Linear actuation mechanism for variable geometry diffuser assembly

Abstract

A compressor (32) (e.g., of a heating, ventilation, air conditioning, and / or refrigeration system) includes a vaned or unvaned diffuser (102) configured to receive a fluid flow, a drive ring (134), a push rod (116) configured to translate in a linear direction (118) to drive the drive ring (134) to rotate, a drive pin (112) configured to translate in a further linear direction (148) in response to rotation of the drive ring (134), and a variable geometry diffuser (VGD) ring (110) configured to be actuated in response to translation of the drive pin (112) in the further linear direction (148) to change a width of the vaned or unvaned diffuser (102).

Description

Cross-references to related applications

[0001] This application claims priority and benefit to U.S. Provisional Application No. 63 / 604,662, filed November 30, 2023, entitled “Linear Actuation Mechanism for Variable Geometry Diffuser Assembly,” the entire contents of which are incorporated herein by reference for all purposes. Background Technology

[0002] This section aims to introduce the reader to various technical aspects that may be related to the various aspects of this disclosure described below. This discussion is intended to provide background information to facilitate a preferred understanding of the various aspects of this disclosure. Therefore, it should be understood that these statements should be read in this light, rather than as an endorsement of prior art.

[0003] Cooler systems, or vapor compression systems, utilize a working fluid (e.g., a refrigerant) that changes the phase between vapor, liquid, and combinations thereof in response to varying temperatures and pressures exposed within components of the cooler system. Cooler systems can enable heat exchange between the working fluid and a conditioning fluid (e.g., water) and can deliver the conditioning fluid to regulated equipment and / or regulated environments served by the cooler system. In such applications, the conditioning fluid can be directed through downstream devices, such as air processors, to regulate other fluids, such as air within a building.

[0004] The cooler system may include a compressor configured to pressurize and circulate the working fluid through the working fluid loop of the cooler system. In some applications, the compressor shaft may be driven to rotate by an electric motor to drive the compressor impeller to rotate, which (in conjunction with a diffuser) pressurizes the working fluid before delivering it to, for example, a collector.

[0005] In some conventional configurations, a considerable amount of space in the compressor (e.g., axial and / or radial space) is dedicated to various components, such as rotating parts, that selectively alter the width of the diffuser to change or control, for example, the amount of working fluid flowing through the compressor and / or the pressure differential generated by the compressor. In conventional configurations, this significant space (e.g., axial and / or radial space) dedicated to such components substantially increases the compressor's footprint. Additionally or alternatively, some conventional configurations may not be able to accurately and / or precisely alter the diffuser width, negatively impacting the compressor's operational control. Therefore, the need for improved systems and methods is recognized. Summary of the Invention

[0006] The following provides an overview of certain embodiments disclosed herein. It should be understood that these aspects are presented merely to provide the reader with a brief overview of these certain embodiments, and are not intended to limit the scope of this disclosure. In fact, this disclosure may cover many aspects that may not be set forth below.

[0007] In one embodiment, a compressor (e.g., a compressor for a heating, ventilation, air conditioning, and / or refrigeration system) includes a vaned or bladeless diffuser configured to receive a fluid flow, a drive ring, and a push rod configured to translate in a linear direction to drive the drive ring to rotate. The compressor also includes at least one drive pin (e.g., a plurality of drive pins) configured to translate in a further linear direction in response to rotation of the drive ring. The compressor further includes a variable geometry diffuser (VGD) ring configured to be actuated in response to translation of the at least one drive pin in the further linear direction to change the width of the vaned or bladeless diffuser.

[0008] In another embodiment, a method of operating a compressor (e.g., a compressor for a heating, ventilation, air conditioning, and / or refrigeration system) includes: causing a push rod to translate in a linear direction; causing a drive ring to rotate in response to the translation of the push rod in the linear direction; and causing at least one drive pin (e.g., a plurality of drive pins) to translate further in a separate linear direction in response to the rotation of the drive ring. The method further includes: actuating a variable geometry diffuser (VGD) ring to change the width of a bladed or bladeless diffuser in response to the separate translation of the at least one drive pin in the separate linear direction.

