Linear actuation mechanism of a variable geometry diffuser assembly

Abstract

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

Description

LINEAR ACTUATION MECHANISM OF A VARIABLE GEOMETRY DIFFUSER ASSEMBLYCROSS-REFERENCE TO RELATED APPLICATIONS

[0001] This application claims priority to and the benefit of U.S. Provisional Application No. 63 / 604,662, entitled “LINEAR ACTUATION MECHANISM OF A VARIABLE GEOMETRY DIFFUSER ASSEMBLY,” filed November 30, 2023, which is hereby incorporated by reference in its entirety for all purposes.BACKGROUND

[0002] This section is intended to introduce the reader to various aspects of art that may be related to various aspects of the present disclosure, which are described below. This discussion is believed to be helpful in providing the reader with background information to facilitate a better understanding of the various aspects of the present disclosure. Accordingly, it should be understood that these statements are to be read in this light, and not as admissions of prior art.

[0003] Chiller systems, or vapor compression systems, utilize a working fluid (e.g., a refrigerant) that changes phases between vapor, liquid, and combinations thereof in response to exposure to different temperatures and pressures within components of the chiller system. The chiller system may place the working fluid in a heat exchange relationship with a conditioning fluid (e.g., water) and may deliver the conditioning fluid to conditioning equipment and / or a conditioned environment serviced by the chiller system. In such applications, the conditioning fluid may be directed through downstream equipment, such as air handlers, to condition other fluids, such as air in a building.

[0004] The chiller system may include a compressor configured to pressurize the working fluid and circulate the working fluid through a working fluid circuit of the chiller system. In some applications, a shaft of the compressor may be driven into rotation by a motor in order to drive rotation of an impeller of the compressor that (in conjunction witha diffuser) pressurizes the working fluid prior to delivery of the working fluid into, for example, a collector.

[0005] In some traditional configurations, considerable space (e.g., axial space and / or radial space) of the compressor is devoted to various componentry, such as rotary componentry, that selectively modifies a width of the diffuser to vary or control, for example, an amount of the working fluid flowing through the compressor and / or a pressure differential created by the compressor. The considerable space (e g., axial space and / or radial space) of the compressor devoted to such componentry substantially increases a footprint of the compressor in traditional configurations. Additionally or alternatively, certain traditional configurations may not accurately and / or precisely modify the width of the diffuser, which negatively impacts operational control of the compressor. Accordingly, it is now recognized that improved systems and methods are desired.SUMMARY

[0006] A summary of certain embodiments disclosed herein is set forth below. It should be understood that these aspects are presented merely to provide the reader with a brief summary of these certain embodiments and that these aspects are not intended to limit the scope of this disclosure. Indeed, this disclosure may encompass a variety of aspects that may not be set forth below.

[0007] In an embodiment, a compressor (e.g., of a heating, ventilating, air conditioning, and / or refrigeration system) includes a vane or vaneless diffuser configured to receive a flow of a fluid, a drive ring, and a push rod configured to be translated in a linear direction to drive the drive ring into rotation. The compressor also includes at least one drive pin (e.g., several drive pins) configured to be translated in an additional linear direction in response to the rotation of the drive ring. The compressor also includes a variable geometry diffuser (VGD) ring configured to be actuated to change a width of the vane or vaneless diffuser in response to translation of the at least one drive pin in the additional linear direction.

[0008] In another embodiment, a method of operating a compressor (e.g., of a heating, ventilating, air conditioning, and / or refrigeration system) includes causing translation of a push rod in a linear direction, causing rotation of a drive ring in response to the translation of the push rod in the linear direction, and causing additional translation of at least one drive pin (e.g., several drive pins) in an additional linear direction in response to the rotation of the drive ring. The method also includes actuating a variable geometry diffuser (VGD) ring to change a width of a vane or vaneless diffuser in response to the additional translation of the at least one drive pin in the additional linear direction.

[0009] In still another embodiment, a variable geometry diffuser (VGD) assembly includes a VGD ring, a push rod configured to be translated in a linear direction to drive a drive ring into rotation, and at least one drive pin (e.g., several drive pins) configured to be translated in an additional linear direction in response to the rotation of the drive ring to cause actuation of the VGD ring, where the additional linear direction is transverse to the linear direction.BRIEF DESCRIPTION OF THE DRAWINGS

[0010] Various aspects of this disclosure may be better understood upon reading the following detailed description and upon reference to the drawings in which:

[0011] FIG. l is a perspective view of an embodiment of a building that may utilize a heating, ventilating, air conditioning, and / or refrigeration (HVAC&R) system in a commercial setting, in accordance with an aspect of the present disclosure;

[0012] FIG. 2 is a perspective view of an embodiment of a vapor compression system, in accordance with an aspect of the present disclosure;

[0013] FIG. 3 is a schematic view of an embodiment of a vapor compression system, in accordance with an aspect of the present disclosure;

