operation based on one or more 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, the pump 204, the heat exchangers 206, 208, the bypass conduit 210, and / or the valves 212, 214.

[0068] In contrast, when the pressure of the heat exchange fluid is too low, the pump 204 may experience operability problems and increased wear. Thus, when the pressure of the heat exchange fluid in the heat transfer bus 202 drops to a pressure value below the minimum pressure value or otherwise reduced, one or more of the radiator valves 214 are opened. In this example, at least a portion of the heat exchange fluid flows through the bypass conduit 210 instead of the radiator heat exchanger 208. Therefore, less heat is removed from the heat exchange fluid by the radiator heat exchanger 208, which increases the temperature of the fluid and thus increases the pressure of the fluid. In some examples, the minimum pressure value is 1070 psi or greater. In some examples, the minimum pressure value is between 1150 psi and 1350 psi, such as 1250 psi. In some other examples, the minimum pressure value is between 2400 psi and 2600 psi, such as 2500 psi. This minimum pressure value is typically used when the heat exchange fluid is in a supercritical state (e.g., when the heat exchange fluid is carbon dioxide).

[0069] Thus, 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 some other examples, the range extends from 2500 psi to 2800 psi.

[0070] Thus, the operation of the pump 204 and valves 212 , 214 allows the disclosed thermal management system 200 to maintain the pressure of the heat exchange fluid within the heat transfer bus 202 within a specified range of values ​​as the thermal load imposed on the thermal management system 200 changes.

[0071] In addition, an example pump 204 drives the heat exchange fluid through the thermal management system 200. In some examples, the thermal management system 200 includes one pump 204 or multiple pumps 204, depending on the desired flow rate, the delta pressure on the pump 204, and / or the kinetic energy loss of the heat exchange fluid in the heat transfer bus 202. For example, the pump 204 can increase the output head to accelerate the flow of the heat exchange fluid to a first flow rate. As the heat exchange fluid passes through the heat transfer bus 202, the example kinetic energy of the heat exchange fluid is dissipated due to friction, temperature changes, etc. Due to the kinetic energy loss, the heat exchange fluid is decelerated to a second flow rate at a point upstream of the pump 204. When the example second flow rate is lower than the desired operating flow rate of the heat exchange fluid, the pump 204 can be a different architecture that outputs a higher first flow rate, or one or more additional pumps 204 can be included in the thermal management system 200.

[0072] Figure 4 is an example heat transfer bus pump 400 (e.g., sCO2 pump, Figure 3 A schematic diagram of a pump 204, etc. Figure 4 In the illustrated example, a heat transfer bus pump 400 drives a heat exchange fluid (such as (sCO2)) through one or more fluid conduits 402 (eg, Figure 3 Specifically, the heat exchange fluid flows through an inlet pipe 404 and encounters an impeller 406 (e.g., a compressor wheel), which rotates to drive the heat exchange fluid through a pump outlet 408 that is fluidly coupled to the fluid conduit 402. In turn, the fluid conduit 402 can supply the heat exchange fluid to one or more heat exchangers (e.g., Figure 3 heat exchangers 206, 208). Thus, the heat transfer bus pump 400 can pump heat exchange fluid to manage Figure 1 The aircraft 10 and / or Figure 2 of the working fluid associated with the gas turbine engine 100 .

[0073] exist Figure 4 In the example shown, the heat transfer bus pump 400 includes a motor 410 positioned in a motor housing 412. Figure 4 4, the motor 410 is an induction motor operably coupled to a variable frequency drive (VFD) and a control circuit (not shown) (such as a full authority digital engine controller (FADEC)) that controls the speed of the motor 410. For example, the control circuit can operate the motor 410 based on the pressure and / or temperature of the heat exchange fluid in the fluid conduit 402 and / or the heat transfer bus pump 400. In some examples, the control circuit can operate the motor 410 based on the pressure and / or temperature of the working fluid affected by the heat exchange fluid. Additionally or alternatively, the control circuit can operate the motor 410 based on vibration measurements obtained by an accelerometer operably coupled to the heat transfer bus pump 400 and / or the fluid conduit 402.

[0074] exist Figure 4 4, the motor housing 412 is at least partially surrounded by a cooling jacket 414 to prevent the motor 410 from overheating. The rear end of the motor housing 412 is coupled to the rear bearing housing 416 via a first bolt 418. In addition, the end cap 420 is coupled to the rear bearing housing 416 via the first bolt 418. The front end of the motor housing 412 is coupled to a front bearing housing 422 opposite to the rear bearing housing 416 via a second bolt 424. In addition, the front bearing housing 422 is coupled to a back plate 426 and a pump outlet 408 on the opposite side of the back plate 426 via the second bolt 424.

[0075] exist Figure 4In the example shown, the motor 410 includes a stator 428 for inducing alternating current in the field coils and emitting an alternating magnetic field around the central axis of the motor 410. The alternating magnetic field interacts with the permanent magnets of the rotor 430, thereby providing torque to the rotor 430. The rotor 430 is fixedly coupled to an impeller shaft 432 ("shaft 432"), and the shaft is fixedly coupled to the impeller 406. In this way, the motor 410 drives the rotation of the shaft 432, which in turn drives the rotation of the impeller 406. The rear end of the shaft 432 is supported by a first radial foil bearing 434 coupled to the rear bearing housing 416. Similarly, the front end of the shaft 432 is supported by a second radial foil bearing 436 coupled to the front bearing housing 422.

[0076] The first radial foil bearing 434 and the second radial bearing 436 include spring-loaded foil journal bushings that support the radial load of the shaft 432 during relatively low (e.g., startup) rotational speeds (e.g., 0-5000 revolutions per minute (rpm), etc.). When the motor 410 rotates the shaft 432 at relatively high (e.g., operating) rotational speeds (e.g., 5000-20000 rpm, etc.), the pressure of the working medium (e.g., air, oil, sCO2, etc.) increases and pushes the foil bushings radially outward. Therefore, when the shaft 432 rotates at operating speeds (e.g., 3000 rpm, 10000 rpm, 25000 rpm, etc.), the pressurized working medium supports the radial load of the shaft 432.

[0077] exist Figure 4 In the example shown, the thrust disk 438 of the shaft 432 is supported by a thrust bearing system 440. For example, the thrust bearing system 440 may include a foil bearing to support the axial load of the shaft 432 via interaction with the thrust disk 438. In some examples, the thrust bearing system 440 is coupled to the rear bearing housing 416 and / or the end cap 420 via bolts.

[0078] The example impeller 406 of the heat transfer bus pump 400 includes ejector vanes 442 on the rear portion of the impeller 406. At the operating speed of the motor 410, the ejector vanes 442 cause the working fluid (e.g., sCO2) to flow forward into the fluid conduit 402 from the front bearing housing 422, the motor housing 412, etc.