[0009] In another embodiment, a variable geometry diffuser (VGD) assembly includes: a VGD ring; a push rod configured to translate in a linear direction to drive a drive ring to rotate; and at least one drive pin (e.g., a plurality of drive pins) configured to translate in another linear direction in response to rotation of the drive ring to actuate the VGD ring, wherein the other linear direction is transverse to the first linear direction. Attached Figure Description

[0010] A better understanding of the various aspects of this disclosure can be achieved by reading the following detailed description and referring to the figures, in which: Figure 1 This is a perspective view of an embodiment of a building in a commercial environment that can utilize heating, ventilation, air conditioning and / or cooling (HVAC&R) systems, according to one aspect of this disclosure; Figure 2 This is a perspective view of an embodiment of a vapor compression system according to one aspect of this disclosure; Figure 3This is a schematic diagram of an embodiment of a vapor compression system according to one aspect of the present disclosure; Figure 4 This is a schematic diagram of an embodiment of a vapor compression system according to one aspect of the present disclosure; Figure 5 This is a schematic cross-sectional view as part of an embodiment of a compressor that can be used in an HVAC&R system according to one aspect of this disclosure; Figure 6 This is a schematic illustration of a portion of an embodiment of a variable geometry diffuser (VGD) assembly that can be used in a compressor according to one aspect of this disclosure, including its linear actuation mechanism; Figure 7 It is an aspect of this disclosure that can be used in a compressor. Figure 7 A cross-sectional schematic diagram of a portion of an embodiment of a VGD component, along... Figure 6 Cut off line 7-7 in the middle; Figure 8 This is a perspective view of a portion of an embodiment of a VGD assembly usable in a compressor according to one aspect of this disclosure (including a drive ring having tilted grooves therein); and Figure 9 This is a process flow diagram illustrating an embodiment of a method for operating a compressor including a VGD component with a linear actuation mechanism according to one aspect of this disclosure. Detailed Implementation

[0011] One or more specific embodiments will be described below. To provide a concise description of these embodiments, not all features of the actual specific implementation are described in the specification. It should be understood that, in the development of any such actual implementation, as in any engineering or design project, numerous implementation-specific decisions must be made to achieve the developer's specific goals, such as consistency with system-related and enterprise-related constraints, which may vary from one implementation to another. Furthermore, it should be understood that such development work may be complex and time-consuming, but is merely a routine task of design, manufacture, and production for those skilled in the art who benefit from this disclosure.

[0012] When describing elements of various embodiments of this disclosure, the articles “a,” “an,” and “described” are intended to mean the presence of one or more of the elements. The terms “comprising,” “including,” and “having” are intended to be inclusive and mean that additional elements may be present in addition to those listed. Furthermore, it should be understood that references to “one embodiment” or “embodiment” in this disclosure are not intended to exclude the existence of additional embodiments incorporated into the described features.

[0013] As used herein, the terms “approximately,” “generally,” and “substantially” are intended to convey that the attribute value being described is within a relatively small range of the attribute value, as understood by one of skill in the art. For example, when an attribute value is described as “approximately” equal to (or, for example, “substantially similar” to) a given value, this is intended to mean that the attribute value is within + / - 5%, + / - 4%, + / - 3%, + / - 2%, + / - 1%, or even closer to the given value. Similarly, when a given feature is described as “substantially parallel” to another feature, “substantially perpendicular” to another feature, etc., this is intended to mean that the given feature has the described property, such as being parallel to another feature, perpendicular to another feature, etc., within + / - 5%, + / - 4%, + / - 3%, + / - 2%, + / - 1%, or even closer to the given feature. Furthermore, it should be understood that mathematical terms such as “flat,” “sloping,” “vertical,” and “parallel” are intended to encompass the characteristics of a surface or element as understood by a person of ordinary skill in the relevant field, and should not be interpreted as rigorously as they would be in the mathematical field. For example, a “flat” surface is intended to encompass a surface that is machined, molded, or otherwise formed substantially flat or smooth (within relevant tolerances) using techniques and tools available to a person of ordinary skill in the field. Similarly, a “sloping” surface is intended to encompass a surface that is machined, molded, or otherwise formed angularly (e.g., inclined) relative to a reference point using techniques and tools available to a person of ordinary skill in the field.

[0014] Embodiments of this disclosure relate to a compressor, such as a compressor used in a heating, ventilation, air conditioning, and refrigeration (HVAC&R) system (e.g., a cooler) having a vapor compression system (e.g., a vapor compression loop). In operation, the compressor pressurizes a working fluid within the vapor compression system and directs the working fluid to a condenser, which cools and condenses the working fluid. The condensed working fluid can be directed to an expansion device, which reduces the pressure of the working fluid, thereby further cooling the working fluid. The cooled working fluid can be directed from the expansion device to an evaporator, in which the working fluid can be positioned in a heat exchange relationship with a conditioning fluid to cool the conditioning fluid. The conditioning fluid can circulate between the evaporator and a structure, such as a building, where it is used to cool airflow delivered to a conditioned space within the structure. In some embodiments, an air handling unit (AHU) of an HVAC&R system can receive the conditioning fluid from a cooler and utilize it to cool airflow delivered to a conditioned space. The conditioning fluid can then be returned to the evaporator for further cooling. According to embodiments of this disclosure, other types of compressors and other types of HVAC&R systems having such compressors may be used.