[0014] FIG. 4 is a schematic view of an embodiment of a vapor compression system, in accordance with an aspect of the present disclosure;

[0015] FIG. 5 is a schematic cross-sectional view of a portion of an embodiment of a compressor that may be utilized in an HVAC&R system, in accordance with an aspect of the present disclosure;

[0016] FIG. 6 is a schematic illustration of a portion of an embodiment of a variable geometry diffuser (VGD) assembly, including a linear actuation mechanism thereof, that may be utilized in a compressor, in accordance with an aspect of the present disclosure;

[0017] FIG. 7 is a cross-sectional schematic illustration of a portion of an embodiment of the VGD assembly of FIG. 7, taken along line 7-7 in FIG. 6, that may be utilized in a compressor, in accordance with an aspect of the present disclosure;

[0018] FIG. 8 is a perspective view of a portion of an embodiment of a VGD assembly, including a drive ring having a ramped slot therein, that may be utilized in a compressor, in accordance with an aspect of the present disclosure; and

[0019] FIG. 9 is a process flow diagram illustrating an embodiment of a method of operating a compressor including a VGD assembly having a linear actuation mechanism, in accordance with an aspect of the present disclosure.DETAILED DESCRIPTION

[0020] One or more specific embodiments will be described below. In an effort to provide a concise description of these embodiments, not all features of an actual implementation are described in the specification. It should be appreciated 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 developers’ specific goals, such as compliance with system-related and business-related constraints, which may vary from one implementation to another. Moreover, it should be appreciatedthat such a development effort might be complex and time consuming, but would nevertheless be a routine undertaking of design, fabrication, and manufacture for those of ordinary skill having the benefit of this disclosure.

[0021] When introducing elements of various embodiments of the present disclosure, the articles “a,” “an,” and “the” are intended to mean that there are one or more of the elements. The terms “comprising,” “including,” and “having” are intended to be inclusive and mean that there may be additional elements other than the listed elements. Additionally, it should be understood that references to “one embodiment” or “an embodiment” of the present disclosure are not intended to be interpreted as excluding the existence of additional embodiments that also incorporate the recited features.

[0022] As used herein, the terms “approximately,” “generally,” and “substantially,” and so forth, are intended to convey that the property value being described may be within a relatively small range of the property value, as those of ordinary skill would understand. For example, when a property value is described as being “approximately” equal to (or, for example, “substantially similar” to) a given value, this is intended to mean that the property value may be within + / - 5%, within + / - 4%, within + / - 3%, within + / - 2%, within + / - 1%, or even closer, of the given value. Similarly, when a given feature is described as being “substantially parallel” to another feature, “generally perpendicular” to another feature, and so forth, this is intended to mean that the given feature is within + / - 5%, within + / - 4%, within + / - 3%, within + / - 2%, within + / - 1%, or even closer, to having the described nature, such as being parallel to another feature, being perpendicular to another feature, and so forth. Further, it should be understood that mathematical terms, such as “planar,” “slope,” “perpendicular,” “parallel,” and so forth are intended to encompass features of surfaces or elements as understood to one of ordinary skill in the relevant art, and should not be rigidly interpreted as might be understood in the mathematical arts. For example, a “planar” surface is intended to encompass a surface that is machined, molded, or otherwise formed to be substantially flat or smooth (within related tolerances) using techniques and tools available to one of ordinary skill in the art. Similarly, a surface having a “slope” is intendedto encompass a surface that is machined, molded, or otherwise formed to be oriented at an angle (e.g., incline) with respect to a point of reference using techniques and tools available to one of ordinary skill in the art.

[0023] Embodiments of the present disclosure relate to a compressor, such as a compressor employed in a heating, ventilation, air conditioning, and refrigeration (HVAC&R) system (e.g., a chiller) having a vapor compression system (e.g., vapor compression circuit). In operation, the compressor may pressurize a working fluid within the vapor compression system and direct the working fluid to a condenser, which may cool and condense the working fluid. The condensed working fluid may be directed to an expansion device, which may reduce a pressure of the working fluid, further cooling the working fluid. From the expansion device, the cooled working fluid may be directed to an evaporator, where the working fluid may be placed in a heat exchange relationship with a conditioning fluid to cool the conditioning fluid. The conditioning fluid may be circulated between the evaporator and a structure, such as a building, where the conditioning fluid is used to cool an air flow delivered to a conditioned space of the structure. In some embodiments, an air handling unit (AHU) of the HVAC&R system may receive the conditioning fluid from the chiller and utilize the conditioning fluid to cool the air flow delivered to the conditioned space. The conditioning fluid may then be returned to the evaporator to be cooled again. Other types of compressors and other types of HVAC&R systems having such compressors may be employed in accordance with embodiments of the present disclosure.