[0079] exist Figure 4In the illustrated example, an example sCO2 fluid flows into the heat transfer bus pump 400 through the fluid conduit 402, as indicated by the arrow indicating the flow direction 444. At a low speed (e.g., a starting speed) of the motor 410, the flow direction 444 of the example sCO2 exerts a back thrust 446 on the impeller 406 and the shaft 432, as indicated by the arrow indicating the direction of the back thrust 446. At a high speed (e.g., an operating speed) of the motor 410, the ejector vanes 442 drive the heat exchange fluid within the heat transfer bus pump 400 forward toward the pump outlet 408, and the fluid generates a forward thrust 448 on the impeller 406 and the shaft 432, as indicated by the arrow indicating the direction of the forward thrust 448. A thrust bearing system 440 is included in the heat transfer bus pump 400 to support the back thrust 446 and the forward thrust 448 of the shaft 432.

[0080] In some examples, the heat transfer bus pump 400 includes an example outer flow line 450 that branches from the pump outlet 408 to provide sCO2 as a working medium to the thrust bearing system 440 and support the thrust disk 438 when pressurized. Additionally or alternatively, the outer flow line 450 branches from the fluid conduit 402 and / or the ejector vane 442. The example outer flow line 450 can bypass one or more of the motor housing 412, the rear bearing housing 416, the front bearing housing 422, and / or the back plate 426 to approach the thrust bearing system 440.

[0081] In some examples, the heat transfer bus pump 400 includes an example inner flow line 452 that branches from the ejector vane 442 to provide sCO2 as a working medium to the thrust bearing system 440 and support the thrust disk 438 when pressurized. Additionally or alternatively, the inner flow line 452 branches from the fluid conduit 402 and / or the pump outlet 408. The example inner flow line 452 can pass through one or more of the motor housing 412, the rear bearing housing 416, the front bearing housing 422, and / or the back plate 426 to access the thrust bearing system 440.

[0082] Figure 4 The outer streamlines 450 and inner streamlines 452 are shown as example configurations to reflect the approximate location of the streamlines and the direction of flow. Figure 4 4 shows an outer flow line 450 and an inner flow line 452, but only one may be included in the heat transfer bus pump 400 to achieve the same function. The heat transfer bus pump 400 may be configured with an outer flow line 450 to reduce complexity during manufacturing and / or assembly and reduce the risk of internal leaks. The heat transfer bus pump 400 may be configured with an inner flow line 452 to reduce the amount of space occupied by the heat transfer bus pump 400. Figure 4 Also shown in FIG. 4 are first return flow lines 454 and second return flow lines 456 to generally depict the exit point and flow direction of the working fluid from the thrust bearing system 440 to the ejector vanes 442 .

[0083] Figure 5 is used to monitor the system (for example, Figure 3 2 is a cross-sectional view of a first example pump system 500 for pressurizing a fluid (e.g., a heat exchange fluid, such as sCO2) in a thermal management system 200 of the present invention. The example pump system 500 includes an example motor 502 and an example impeller 504. The example motor 502 includes an example rotor shaft 506, an example rotor 508, and an example stator. In this example, the motor 502 included in the example pump system 500 is similar to Figure 4 The heat transfer pump 400. However, the example motor 502 may be included in any other example system. Figure 5 The example pump system 500 shown in FIG. 5 includes an impeller 504 to pressurize a fluid (e.g., sCO2) in the system. The example impeller 504 is connected to a rotor shaft 506 (e.g., an impeller shaft) and rotates at the same speed as the rotor shaft 506. In some examples, the impeller 504 is the same or similar to an impeller used in a centrifugal pump and includes blades or vanes to deflect the incoming fluid flow radially outward to an outlet streamline (e.g., Figure 4 The example impeller 504 converts the mechanical power of the motor 502 (eg, the rotor shaft 506 and the stator 510) into the fluid power of the fluid flow.

[0084] exist Figure 5 In the example pump system 500 of the embodiment, the stator 510 exerts a torque on the rotor 508. Since the example rotor 508 is connected (e.g., fixedly coupled) to the rotor shaft 506 (e.g., via bolts, adhesives, interference fits, etc.), the stator 510 causes the rotor 508 and the rotor shaft 506 to rotate, while the stator 510 remains stationary. In some examples, the stator 510 includes field magnets (e.g., electromagnets or permanent magnets) that generate magnetic fields based on currents (e.g., DC or AC) passing through various electromagnets of the stator 510. The example stator 510 generates a first set of magnetic fields that exert a force on a second set of magnetic fields generated by the rotor 508. The example rotor 508 generates a second set of magnetic fields via permanent magnets or electromagnets. Therefore, the stator 510 and the rotor 508 are magnetically coupled. Since the example stator 510 is stationary and fixed in place, the force causes the example rotor 508 to rotate and generate torque. Because the example rotor shaft 506 is connected to the example rotor 508 , the rotor shaft 506 produces the same torque and rotates at the same angular velocity.

[0085] The example rotor 508 and the example stator 510 have a generally conical shape. The example rotor 508 includes a first example end 512 having a first outer diameter and a second example end 514 having a second outer diameter, the second diameter being different from (e.g., smaller than) the first diameter. For example, the ratio between the second diameter and the first diameter can vary in the range of 1.3 to 3.0. In other words, the example rotor 508 includes at least one example conical surface 516 (e.g., a first example conical surface 516) defined by an angle greater than 0 degrees and less than 90 degrees relative to the centerline of the motor 502. The first example conical surface 516 is the outer surface of the rotor 508 facing away from the rotor shaft 506. In this example, the example inner surface 518 of the rotor 508 faces the rotor shaft 506. In addition, the example inner surface 518 is substantially parallel to the rotor shaft 506 (e.g., within 5 degrees). The example stator 510 is aligned with the example rotor 508 (e.g., concentrically aligned, concentric, coaxial, etc.). Thus, the example stator 510 is positioned around the first tapered surface 516. In this example, the stator 510 includes a second example tapered surface 520 that is aligned with the first tapered surface 516. In some examples, the pump system 500 can include an example motor housing 522 that surrounds (e.g., covers) the motor 502, the rotor 508, and the stator 510.

[0086] During operation of the example pump system 500, the example tapered surfaces 516, 520 cause the resultant magnetic force (from the magnetic interaction between the stator 510 and the rotor 508) to be tilted or angled. Figure 5 524, 526. The axial components of the resultant force vectors 524, 526 can counteract (e.g., balance) axial loads in the pump system 500. For example, the resultant force represented by the vectors 524, 526 can cause the rotor 508 and the rotor shaft 506 to move forward in the pump system 500. This forward movement of the rotor 508 and the rotor shaft 506 can counteract rearward movement of the rotor shaft 506 during operation.