[0015] The compressor (e.g., a centrifugal compressor) may include an impeller and a diffuser (e.g., a bladed or bladeless diffuser), wherein the impeller is configured to bias (e.g., accelerate) the working fluid toward the diffuser, and the diffuser is configured to decelerate and pressurize the working fluid. In some embodiments, the working fluid may be received by a collector of the compressor downstream of the diffuser. The compressor may also include a variable geometry diffuser (VGD) assembly configured to selectively change or adjust the width (e.g., cross-sectional area) of the diffuser to change or control, for example, the amount of working fluid flowing through the compressor and / or the pressure differential generated by the compressor.

[0016] According to this embodiment, the VGD assembly of the compressor may include an actuation mechanism (e.g., a linear actuation mechanism, an actuation system) configured to apply motion (e.g., linear motion) to drive actuation, for example, of a VGD ring, which is movable between various positions (e.g., a first position retracted from the diffuser, a second position extended into the diffuser, etc.) to control the amount of working fluid flowing through the compressor (e.g., through the diffuser) and / or the pressure differential generated by the compressor. While certain aspects of this disclosure relate to linear actuation mechanisms, it should be understood that, in addition to linear actuation of certain components (such as push rods and / or at least one drive pin (e.g., several drive pins, such as two or more drive pins, three or more drive pins, etc.)), a linear actuation mechanism may also include rotational actuation of certain other components (such as a drive ring).

[0017] Generally, compared to conventional configurations employing other actuation mechanisms (such as external rotating components), the currently disclosed embodiments reduce the space required (e.g., axial and / or radial space) for components dedicated to actuating the VGD ring. In this way, the currently disclosed embodiments can include compressors with a smaller footprint than conventional configurations. Additionally or alternatively, the currently disclosed embodiments include actuation mechanisms with a higher degree of accuracy and / or precision than conventional configurations. That is, the currently disclosed embodiments can more accurately and / or precisely (e.g., sensitively) control the width of the diffuser, thereby enabling greater operational control of the compressor. These and other aspects of this disclosure are described in detail below with reference to the accompanying drawings.

[0018] Now turn to the attached diagram. Figure 1This is a perspective view of an embodiment of a heating, ventilation, air conditioning, and / or cooling (HVAC&R) system 10 in a building 12 for a typical commercial environment. The HVAC&R system may include a vapor compression system 14 for supplying a cooled liquid to cool the building 12 and a boiler 16 for supplying a warm liquid to heat the building 12. The vapor compression system 14 (also referred to herein as a cooler) circulates a working fluid (e.g., a refrigerant) cooled by a cooling fluid (e.g., a liquid, such as water) in the condenser of the vapor compression system 14 and heated by a conditioning fluid (e.g., a liquid, such as water) in the evaporator of the vapor compression system 14. The cooling fluid may be supplied by a cooling tower that cools the cooling fluid via, for example, ambient air. The airflow supplied to the conditioned spaces of the building 12 may be cooled using the conditioning fluid cooled by the working fluid as described above.

[0019] HVAC&R system 10 may also include an air distribution system that circulates air through building 12. The air distribution system may also include an air return duct 18, an air supply duct 20, and / or an air processor 22. In some embodiments, air processor 22 may include a heat exchanger connected via duct 24 to boiler 16 and vapor compression system 14. Depending on the operating mode of HVAC&R system 10, the heat exchanger in air processor 22 may receive heated liquid from boiler 16 or conditioned fluid (e.g., cooled liquid, such as water) from vapor compression system 14. HVAC&R system 10 is shown as having a separate air processor on each floor of building 12, but in other embodiments, HVAC&R system 10 may include air processor 22 and / or other components that may be shared between floors. Figure 2 and Figure 3 An embodiment of a vapor compression system 14 or cooler that can be used in an HVAC&R system 10 is illustrated. The vapor compression system 14 allows working fluid to circulate through a loop (e.g., a working fluid loop) starting with a compressor 32 (such as a centrifugal compressor). The loop may also include a condenser 34, an expansion valve or device 36, and an evaporator 38. The vapor compression system 14 may further include a control panel 40 having an analog-to-digital (A / D) converter 42, a microprocessor 44, non-volatile memory 46, and / or an interface board 48.

[0020] Some examples of fluids that can be used as working fluids in vapor compression system 14 include: hydrofluorocarbon (HFC) based refrigerants, such as R-410A, R-407, R-134a, hydrofluoroolefins (HFO); “natural” refrigerants, such as ammonia (NH3), R-717, carbon dioxide (CO2), R-744; or hydrocarbon-based refrigerants, water vapor, or any other suitable working fluid. Other possible working fluids include R-123, R-514A, R-1130yd, R-1233zd, R-134a, R-1142ze, R-1142yf, R-1311, R-32, and R-410A. In some embodiments, vapor compression system 14 may be configured to efficiently utilize a working fluid having a standard boiling point of about 19 degrees Celsius (66 degrees Fahrenheit) at one atmosphere, also referred to as a low-pressure refrigerant in contrast to medium-pressure working fluids such as R-134a. As used in this article, "standard boiling point" can refer to the boiling point temperature measured at one atmosphere.

[0021] In some embodiments, the vapor compression system 14 may use one or more of a variable speed drive (VSD) 52, a motor 50, a compressor 32, a condenser 34, an expansion valve or device 36, and / or an evaporator 38. The motor 50 may drive the compressor 32 during normal operating mode and may be powered by the VSD 52. The VSD 52 receives alternating current (AC) power during normal operating mode, wherein the AC power includes a specific fixed line voltage and fixed line frequency from an AC power source, and supplies power to the motor 50 with variable voltage and frequency. In other embodiments, the motor 50 may be powered directly by an AC or direct current (DC) power source. The motor 50 may include any type of motor that can be powered by a VSD or directly from an AC or DC power source, such as a switched reluctance motor, an induction motor, an electronically commutated permanent magnet motor, or another suitable motor.

[0022] Compressor 32 compresses the working fluid vapor and delivers the vapor to condenser 34 through a discharge passage. In some embodiments, compressor 32 may be a centrifugal compressor. The working fluid vapor delivered by compressor 32 to condenser 34 transfers heat to the cooling fluid (e.g., water or air) in condenser 34. The working fluid vapor may condense into working fluid liquid in condenser 34 due to heat transfer with the cooling fluid. The liquid working fluid from condenser 34 may flow through expansion device 36 to evaporator 38. Figure 3 In the illustrated embodiment, the condenser 34 is water-cooled and includes a tube bundle 54 connected to a cooling tower 56, which supplies cooling fluid to the condenser 34.

[0023] The liquid working fluid delivered to evaporator 38 can absorb heat from the conditioning fluid, which is then directed to load 62 (e.g., Figure 1 (Building 12). For example, the regulating fluid can be cooled by the working fluid in the evaporator 38, and then... Figure 1 The airflow in building 12 is provided to regulate the space within building 12. The liquid working fluid in evaporator 38 can undergo a phase change from liquid working fluid to working fluid vapor. For example... Figure 3 As shown in the illustrated embodiment, the evaporator 38 may include a tube bundle 58 having a supply line 60S and a return line 60R connected to the cooling load 62. A conditioning fluid (e.g., water, ethylene glycol, calcium chloride brine, sodium chloride brine, or any other suitable fluid) enters the evaporator 38 via the return line 60R and exits the evaporator 38 via the supply line 60S. The evaporator 38 can reduce the temperature of the conditioning fluid in the tube bundle 58 through heat transfer with the working fluid. The tube bundle 58 in the evaporator 38 may comprise multiple tubes and / or multiple tube bundles. In any case, the vapor working fluid exits the evaporator 38 and returns to the compressor 32 via the suction line to complete the cycle.

[0024] Figure 4 This is a schematic diagram of an embodiment of a vapor compression system 14 having an intermediate loop 64 incorporated between the condenser 34 and the expansion unit 36. The intermediate loop 64 may have an inlet line 68 directly fluidly connected to the condenser 34. In other embodiments, the inlet line 68 may be indirectly fluidly coupled to the condenser 34. Figure 4 As illustrated in the depicted embodiment, the inlet line 68 includes a first expansion device 66 positioned upstream of the intermediate container 70. In some embodiments, the intermediate container 70 may be a flash evaporator (e.g., a flash evaporative intercooler). In other embodiments, the intermediate container 70 may be configured as a heat exchanger or a "surface heat saver". Figure 4In the illustrated embodiment, intermediate container 70 serves as an instantaneous evaporation tank, and first expansion device 66 is configured to reduce the pressure of the liquid working fluid received from condenser 34 (e.g., to expand the liquid working fluid). During the expansion process, a portion of the liquid working fluid may vaporize, and thus, intermediate container 70 can be used to separate the vapor working fluid from the liquid working fluid received from first expansion device 66. Additionally, intermediate container 70 can provide further expansion of the liquid working fluid due to the pressure drop experienced by the liquid working fluid upon entering intermediate container 70 (e.g., due to the rapid increase in volume experienced upon entering intermediate container 70). Vapor working fluid in intermediate container 70 can be drawn by compressor 32 through suction line 74 of compressor 32. In other embodiments, vapor working fluid in intermediate container 70 may be drawn into an intermediate stage of compressor 32 (e.g., not a suction stage). Due to the expansion of the working fluid at expansion device 66 and / or in intermediate container 70, the liquid working fluid collected in intermediate container 70 may have a lower enthalpy than the liquid working fluid leaving condenser 34. Then, the liquid working fluid from the intermediate container 70 can flow through the pipeline 72 and through the second expansion device 36 to reach the evaporator 38.