[0087] Figure 6 600 is a cross-sectional view of a second example pump system 600 for pressurizing a fluid in a system. The example pump system 600 includes an example motor 602. The example motor 602 includes an example rotor shaft 604, an example rotor 606, and an example stator 608. Figure 6 The example rotor 606 is similar to Figure 5 Example rotor 508. However, Figure 6The example rotor 606 in includes a first example conical portion 610 adjacent to a second example conical portion 612. The first example conical portion 610 includes a first example conical surface 614, and the second example conical portion 612 includes a second example conical surface 616 adjacent to the first conical surface 614. In this example, the first and second conical surfaces 614, 616 face away from the rotor axis 604. In some examples, the first example conical surface 614 is positioned (e.g., tilted) at a first angle (e.g., 20 degrees) relative to the rotor axis 604, and the second conical surface 616 is positioned at a second angle (e.g., 10 degrees) relative to the rotor axis 604, and the second angle is different from the first angle. In some examples, the first conical surface 614 or the second conical surface 616 can be substantially parallel to the example rotor axis 604 (e.g., within 5 degrees). In addition, the example stator 608 is aligned with the conical surfaces 614, 616. Example inner surfaces 618, 620 of the stator 608 surround the tapered surfaces 614, 616 of the rotor 606. In this example, the inner surfaces 618, 620 can be tapered to align with the tapered surfaces 614, 616 of the rotor 606. In some examples, the pump system 600 can include an example motor housing 622 that surrounds (e.g., covers) the motor 602, the rotor 606, and the stator 608.

[0088] During operation of the example pump system 600, the example conical surfaces 614, 616, 618, 620 of the rotor 606 and the stator 608 tilt the resultant magnetic force between the rotor 606 and the stator 608 in the direction generally indicated by the example resultant force vectors 624, 626, 628, 630. The axial component of the resultant force vectors 624, 626, 628, 630 can counteract (e.g., balance) the axial loads in the pump system 600. For example, the resultant force represented by the vectors 626, 630 can cause the rotor 606 and the rotor shaft 604 to move forward in the pump system 600. This forward movement of the rotor 606 and the rotor shaft 604 can counteract the rearward movement of the rotor shaft 604 during operation. Additionally or alternatively, the resultant force represented by the vectors 624, 628 can cause the rotor 606 and the rotor shaft 604 to move backward in the pump system 600. This rearward movement of rotor 606 and rotor shaft 604 may offset forward movement of rotor shaft 604 during operation.

[0089] Figure 7 700 is a cross-sectional view of a third example pump system 700 for pressurizing a fluid in a system. The example pump system 700 includes an example motor 702. The example motor 702 includes an example rotor shaft 704, an example rotor 706, and an example stator 708. Figure 7 The example pump system 700 is similar to Figure 5500. However, the example pump system 700 includes an example thrust plate 710 coupled to the rotor shaft 704. In this example, the thrust plate 710 is positioned in front of the motor 702. In other examples, the thrust plate 710 is positioned behind the motor 702. Figure 7 , the example resultant force vectors 712, 714 generated due to the conical shape of the rotor 706 and the stator 708 can counteract (e.g., balance) axial loads in the pump system 700. For example, the resultant force represented by the vectors 712, 714 can cause the rotor 706 and the rotor shaft 704 to move forward in the pump system 700. This forward movement of the rotor 706 and the rotor shaft 704 can counteract the rearward movement of the rotor shaft 704 during operation. Additionally or alternatively, the example thrust disk 710 can prevent or otherwise reduce axial movement of the rotor shaft 704. The example thrust disk 710 is fixed to the rotor shaft 704 and extends from the rotor shaft 704 substantially perpendicular (e.g., within 5 degrees) to the example rotational axis of the rotor shaft 704. When the rotor shaft 704 rotates, axial and / or thrust loads are transferred to the thrust disk 710 to counteract the axial loads from the rotor shaft 704 while allowing the rotor shaft 704 to rotate.

[0090] Figure 8 800 is a cross-sectional view of a fourth example pump system 800 for pressurizing a fluid in a system. The example pump system 800 includes an example motor 802 including an example rotor shaft 804 , an example rotor 806 , and an example stator 808 . Figure 8 The example pump system 800 is similar to Figure 7 However, the example pump system 800 includes an example piston seal 810 positioned adjacent to the example thrust plate 812. Figure 8 800 , the example resultant force vectors 814, 816 generated due to the conical shape of the rotor 806 and the stator 808 can counteract (e.g., balance) axial loads in the pump system 800. For example, the resultant force represented by the vectors 814, 816 can cause the rotor 806 and the rotor shaft 804 to move forward in the pump system 800 to counteract the rearward movement of the rotor shaft 804 during operation. Additionally or alternatively, the example thrust disk 812 can prevent or otherwise reduce axial movement of the rotor shaft 804. When the rotor shaft 804 rotates and transmits an axial or thrust load to the thrust disk 812, the example piston seal 810 counteracts (e.g., cushions, supports, etc.) the axial load from the thrust disk 812 while allowing the rotor shaft 804 to rotate.

[0091] Fig. 9 is an example diagram of a first example process 900 for controlling the current provided to an example motor. For purposes of explanation, reference is made to Figure 5The example process 900 is described with reference to the example pump system 500. However, the example process 900 may be performed in any of the following manners: Figure 6 Example pump system 600, Figure 7 Example pump system 700 or Figure 8 The example pump system 800 of the present invention is implemented in the example pump system 800 of the present invention. The first example process 900 includes example sensor output data 902 from an example sensor to determine the axial position of the motor 502 relative to the rotor shaft 506 (e.g., an axial position estimate). In particular, the example sensor can determine the displacement between the stator 510 and the rotor 508, and the rotor 508 is fixedly coupled to the rotor shaft 506. In some examples, the sensor can be positioned at the motor housing 522 or any other location near the motor 502 (e.g., disposed on the motor housing 522 or any other location near the motor 502, adjacent to the motor housing 522 or any other location near the motor 502, etc.). In some examples, the motor 502 can be a permanent magnet embedded in a steel motor (PMSM), a switched reluctance motor (SRM), or an induction motor. In some examples, the sensor can be a Hall effect sensor, a variable reluctance sensor, an optical sensor, an eddy current sensor, a linear variable differential transformer (LVDT) sensor, etc.