[0025] According to this embodiment, compressor 32 (which can be used in) Figures 1 to 4 (As shown in any system and / or any other suitable HVAC&R system) can be a centrifugal compressor having an impeller and a diffuser that pressurizes the working fluid before delivering it to a collector, such as compressor 32. A variable geometry diffuser (VGD) assembly including a VGD ring can be used to selectively change the width of the diffuser to change or control, for example, the amount of working fluid flowing through compressor 32 and / or the pressure differential generated by compressor 32. According to this embodiment, the VGD assembly of compressor 32 may include an actuation mechanism (e.g., a linear actuation mechanism, actuator, actuation system) configured to apply motion (e.g., linear motion, linear force) to drive actuation of various aspects and / or components (such as the VGD ring) of the VGD assembly, thereby moving the VGD ring to various positions (e.g., a first position extending into the diffuser by a first amount, a second position extending into the diffuser by a second amount, a third position retracted from the diffuser, etc.). The actuation mechanisms (e.g., linear actuation mechanisms, linear actuators, actuation systems) of the currently disclosed embodiments can reduce the spatial size (e.g., axial and / or radial space) of components dedicated to actuating (e.g., moving) aspects of the VGD assembly (such as the VGD ring of the VGD assembly), thereby reducing the footprint of the compressor 32 relative to conventional configurations. Additionally or alternatively, the currently disclosed embodiments can more accurately and / or precisely change the width of the diffuser relative to conventional configurations, thereby improving operational control of the compressor 32. These and other aspects of this disclosure are described in detail below with reference to the accompanying drawings.

[0026] Figure 5 This is a schematic cross-sectional view as part of an embodiment of compressor 32 (e.g., a centrifugal compressor), which can... Figures 1 to 4 This is employed in any system shown and / or any other suitable HVAC&R system (e.g., cooler system, heat pump, etc.). As shown, compressor 32 includes: an impeller 100 configured to accelerate a working fluid; a diffuser 102 (e.g., a bladed or bladeless diffuser) configured to receive the working fluid downstream of the impeller 100 and decelerate (e.g., diffuse and / or pressurize) the working fluid; and a diffuser plate 104 and a nozzle base plate 106, which cooperatively define at least a portion of the diffuser 102, although other arrangements are also possible. That is, the diffuser 102 may include a space or gap between the diffuser plate 104 and the nozzle base plate 106. Although not shown in Figure 5 As shown, but in some embodiments, compressor 32 includes a collector that is fluidly connected to diffuser 102 and configured to receive decelerated and pressurized working fluid from diffuser 102.

[0027] In the illustrated embodiment, the compressor 32 further includes a variable geometry diffuser (VGD) assembly 108 having a VGD ring 110, at least one drive pin 112, a linear actuation mechanism 114 (e.g., a linear actuator, a linear actuator system), and one or more linkages 115. The VGD ring is configured to be actuated or moved to various positions (e.g., from a first position where the diffuser 102 is fully retracted and a second position where the VGD ring 110 extends into at least one of the diffuser 102), and the one or more linkages extend (e.g., operatively connected) between the linear actuation mechanism 114 and the drive pin 112. In some embodiments, the drive pin 112 and / or linkage 115 (or a portion thereof) may be considered as components of the linear actuation mechanism 114. Although Figure 5 Only one example of a drive pin 112 is shown, but it should be understood that in some embodiments multiple drive pins (e.g., two, three, four, five, six, seven or more drive pins) may be used, such as Figure 6 The embodiment shown includes a first drive pin 112a, a second drive pin 112b, and a third drive pin 112c.

[0028] Continue to refer to Figure 5Aspects of the linear actuation mechanism 114, the linkage 115, and / or the drive pin 112 are configured to actuate (e.g., move) the VGD ring 110 between various positions, as described above. As described in more detail below, the linear actuation mechanism 114 employs at least linear actuation to ultimately actuate or move the VGD ring 110 to selectively change the cross-sectional width of a portion of the diffuser 102, thereby controlling, for example, the amount of working fluid flowing through the compressor 32 and / or the pressure differential generated by the compressor 32.

[0029] In some embodiments, the controller 90 has memory circuitry 92 (e.g., memory, memory device) storing instructions and processing circuitry 94 configured to execute the instructions to perform various functions. For example, memory circuitry 92 may include volatile memory, such as random access memory (RAM), and / or non-volatile memory, such as read-only memory (ROM), optical disk drive, hard disk drive, solid-state drive, or any other non-transitory computer-readable medium that includes instructions (e.g., processor input instructions) to perform various functions. Processing circuitry 94 may be configured to execute such instructions. For example, processing circuitry 94 may include one or more application-specific integrated circuits (ASICs), one or more field-programmable gate arrays (FPGAs), one or more general-purpose processors, or any combination thereof. When executing instructions, processing circuitry 94 may be configured to control aspects of VGD component 108 (e.g., operation), such as aspects of linear actuator 114, to control the position of VGD ring 110 relative to diffuser 102. For example, controller 90 may receive one or more inputs 96, such as sensor feedback from sensor 98 (e.g., temperature sensor, pressure sensor, etc.), and control VGD component 108 based on the one or more inputs 96. Other control schemes and / or arrangements are also possible according to this disclosure.

[0030] By employing the linear actuation mechanism 114, the rotational and / or axial space (e.g., radial footprint, axial footprint) dedicated to the VGD assembly 108 and its actuation or movement in the compressor 32 can be reduced compared to conventional configurations, thereby reducing the footprint of the compressor 32. Additionally or alternatively, the currently disclosed VGD assembly 108, including the linear actuation mechanism 114, improves the accuracy of controlling the position of the VGD ring 110. The VGD assembly 108 (including the components of the VGD ring 110, the linear actuation mechanism 114, and the linkage 115) will be described in detail below with reference to the accompanying drawings.

[0031] Figure 6 This is a schematic diagram of an embodiment of a VGD component 108 (including its linear actuation mechanism 114), which in... Figure 5This is employed in compressor 32. In the illustrated embodiment, the linear actuation mechanism 114 includes a push rod 116 configured to be actuated in a first linear direction 118. For example, push rod 116 may be coupled to a rocker arm 119, which in the illustrated embodiment is coupled to the housing wall 120 of compressor 32. In some embodiments, rocker arm 119 is actuated in direction 122 (e.g., pushed or pulled), causing it to rotate about pivot 124 (e.g., in a circumferential or rotational direction 123). A slot 125 in rocker arm 119 allows the rotational movement of rocker arm 119 to apply a translational movement in the first linear direction 118 to push rod 116. That is, when rocker arm 119 rotates about pivot 124, slot 125 in rocker arm 119 is movable relative to end section 127 of push rod 116. In some embodiments, pin 129 is coupled to end section 127 of push rod 116 and extends within a slot 125 in rocker arm 119, such that the position of pin 129 within slot 125 changes as rocker arm 119 rotates about pivot 124. In this way, rotation of rocker arm 119 about pivot 124 can cause actuation or movement of push rod 116 in a first linear direction 118. Actuation of rocker arm 119, push rod 116, or both can be caused by prior information regarding… Figure 5 The controller 90 described is controlled based on one or more inputs 96 to the controller 90 (e.g., sensor feedback from sensor 98).

[0032] As shown, push rod 116 can extend through opening 126 in housing wall 120, wherein one or more bearings 128 (e.g., rod guide bearings) are positioned within opening 126 and between push rod 116 and housing wall 120. Further, housing cap 130 coupled to (or forming part of) housing wall 120 may include one or more O-ring seals 132 that form a seal on push rod 116. Push rod 116 can extend from rocker arm 119 through opening 126 in housing wall 120 and reach drive ring 134 of VGD assembly 108. In the illustrated embodiment, radial groove 136 (also referred to as recess) formed in drive ring 134 is configured to receive a first cam follower 138 coupled to push rod 116 (e.g., via arm 139), note the first cam follower 138 and arm 139 shown in an additional cross-sectional view directly below drive ring 134. When the push rod 116 is actuated or moved in the first linear direction 118, the position of the first cam follower 138 relative to the radial groove 136 can be changed.

[0033] In some embodiments, the VGD assembly 108 may further include additional slots 140 (e.g., transverse slots) disposed in the diffuser plate. Although the additional slots 140 are in Figure 6 The image is shown for the context, but it should be understood that an additional slot 140 may be formed in the image. Figure 6In components not shown (such as diffuser plates). For example, Figure 7 yes Figure 7 A cross-sectional schematic diagram of a portion of the VGD component 108, along Figure 7 Line 8-8 is cut off in the middle, and the VGD component is in Figure 5 It is used in compressor 32. The additional slot 140 is located in... Figure 7 In the diffuser plate 160 shown. Figure 6 and Figure 7 The second cam follower 142 shown may be set in Figure 7 In a further slot 140 of the diffuser plate 160 shown, the second cam follower 142 is connected to the push rod 116 via a further arm 143. When the push rod 116 is in Figure 6 When actuated in the first linear direction 118 as shown, push rod 116 can drive drive ring 134 to rotate (e.g., in the circumferential direction 144). However, such rotation can be achieved via cam follower 138, arm 139, second cam follower 142 and / or additional arm 143 (e.g., via corresponding components such as drive ring 134 and / or Figure 7 The interference of the diffuser plate 160 shown limits the range to within range 146. Furthermore, in response to such rotation, the cam follower 138 and / or arm 139 can move to different relative positions within the radial slot 136, as shown.