[0092] exist Fig. 9 In block 906, the example controller circuit 904 controls (e.g., adjusts, changes, manages, etc.) the current of the example motor 502. The example process 900 begins when the example sensor output data 902 indicates movement of the motor 502 relative to the rotor shaft 506. For example, when a forward thrust or a backward thrust is applied to the rotor shaft 506, an axial displacement (e.g., in a forward direction or a backward direction) of the rotor shaft 506 (and the rotor 508) may occur from an initial position. At block 906, the example controller circuit 904 converts the sensor output data 902 from a three-phase (abc) signal to a dq rotating reference frame (dq). At example nodes 908, 910, the example controller circuit 904 converts the sensor output data 902 from a three-phase (abc) signal to a dq rotating reference frame (dq). Based on the example sensor output data 902 and the initial current input (I q * and I d * ) to determine the adjusted current input (I q and I d ). In this example, the current on the orthogonal (q) axis (e.g., I q and I q * ) represents the axis on which the motor 502 generates torque. In addition, the current on the DC (d) axis (e.g., I d and I d * ) represents the axis on which the motor 502 generates flux.

[0093] The example process 900 includes an example proportional-integral (PI) controller 912 to monitor the regulated current input I q The example controller circuit 904 may modify (eg, increase or decrease) the adjusted current input I based on deviations, error messages, etc. from the PI controller 912. q Additionally, the example process 900 includes an example PI controller 914 to monitor the regulated current input I d The example controller circuit 904 may modify the regulated current input I based on deviations, error messages, etc. from the PI controller 914. d Due to the example decoupling network 916, the example controller circuit 904 can independently control the regulated current input I q ,I d In addition, the example controller circuit 904 can determine the output voltage (V q * ) and the output voltage on the d-axis (V d * ).

[0094] At block 918, the example controller circuit 904 converts the output voltage V from the dq reference frame to q * and V d * Converted into three-phase (abc) signal (V a,b,c * ). Thus, the example pulse width modulator (PWM) 920 can control the speed of the motor 502 via a series of pulses / signals. At block 922, the example controller circuit 904 converts the pulses from the PWM 920 from direct current (DC) to alternating current (AC). In some examples, the example analog-to-digital converter (ADC) 924 converts the pulses from AC to DC. In turn, the example motor 502 accesses the pulses from the PWM 920 and adjusts the current accordingly.

[0095] Through the example process 900, the example sensor can detect the rearward displacement of the rotor shaft 506 relative to the stator 510. The example controller circuit 904 can adjust the amount of current supplied to the motor 502 based on this displacement. In some examples, increasing the amount of current supplied to the motor 502 can increase the speed of the motor 502, which in turn can increase the magnitude of the resultant force vectors 524, 526 (caused by the generally conical shape of the rotor 508 and the stator 510). As a result, the increased resultant force causes the rotor 508 and the rotor shaft 506 to move forward in the pump system 500, which balances the initial rearward displacement of the rotor shaft 506. The example controller circuit 904 can determine the current supplied to the motor 502 based on the displacement of the rotor shaft 506. In other words, the example resultant forces 524, 526 are the current (I q and I d ) function.

[0096] Additionally or alternatively, the example sensor can detect the forward displacement of the rotor shaft 506 relative to the stator 510. The example controller circuit 904 can reduce the amount of current supplied to the motor, which reduces the speed of the motor 502 and reduces the resultant forces 524, 526 (caused by the generally conical shapes of the rotor 508 and the stator 510). As a result, the reduced resultant forces 524, 526 cause the rotor 508 and the rotor shaft 506 to move backward in the pump system 500, which balances the initial forward displacement of the rotor shaft 506.

[0097] Fig.10 is an example diagram of a second example process 1000 for controlling current supplied to an example motor. For purposes of explanation, reference is made to Figure 5 The example process 1000 is described with reference to the example pump system 500. However, the example process 1000 may be used in Figure 6 Example pump system 600, Figure 7 Example pump system 700 or Figure 8 The example pump system 800 is implemented in FIG. Fig.10 An example of processing 1000 is similar to Fig. 9900 . However, instead of the example sensor output data 902 , the example controller circuit 1002 accesses the example operating conditions 1004 of the pump system 500 to determine the current supply of the motor 502 . In some examples, the operating conditions 1004 of the pump system 500 may include motor speed, motor temperature, etc. For example, when the operating conditions 1004 of the pump system 500 indicate that the motor 502 is operating at a relatively high speed (e.g., 60,000 rpm), the example controller circuit 1002 may adjust the current supply of the motor 502 to balance the displacement between the rotor shafts 506 . In some examples, the speed of the motor 502 may be compared to an example threshold value. For example, if the speed of the motor 502 exceeds the example threshold value, the example controller circuit 904 may reduce the current supply of the motor 502 to prevent or limit the forward displacement of the rotor shaft 506 relative to the stator 510. In this example, reducing the speed of the motor 502 can reduce the magnitude of the resultant forces 524, 526 (caused by the generally conical shapes of the rotor 508 and the stator 510) and balance the forward displacement of the rotor shaft 506. Therefore, the example controller circuit 1002 can determine the current supplied to the motor 502 based on the operating conditions 1004 of the pump system 500.

[0098] Fig.11 is an example diagram of a third example process 1100 for controlling the current provided to an example motor. For purposes of explanation, reference is made to Figure 7 The example process 1100 is described with reference to the example pump system 700 of FIG. However, the example process 1100 may also be performed in Figure 8 The example pump system 800 is implemented in FIG. Fig.11 The example process 1100 is similar to Fig. 9 900. However, the example process 1100 also includes an example differential pressure transducer 1102 and an example gas control valve 1104. The example differential pressure transducer 1102 detects (e.g., monitors, senses, etc.) a pressure balance / imbalance associated with the thrust plate 710. The example gas control valve 1104 can allow or prohibit bleed air from flowing into an example bearing chamber corresponding to the thrust plate 710. Thus, the example gas control valve 1104 can change the pressure level in the bearing chamber. In this example, the differential pressure transducer 1102 is coupled to the gas control valve 1104. Thus, the example differential pressure transducer 1102 can monitor the pressure (e.g., pressure change) associated with the gas control valve 1104. The example gas control valve 1104 and the example differential pressure transducer 1102 can be positioned in a conduit outside (e.g., outside) the motor 702.