[0034] Continue to refer to Figure 6When the drive ring 134 is driven to rotate in the circumferential direction 144, one or more drive pins—such as the first drive pin 112a, the second drive pin 112b, and the third drive pin 112c in the illustrated embodiment—can be actuated or moved in a second linear direction 148 (e.g., transverse to the first linear direction 118), as shown. For example, the drive pins 112a, 112b, 112c can be connected to the drive ring 134 via corresponding cam followers 150a, 150b, 150c and corresponding arms 152a, 152b, 152c connecting the corresponding cam followers 150a, 150b, 150c to the drive pins 112a, 112b, 112c. The cam followers 150a, 150b, 150c can be disposed in corresponding inclined cam grooves 154a, 154b, 154c, which are disposed in the outer diameter 156 of the drive ring 134. An example (i.e., the inclined cam groove 154a) will be described with reference to another drawing of this disclosure. When the drive ring 134 is driven to rotate in the circumferential direction 144, the cam followers 150a, 150b, 150c change position relative to the inclined cam grooves 154a, 154b, 154c, which forces the drive pins 112a, 112b, 112c to move in the second linear direction 148. The movement of the drive pins 112a, 112b, 112c can cause the VGD ring (not in) Figure 6 As shown in the text, but Figure 5 Actuation (as shown in the figure), such as actuation in the second linear direction 148, as previously described.

[0035] To provide further additional background, Figure 8 This is a perspective view of an embodiment of a drive ring 134, which includes an example of an inclined cam groove 154 disposed in the outer diameter 156 of the drive ring 134. As shown, the inclined cam groove 154 extends along an inclined path between a first face 170 and a second face 172 of the drive ring 134. For example, an opening 174 to the inclined cam groove 154 may be formed in the second face 172, wherein the inclined cam groove 154 extends from the opening 174 toward the first face 170 and along the outer diameter 156. When the drive ring 134 is driven to rotate as previously described, a cam follower (not in the...) extends into the inclined cam groove 154... Figure 8 As shown in the text, but Figure 6 and Figure 7 (As shown in the figure) are moved to different positions within the tilting cam groove 154, causing the cam follower (and the drive pin associated with the cam follower) to move in the second linear direction 148.

[0036] Figure 9 This is an explanation of the operation. Figure 5A process flow diagram of an embodiment of method 200 for a compressor, such as operating a linear actuation mechanism for a VGD assembly. In the illustrated embodiment, method 200 includes translating (box 202) a push rod in a linear direction. For example, as previously described, the push rod can be translated in a linear direction via actuation of a rocker arm about a pivot, wherein the rocker arm is coupled to the push rod (e.g., via a pin extending through a slot in the rocker arm) and the compressor housing wall.

[0037] Method 200 also includes driving (frame 204) rotation of the drive ring in response to translation of the push rod in a linear direction. For example, the push rod may be coupled to the drive ring via a cam follower disposed in a radial groove of the drive ring. The push rod may also be coupled to the diffuser plate of the compressor via an additional cam follower disposed in another groove (e.g., a transverse groove) formed in the diffuser plate.

[0038] Method 200 also includes translating (box 206) the drive pin in a separate linear direction in response to rotation of the drive ring. For example, the drive pin may be coupled to the drive ring via a drive pin cam follower disposed in an inclined cam groove formed in the outer diameter of the drive ring. When the drive ring is driven to rotate, the drive pin cam follower and the drive pin coupled thereto may be actuated or moved in a separate linear direction (e.g., between the faces of the drive ring).

[0039] Method 200 further includes actuating (box 208) the VGD ring in response to translation of the drive pin in an additional linear direction to change the width of the diffuser (e.g., the space or gap between the diffuser plate and the nozzle base plate). For example, the drive pin may be coupled to or otherwise abut the VGD ring. When the drive pin moves in the aforementioned additional linear direction, the drive ring may actuate the VGD ring (e.g., in the additional linear direction), for example, actuated into the diffuser. Generally, the VGD ring can be actuated between various positions via the aforementioned features, including a first position retracted from the diffuser and one or more second positions extended into the diffuser. In doing so, the amount of working fluid moving through the diffuser and / or the differential pressure generated by the compressor can be selectively controlled.

[0040] While only certain features and embodiments are shown and described, many modifications and alterations will occur to those skilled in the art without substantially departing from the novel teachings and advantages of the subject matter set forth in the claims, such as variations in the size, dimensions, structure, shape and proportions of various elements, parameter values ​​(such as temperature and pressure), installation arrangements, use of materials, color, orientation, etc. The order or sequence of any process or method steps may be changed or reordered according to alternative embodiments. Therefore, it should be understood that the appended claims are intended to cover all such modifications and variations that fall within the true spirit of this disclosure.