[0099] In some examples, the example controller circuit 1106 determines the current supply to the motor 702 based on the pressure data from the differential pressure transducer 1102. For example, the axial displacement of the rotor shaft 704 may cause the axial displacement of the thrust disk 710. Such displacement of the thrust disk 710 will cause a pressure imbalance on the front side or the rear side of the thrust disk 710. The example differential pressure transducer 1102 can detect such pressure imbalance associated with the thrust disk 710. In particular, the pressure imbalance data can indicate the axial displacement of the thrust disk 710, thereby indicating the axial displacement of the rotor shaft 704. The example controller circuit 1106 can adjust the current supply to the motor 702 to balance such displacement between the rotor shaft 704 and the stator 708. Therefore, the example controller circuit 1106 can determine the current supplied to the motor 702 based on the displacement of the rotor shaft 704 (determined by the sensor output data 902) and the pressure imbalance data associated with the thrust disk 710.

[0100] Fig.12 is an example diagram of a fourth example process 1200 for controlling the current provided to an example motor. For purposes of explanation, reference is made to Figure 7 The example process 1200 is described with reference to the example pump system 700. However, the example process 1200 may be performed in any of the following manners: Figure 8 The example pump system 800 is implemented in FIG. Fig.12 The example process 1200 is similar to Fig.11 100 . However, instead of the example sensor output data 902 , the example controller circuit 1202 accesses the operating condition 1004 and the pressure output data of the pump system 700 to determine the current supply to the motor 702 . For example, the example controller circuit 1202 can determine a position estimate (e.g., a displacement estimate) of the rotor shaft 704 based on the operating condition 1004 of the pump system 700 . In addition, the example controller circuit 1202 accesses pressure data from a differential pressure transducer 1102 . In this example, the differential pressure transducer 1102 detects a pressure imbalance associated with the thrust disk 710 . For example, the differential pressure transducer 1102 can detect a pressure imbalance caused by an axial displacement of the rotor shaft 704 and the thrust disk 710 . Therefore, the example controller circuit 1202 can determine the current supplied to the motor 702 based on the position estimate of the rotor shaft 704 and the pressure imbalance data associated with the thrust disk 710 .

[0101] Fig.13 A flowchart representing example machine readable instructions that may be executed to configure a processor circuit to implement Fig. 9 The controller circuit 904, Fig.10 The controller circuit 1002, Fig.11 The controller circuit 1106 or Fig.12The machine-readable instructions may be for use by a processor circuit (e.g., the following in conjunction with Fig.14 The processor circuit 1412 shown in the example processor platform 1400 discussed above) may be one or more executable programs or portions of executable programs executed by the processor circuit 1412 shown in the example processor platform 1400 discussed above. The program may be embodied in software stored on one or more non-transitory computer-readable storage media (e.g., compact disk (CD), floppy disk, hard disk drive (HDD), solid-state drive (SSD), digital versatile disk (DVD), Blu-ray disk, volatile memory (e.g., any type of random access memory (RAM), etc.) or non-volatile memory (e.g., electrically erasable programmable read-only memory (EEPROM), flash memory, HDD, SSD, etc.) associated with a processor circuit located in one or more hardware devices, but the entire program and / or its portions may alternatively be executed by one or more hardware devices other than the processor circuit and / or embodied in firmware or dedicated hardware. The machine-readable instructions may be distributed across multiple hardware devices and / or executed by two or more hardware devices (e.g., server and client hardware devices). For example, the client hardware device may be implemented by an endpoint client hardware device (e.g., a hardware device associated with a user) or an intermediate client hardware device (e.g., a radio access network (RAN) gateway that can facilitate communication between a server and an endpoint client hardware device). Similarly, a non-transitory computer-readable storage medium may include one or more media located in one or more hardware devices. In addition, although the example programs are referenced Fig.13 , but many other methods of implementing controller circuit 904, controller circuit 1002, controller circuit 1106, or controller circuit 1202 may be used instead. For example, the order of execution of the blocks may be changed, and / or some of the blocks described may be changed, eliminated, or combined. Additionally or alternatively, any or all of the blocks may be implemented by one or more hardware circuits (e.g., processor circuits, discrete and / or integrated analog and / or digital circuits, FPGAs, ASICs, comparators, operational amplifiers (op-amps), logic circuits, etc.) that are constructed to perform corresponding operations without executing software or firmware. The processor circuit may be distributed in different network locations and / or in one or more hardware devices (e.g., single-core processors (e.g., single-core central processing unit (CPU)), multi-core processors (e.g., multi-core CPUs, XPUs, etc.)) located in a single machine, multiple processors distributed on multiple servers in a server rack, multiple processors distributed on one or more server racks, CPUs and / or FPGAs located in the same package (e.g., the same integrated circuit (IC) package or in two or more independent housings, etc.) local.

[0102] The machine-readable instructions described herein may be stored in one or more of a compressed format, an encrypted format, a segmented format, a compiled format, an executable format, a packaged format, etc. The machine-readable instructions as described herein may be stored as data or data structures (e.g., stored as portions of instructions, codes, representations of codes, etc.) that can be used to create, manufacture, and / or generate machine-executable instructions. For example, the machine-readable instructions may be segmented and stored on one or more storage devices and / or computing devices (e.g., servers) located in the same or different locations (e.g., in the cloud, edge devices, etc.) of a network or a collection of networks. The machine-readable instructions may need to be installed, modified, adapted, updated, combined, supplemented, constructed, decrypted, decompressed, unpacked, distributed, redistributed, compiled, etc., so that they can be directly read, interpreted, and / or executed by a computing device and / or other machine. For example, the machine-readable instructions may be stored in multiple parts that are individually compressed, encrypted, and / or stored on separate computing devices, where the parts form a set of machine-executable instructions when decrypted, decompressed, and / or combined, and the set of machine-executable instructions implements one or more operations that can together form a program such as described herein.

[0103] In another example, the machine-readable instructions may be stored in a state where they can be read by a processor circuit, but require the addition of a library (e.g., a dynamic link library (DLL)), a software development kit (SDK), an application programming interface (API), etc., in order to execute the machine-readable instructions on a particular computing device or other device. In another example, it may be necessary to construct the machine-readable instructions (e.g., stored settings, data inputs, recorded network addresses, etc.) before the machine-readable instructions and / or corresponding programs can be executed in whole or in part. Therefore, as used herein, a machine-readable medium may include machine-readable instructions and / or programs regardless of the particular format or state of the machine-readable instructions and / or programs when stored or otherwise at rest or in transmission.

[0104] The machine-readable instructions described herein may be represented by any past, present, or future instruction language, scripting language, programming language, etc. For example, the machine-readable instructions may be represented using any of the following languages: C, C++, Java, C#, Perl, Python, JavaScript, Hypertext Markup Language (HTML), Structured Query Language (SQL), Swift, etc.

[0105] As mentioned above, Fig.13The example operations of may be implemented using executable instructions (e.g., computer and / or machine readable instructions) stored on one or more non-transitory computer and / or machine readable media (e.g., optical storage devices, magnetic storage devices, HDDs, flash memory, read-only memory (ROM), CDs, DVDs, caches, any type of RAM, registers, and / or any other storage device or storage disk that stores information for any duration (e.g., extended period of time, permanent, transient instances, temporary buffering and / or cached information)). As used herein, the terms non-transitory computer readable medium, non-transitory computer readable storage medium, non-transitory machine readable medium, and non-transitory machine readable storage medium are expressly defined to include any type of computer readable storage device and / or storage disk, and to exclude propagating signals and to exclude transmission media. As used herein, the terms "computer readable storage device" and "machine readable storage device" are defined to include any physical (mechanical and / or electrical) structure that stores information, but to exclude propagating signals and to exclude transmission media. Examples of computer-readable storage devices and machine-readable storage devices include any type of random access memory, any type of read-only memory, solid-state memory, flash memory, optical disks, magnetic disks, disk drives, and / or redundant array of independent disks (RAID) systems. As used herein, the term "device" refers to a physical structure (such as a mechanical and / or electrical device, hardware, and / or circuit) that may or may not be constructed from computer-readable instructions, machine-readable instructions, etc., and / or manufactured to perform computer-readable instructions, machine-readable instructions, etc.

[0106] Fig.13 It means respectively about Figure 5-8 The example pump systems 500, 600, 700, 800 and respectively Figure 9-12 Flowchart of an example method 1300 described in the example processes 900, 1000, 1100, 1200 of the present invention. The example method 1300 controls the current provided to the example motors (e.g., motor 502, motor 602, motor 702, motor 802) disclosed herein. The method 1300 begins at block 1302, where an example controller circuit (e.g., controller circuit 904, controller circuit 1002, controller circuit 1106, controller circuit 1202) determines positioning information of an example rotor shaft (e.g., rotor shaft 506, rotor shaft 604, rotor shaft 704, rotor shaft 804) relative to an example stator (e.g., stator 510, stator 608, stator 708, stator 808). In some examples, the controller circuit 904 determines positioning information (e.g., first positioning information, initial positioning information, first axial position, etc.) of the rotor shaft 506 relative to the stator 510.

[0107] At block 1304, the example controller circuit 904 detects a change in the position of the rotor shaft 506. In some examples, the controller circuit 904 detects second positioning information (e.g., changed positioning information, second axial position, etc.) of the rotor shaft 506 relative to the stator 510. In some examples, the second positioning information is different from the first positioning information. In some examples, the controller circuit 904 determines that the second positioning position is in front of the stator 510 or behind the stator 510. Therefore, the example controller circuit 904 can determine a forward movement / displacement or a backward movement / displacement of the rotor shaft 506. In some examples, the controller circuit 904 can detect the changed position of the rotor shaft 506 via sensor output data 902 from an example sensor positioned adjacent to the rotor 508. In some examples, the sensor output data 902 includes the first positioning information and the second positioning information.

[0108] In some examples, the controller circuit 1002 or the controller circuit 1202 determines the second positioning information based on the operating conditions (e.g., speed) of the rotor 706 and the rotor shaft 704. In some examples, the controller circuit 1106 or the controller circuit 1202 can detect the changing position of the rotor shaft 704 via pressure data from the differential pressure transducer 1102 positioned adjacent to the thrust disk 710. For example, the differential pressure transducer 1102 can obtain pressure data corresponding to the front and rear sides of the thrust disk 710. In such an example, the example controller circuit 1106 can detect the changing position of the thrust disk 710 based on the pressure data. Therefore, the changing position of the thrust disk 710 (connected to the rotor shaft 704) can indicate the changing position of the rotor shaft 704.

[0109] At block 1306, the example controller circuit 904 adjusts a current flow rate (e.g., current amount, current supply, current flow, etc.) associated with the rotor 508 and the stator 510 (the motor 502) in response to the changed position of the rotor shaft 506. In some examples, the controller circuit 904 adjusts the current flow rate based on the second positioning information. In some examples, the controller circuit 904 increases the current of the rotor 508 and the stator 510 in response to the forward movement of the rotor shaft 506. In other examples, the controller circuit 904 decreases the current of the rotor 508 and the stator 510 in response to the rearward movement of the rotor shaft 506.

[0110] Fig.14 is a block diagram of an example processor platform 1400 that is structured to execute and / or instantiate Fig.131400 to implement example processes 900, 1000, 1100, 1202. Processor platform 1400 may be, for example, a server, a personal computer, a workstation, a self-learning machine (eg, a neural network), or any other type of computing device.

[0111] The processor platform 1400 of the illustrated example includes a processor circuit 1412. The processor circuit 1412 of the illustrated example is hardware. For example, the processor circuit 1412 may be implemented by one or more integrated circuits, logic circuits, FPGAs, microprocessors, CPUs, GPUs, DSPs, and / or microcontrollers from any desired family or manufacturer. The processor circuit 1412 may be implemented by one or more semiconductor-based (e.g., silicon-based) devices. In this example, the processor circuit 1412 is implemented separately. Figure 9-12 The example controller circuit 904, the example controller circuit 1002, the example controller circuit 1106, or the example controller circuit 1202.

[0112] The processor circuit 1412 of the illustrated example includes a local memory 1413 (e.g., cache, registers, etc.). The processor circuit 1412 of the illustrated example communicates with a main memory including a volatile memory 1414 and a non-volatile memory 1416 via a bus 1418. The volatile memory 1414 may be comprised of a synchronous dynamic random access memory (SDRAM), a dynamic random access memory (DRAM), Dynamic Random Access Memory The non-volatile memory 1416 may be implemented by flash memory and / or any other desired type of memory device. Access to the volatile memory 1414 and the non-volatile memory 1416 of the illustrated example is controlled by a memory controller 1417.

[0113] The processor platform 1400 of the illustrated example also includes an interface circuit 1420. The interface circuit 1420 may be configured according to any type of interface standard (eg, an Ethernet interface, a universal serial bus (USB) interface, An interface, a Near Field Communication (NFC) interface, a Peripheral Component Interconnect (PCI) interface, and / or a Peripheral Component Interconnect Express (PCIe) interface) are implemented by hardware.

[0114] In the example shown, one or more input devices 1422 are connected to the interface circuit 1420. The input devices 1422 allow a user to enter data and / or commands into the processor circuit 1412. The input devices 1422 may be implemented by, for example, a position sensor, a pressure sensor, or the like.

[0115] One or more output devices 1424 are also connected to the interface circuit 1420 of the illustrated example. The output device 1424 may be implemented, for example, by a display device (e.g., a light emitting diode (LED), an organic light emitting diode (OLED), a liquid crystal display (LCD), a cathode ray tube (CRT) display, an in-situ switching (IPS) display, a touch screen, etc.) and / or a tactile output device.