[0041] Furthermore, for the sake of providing a concise description of exemplary embodiments, not all features of the actual specific implementation may be described, such as those not relevant to the currently anticipated best mode or those not relevant to enabling. It should be understood that, in the development of such actual implementations, as in any engineering or design project, many implementation-specific decisions may be made. Such development efforts may be complex and time-consuming, but remain routine tasks of design, fabrication, and manufacture for those skilled in the art to which this disclosure pertains.

[0042] The techniques presented and claimed herein are referenced to and applied to practical objects and concrete examples that explicitly improve upon the art and are therefore not abstract, intangible, or purely theoretical. Furthermore, if any claim appended to this specification contains one or more elements designated as “a component for [performing] [the function]” or “a step for [performing] [the function]”, such elements are intended to be interpreted according to 35 USC 112(f). However, for any claim containing elements designated in any other manner, such elements are not intended to be interpreted according to 35 USC 112(f).

Claims

1. A compressor comprising: Bladed or bladeless diffusers configured to receive fluid flow; Drive ring; A push rod configured to translate in a linear direction to drive the drive ring to rotate; A drive pin configured to translate in another linear direction in response to rotation of the drive ring; as well as A variable geometry diffuser (VGD) ring, configured to be actuated in response to translation of the drive pin in the additional linear direction, to change the width of the bladed or bladeless diffuser.

2. The compressor according to claim 1, comprising: Radial grooves or recesses are formed in the drive ring; as well as A cam follower is disposed in the radial groove or recess and connected to the push rod.

3. The compressor according to claim 2, comprising: A diffuser plate or housing having additional slots or grooves formed therein; as well as An additional cam follower is disposed in the additional slot or groove and is connected to the push rod.

4. The compressor of claim 3, wherein the additional slot or groove includes a transverse slot or groove.

5. The compressor according to claim 1, comprising: An inclined cam groove is provided in the drive ring; as well as A cam follower is disposed in the inclined cam groove and connected to the drive pin.

6. The compressor according to claim 5, wherein the inclined cam groove is disposed in the outer diameter of the drive ring.

7. The compressor according to claim 1, comprising: A rocker arm configured to translate the push rod in the linear direction; as well as The housing wall, wherein the push rod extends between the drive ring and the rocker arm through an opening in the housing wall.

8. The compressor of claim 7, further comprising a rod guide bearing disposed between the push rod and the housing wall, within the opening in the housing wall, or adjacent to the opening in the housing wall.

9. The compressor of claim 7, comprising a housing gland coupled to the housing wall and including at least one O-ring seal on the push rod.

10. The compressor of claim 1, comprising a plurality of drive pins configured to translate in the additional linear direction in response to rotation of the drive ring, wherein the plurality of drive pins includes the drive pin.

11. A method of operating a compressor, the method comprising: To move the push rod in a straight line; In response to the translation of the push rod in the linear direction, the drive ring is rotated; In response to the rotation of the drive ring, the drive pin is translated in another linear direction. as well as In response to the additional translation of the drive pin in the additional linear direction, the variable geometry diffuser (VGD) ring is actuated to change the width of the bladed or bladeless diffuser.

12. The method of claim 11, further comprising, in response to translation of the push rod in the linear direction, moving the cam follower within or relative to a radial groove or recess formed in the drive ring.

13. The method of claim 12, further comprising, in response to translation of the push rod in the linear direction, moving an additional cam follower in or relative to an additional slot or recess formed in or in the diffuser plate or housing.

14. The method of claim 11, further comprising, in response to rotation of the drive ring, moving a cam follower coupled to the drive pin within or relative to an inclined cam groove disposed in the drive ring, wherein the inclined cam groove is disposed in the outer diameter of the drive ring.

15. The method of claim 11, further comprising translating the push rod in the linear direction relative to an opening in the housing wall through which the push rod extends via a rocker arm.

16. The method of claim 11, further comprising, in response to rotation of the drive ring, translating a plurality of drive pins in a further linear direction, wherein the plurality of drive pins includes the drive pin.

17. A variable geometry diffuser (VGD) assembly comprising: VGD ring; A push rod configured to translate in a straight line to drive the drive ring to rotate; as well as A drive pin is configured to translate in a separate linear direction in response to rotation of the drive ring to actuate the VGD ring, wherein the separate linear direction is transverse to the linear direction.

18. The VGD assembly of claim 17, comprising a rocker arm configured to translate the push rod in the linear direction.

19. The VGD assembly of claim 17, comprising a rod guide bearing configured to be disposed in an opening in the compressor housing wall between the push rod and the compressor housing wall.

20. The VGD assembly of claim 17, comprising a plurality of drive pins configured to translate in a further linear direction in response to rotation of the drive ring to actuate the VGD ring, wherein the plurality of drive pins includes the drive pin.

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