[0116] The interface circuitry 1420 of the illustrated example also includes a communication device (e.g., a transmitter, a receiver, a transceiver, a modem, a residential gateway, a wireless access point, and / or a network interface) to facilitate data exchange with an external machine (e.g., any kind of computing device) over the network 1426. Communications may be through, for example, an Ethernet connection, a digital subscriber line (DSL) connection, a telephone line connection, a coaxial cable system, a satellite system, a field wireless system, a cellular telephone system, an optical connection, etc.

[0117] The processor platform 1400 of the illustrated example also includes one or more mass storage devices 1428 to store software and / or data. Examples of such mass storage devices 1428 include magnetic storage devices, optical storage devices, floppy disk drives, HDDs, CDs, Blu-ray disk drives, redundant array of independent disks (RAID) systems, solid-state storage devices (such as flash memory devices and / or SSDs), and DVD drives.

[0118] Can be Fig.13 The machine-readable instructions 1432 implemented by the machine-readable instructions may be stored in the mass storage device 1428, the volatile memory 1414, the non-volatile memory 1416, and / or on a removable non-transitory computer-readable storage medium (eg, a CD or DVD).

[0119] In some examples, the systems 400, 500, 600, 700, 800 include means for accelerating. For example, the means for accelerating may be provided by Figure 4 The motor 410, Figure 5 The motor 502, Figure 6 The motor 602 in Figure 7 The motor 702 in Figure 8 It may be implemented with the motor 804 in and / or any other motor described herein.

[0120] In some examples, the systems 400, 500, 600, 700, 800 include means for rotating. For example, the means for rotating may be provided by Figure 4 The rotor 430, Figure 5 The rotor 508, Figure 6 The rotor 606, Figure 7 The rotor 706, Figure 8It may be implemented with rotor 806 in and / or any other rotor described herein.

[0121] In some examples, the systems 400, 500, 600, 700, 800 include a device for providing torque. For example, the device for providing torque may be provided by Figure 4 Stator 428, Figure 5 Stator 510, Figure 6 Stator 608, Figure 7 Stator 708, Figure 8 The invention may be implemented with stator 808 and / or any other stator described herein.

[0122] In some examples, the systems 400, 500, 600 include means for framing. For example, the means for framing may be Figure 4 The motor housing 412, Figure 5 The motor housing 522, Figure 6 The motor housing 622 and / or any other motor housing described herein may be implemented.

[0123] In some examples, the systems 700, 800 include means for supporting. For example, the means for supporting may be Figure 7 Thrust plate 710, Figure 8 The thrust disk 812 and / or any other thrust disk described herein may be implemented.

[0124] In some examples, system 800 includes a device for sealing. For example, the device for sealing can be composed of Figure 8 This may be implemented with the piston seal 810 in and / or any other seal described herein.

[0125] In some examples, the systems 400, 500, 600, 700, 800 include a device for driving. For example, the device for driving may be composed of Figure 4 Impeller shaft 432, Figure 5 The rotor shaft 506, Figure 6 The rotor shaft 604, Figure 7 The rotor shaft 704, Figure 8 The rotor shaft 804 and / or any other shaft described herein may be implemented.

[0126] In some examples, the systems 400, 500, 600, 700, 800 include means for sensing. For example, the means for sensing can be implemented by the example sensors that detect positioning information of any of the motors 410, 502, 602, 702, 804 and / or any other sensors described herein.

[0127] Disclosed herein is a conical rotor for use in a pump. The example motor disclosed herein can adjust the torque output of the example pump to mitigate the axial movement of the impeller shaft. The example disclosed herein utilizes a conical rotor and a conical stator to increase the available torque at the impeller shaft. For example, the axial component of the electromagnetic force between the conical rotor and the conical stator can balance the axial load on the impeller shaft. The electromagnetic force generated by the interaction between the conical rotor and the conical stator causes the conical rotor and the rotor shaft to move forward in the pump. This forward movement of the rotor and the rotor shaft can offset the backward movement of the pump during operation. In addition, the example disclosed herein can increase the current of the example motor in response to the axial displacement of the impeller shaft. Additionally or alternatively, the example disclosed herein can adjust the current of the example motor in response to the operating conditions (e.g., rotational speed, ambient temperature, etc.) of the example impeller shaft. In addition, the example system disclosed herein can improve the operating efficiency of the pump (e.g., a centrifugal sCO2 pump) by minimizing or otherwise reducing the friction energy loss associated with the axial impeller shaft movement.

[0128] A conical motor for use with a pump is disclosed herein. Further aspects of the disclosure are provided by the subject matter of the following clauses:

[0129] An apparatus comprises: an electric motor including a conical rotor having a first diameter at a first end and a second diameter at a second end of the conical rotor, the second diameter being different from the first diameter; and a conical stator aligned with the conical rotor.

[0130] An apparatus as described in any preceding clause, further comprising a housing enclosing the motor, the conical rotor and the conical stator.

[0131] Apparatus as claimed in any preceding clause, wherein the first diameter is smaller than the second diameter.

[0132] Apparatus as claimed in any preceding clause wherein the conical stator is concentrically aligned with the conical rotor.

[0133] An apparatus as described in any preceding clause, further comprising a thrust plate positioned forwardly of the motor.

[0134] An apparatus as recited in any preceding clause, further comprising at least one seal positioned forward of said thrust disk, said thrust disk contacting said at least one seal in response to axial movement of said thrust disk.

[0135] An apparatus as described in any preceding clause, further comprising an impeller shaft coupled to the conical rotor.

[0136] Apparatus according to any preceding clause, further comprising a sensor positioned adjacent the motor, the sensor detecting movement of the impeller shaft.

[0137] An electric motor includes a rotor fixedly coupled to a shaft, the rotor including at least one tapered surface, and a stator magnetically coupled to the rotor, the stator positioned around the at least one tapered surface.

[0138] An electric motor as described in any preceding clause, wherein the at least one tapered surface is a first tapered surface, wherein the stator includes a second tapered surface, the second tapered surface being aligned with the first tapered surface.

[0139] An electric motor as described in any preceding clause, wherein the rotor includes a third conical surface, the first conical surface being positioned at a first angle, the third conical surface being positioned at a second angle, the second angle being different from the first angle.

[0140] An electric motor as described in any preceding clause, wherein the at least one tapered surface faces away from the shaft.

[0141] An apparatus includes a rotor having an inner surface and an outer surface, the inner surface facing an axis, and a stator positioned around the outer surface of the rotor, at least a portion of the outer surface being a conical surface.

[0142] An apparatus as described in any preceding clause, wherein the at least a portion of the outer surface is a first portion and the conical surface is a first conical surface, the rotor includes a second portion positioned adjacent to the first portion, the second portion including a second conical surface, the angle of the second conical surface being different from the angle of the first conical surface.

[0143] Apparatus according to any preceding clause, wherein the first tapered surface is substantially parallel to the axis.

[0144] The device according to any of the preceding items further includes a controller circuit, which: determines a first positioning information of the shaft relative to the stator; detects a second positioning information of the shaft relative to the stator, the second positioning information being different from the first positioning information; and adjusts the current of the rotor and the stator based on the second positioning information of the shaft.

[0145] Apparatus according to any preceding clause, further comprising a sensor positioned adjacent the rotor, the sensor for obtaining data relating to the first positioning information and the second positioning information.

[0146] Apparatus as claimed in any preceding clause wherein the controller circuit obtains the second positioning information based on operating speeds of the rotor and the shaft.

[0147] An apparatus as described in any preceding clause, wherein the second positioning information indicates forward movement of the shaft, wherein the controller circuit increases current to the rotor and the stator in response to the forward movement.

[0148] An apparatus as described in any preceding clause, wherein the second positioning information indicates rearward movement of the shaft, wherein the controller circuit reduces current to the rotor and the stator in response to the rearward movement.

[0149] A device includes at least one memory, machine-readable instructions, and programmable circuits, wherein the programmable circuits execute the machine-readable instructions to: determine first positioning information of a rotor shaft relative to a stator, wherein the rotor shaft is fixedly coupled to a rotor and the stator surrounds the rotor; detect second positioning information of the rotor shaft relative to the stator, wherein the second positioning information is different from the first positioning information; and adjust currents of the rotor and the stator based on the second positioning information of the rotor shaft.

[0150] Apparatus as claimed in any preceding clause, further comprising a controller circuit for obtaining sensor output data from a sensor positioned adjacent the rotor, the sensor output data comprising the first positioning information and the second positioning information.

[0151] Apparatus according to any preceding clause, wherein the first positioning information indicates a first axial position of the rotor shaft and the second positioning information indicates a second axial position of the rotor shaft, the second axial position being in front of the stator or behind the stator.

[0152] An apparatus as in any preceding clause, wherein the programmable circuit determines the second positioning information based on a speed of the rotor and the rotor shaft.

[0153] The apparatus of any preceding clause, further comprising a controller circuit for obtaining pressure data from a differential pressure transducer positioned adjacent a thrust disk coupled to the rotor shaft, wherein the programmable circuit detects the second positioning information based on the pressure data.

[0154] The apparatus of any preceding clause, wherein the second positioning information indicates forward movement of the rotor shaft, wherein the programmable circuit increases current to the rotor and the stator in response to the forward movement.

[0155] The apparatus of any preceding clause, wherein the second positioning information indicates rearward movement of the rotor shaft, wherein the programmable circuit reduces current to the rotor and the stator in response to the rearward movement.

[0156] A method includes: detecting a change in position of a rotor shaft relative to a stator, the rotor shaft being connected to a rotor, the stator being magnetically coupled to the rotor; and adjusting a current flow rate associated with the stator and the rotor in response to the changed position of the rotor shaft.

[0157] A method as in any preceding clause, wherein the changed position is detected via a sensor coupled to the rotor shaft.

[0158] A method as in any preceding clause, further comprising detecting a change in position of a thrust plate, the changed position of the thrust plate being correlated to a changed position of the rotor shaft.

[0159] A method as in any preceding clause, wherein the changing position of the thrust plate is detected via a pressure transducer associated with the thrust plate, the pressure transducer acquiring pressure data corresponding to a front side and a rear side of the thrust plate.

[0160] An apparatus comprising: a device for accelerating, the device for accelerating comprising a device for rotating, a first end of the device for rotating having a first diameter, and a second end of the device for rotating having a second diameter, the second diameter being different from the first diameter; and a device for providing torque, the device for providing torque being aligned with the device for rotating.

[0161] The apparatus of any preceding clause, further comprising means for framing, the means for framing enclosing the means for accelerating, the means for rotating, and the means for providing torque.

[0162] Apparatus as claimed in any preceding clause, wherein the first diameter is smaller than the second diameter.

[0163] Apparatus as claimed in any preceding clause wherein the means for providing torque is concentrically aligned with the means for rotating.

[0164] An apparatus as described in any preceding clause, further comprising means for supporting, the means for supporting being positioned forwardly of the means for accelerating.

[0165] The apparatus of any preceding clause, further comprising means for sealing, the means for sealing being positioned forwardly of the means for supporting, the means for supporting contacting the means for sealing in response to axial movement of the means for supporting.

[0166] Apparatus according to any preceding clause, further comprising means for driving, said means for driving coupled to said means for rotating.

[0167] Apparatus as described in any preceding clause, further comprising means for sensing, said means for sensing being positioned adjacent to said means for accelerating, said means for sensing detecting movement of said means for driving.

[0168] The following claims are incorporated by reference into this detailed description. Although certain example systems, methods, devices, and articles are disclosed herein, the scope of coverage of this patent is not limited thereto. On the contrary, this patent covers all systems, methods, devices, and articles that fully fall within the scope of the patent claims.

Claims

1. A device, characterized in that: include: an electric motor comprising a conical rotor having a first diameter at a first end and a second diameter at a second end of the conical rotor, the second diameter being different from the first diameter; and A conical stator is aligned with the conical rotor.

2. The device according to claim 1, characterized in that Further included is a housing that surrounds the motor, the conical rotor, and the conical stator.

3. The device according to claim 1, characterized in that in, The first diameter is smaller than the second diameter.

4. The device according to claim 1, characterized in that in, The conical stator is concentrically aligned with the conical rotor.

5. The device according to claim 1, characterized in that Further included is a thrust plate positioned forward of the motor.

6. The device according to claim 5, characterized in that Further included is at least one seal positioned forward of the thrust plate, the thrust plate contacting the at least one seal in response to axial movement of the thrust plate.

7. The device according to claim 1, characterized in that Further included is an impeller shaft coupled to the conical rotor.

8. The device according to claim 7, characterized in that Further included is a sensor positioned adjacent the motor, the sensor detecting movement of the impeller shaft.

9. An electric motor, characterized in that: include: a rotor fixedly coupled to the shaft, the rotor comprising at least one conical surface; as well as A stator is magnetically coupled to the rotor, the stator being positioned around the at least one conical surface.

10. The electric motor according to claim 9, characterized in that in, The at least one tapered surface is a first tapered surface, wherein the stator includes a second tapered surface aligned with the first tapered surface.

Images