[0024] The compressor (e.g., centrifugal compressor) may include an impeller and a diffuser (e.g., a vane or vaneless diffuser), where the impeller is configured to bias (e.g., accelerate) the working fluid toward the diffuser, and the diffuser is configured to slow 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 modify or adjust a width (e.g., a cross-sectional area) of the diffuser to vary or control, for example, an amountof the working fluid flowing through the compressor and / or a pressure differential created by the compressor.

[0025] In accordance with present embodiments, the VGD assembly of the compressor may include an actuation mechanism (e.g., a linear actuation mechanism, actuation system) configured to impart motion (e.g., linear motion) to drive, for example, actuation of a VGD ring movable between various positions (e.g., a first position retracted from the diffuser, a second position extending into the diffuser, etc.) to control an amount of the working fluid flowing through the compressor (e.g., through the diffuser) and / or a pressure differential created by the compressor. While certain aspects of the present disclosure refer to a linear actuation mechanism, it should be understood that the linear actuation mechanism may include, in addition to linear actuation of certain componentry, such as a push rod 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.), rotary actuation of certain other componentry, such as a drive ring.

[0026] In general, presently disclosed embodiments reduce an amount of space (e.g., axial space and / or radial space) devoted to componentry for actuating the VGD ring relative to traditional configurations employing other actuation mechanisms, such as extraneous rotary componentry. In this way, presently disclosed embodiments may include a compressor with a smaller footprint than traditional configurations. Additionally or alternatively, presently disclosed embodiments include actuation mechanisms having a higher degree of accuracy and / or precision than traditional configurations. That is, presently disclosed embodiments may more accurately and / or precisely (e.g., acutely) control the width of the diffuser, thereby enabling greater operational control of the compressor. These and other aspects of the present disclosure are described in detail below with reference to the drawings.

[0027] Turning now to the drawings, FIG. 1 is a perspective view of an embodiment of a heating, ventilating, air conditioning, and / or refrigeration (HVAC&R) system 10 in a building 12 for a typical commercial setting. The HVAC&R system may include a vapor compression system 14 to supply chilled liquid to cool the building 12 and a boiler 16 tosupply warm liquid to heat the building 12. The vapor compression system 14, also referred to herein as a chiller, may circulate a working fluid (e.g., refrigerant) that is cooled by a cooling fluid (e.g., liquid such as water) in a condenser of the vapor compression system 14, and that is heated by a conditioning fluid (e.g., liquid, such as water) in an evaporator of the vapor compression system 14. The cooling fluid may be provided by a cooling tower which cools the cooling fluid via, for example, ambient air. The conditioning fluid, cooled by the working fluid as noted above, may be utilized to cool an air flow provided to conditioned spaces of the building 12.

[0028] The HVAC&R system 10 may also include an air distribution system which circulates air through the building 12. The air distribution system can also include an air return duct 18, an air supply duct 20, and / or an air handler 22. In some embodiments, the air handler 22 may include a heat exchanger that is connected to the boiler 16 and the vapor compression system 14 by conduits 24. The heat exchanger in the air handler 22 may receive either heated liquid from the boiler 16 or the conditioning fluid (e.g., chilled liquid such as water) from the vapor compression system 14, depending on the mode of operation of the HVAC&R system 10. The HVAC&R system 10 is shown with a separate air handler on each floor of building 12, but in other embodiments, the HVAC&R system 10 may include air handlers 22 and / or other components that may be shared between or among floors

[0029] FIGS. 2 and 3 illustrate embodiments of the vapor compression system 14, or chiller, which can be used in the HVAC&R system 10. The vapor compression system 14 may circulate a working fluid through a circuit (e.g., working fluid circuit) starting with a compressor 32, such as a centrifugal compressor. The circuit may also include a condenser 34, an expansion valve(s) or device(s) 36, and an evaporator 38. The vapor compression system 14 may further include a control panel 40 that has an analog to digital (A / D) converter 42, a microprocessor 44, a non-volatile memory 46, and / or an interface board 48.

[0030] Some examples of fluids that may be used as working fluids in the vapor compression system 14 are hydrofluorocarbon (HFC) based refrigerants, for example, R-410A, R-407, R-134a, hydrofluoro olefin (HFO), “natural” refrigerants like 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-l 130yd, R-1233zd, R-134a, R-1142ze, R-1142yf, R-1311, R-32, and R-410A. In some embodiments, the vapor compression system 14 may be configured to efficiently utilize working fluids having a normal boiling point of about 19 degrees Celsius (66 degrees Fahrenheit) at one atmosphere of pressure, also referred to as low pressure refrigerants, versus a medium pressure working fluid, such as R-l 34a. As used herein, “normal boiling point” may refer to a boiling point temperature measured at one atmosphere of pressure.

[0031] In some embodiments, the vapor compression system 14 may use one or more of a variable speed drive (VSDs) 52, a motor 50, the compressor 32, the condenser 34, the expansion valve or device 36, and / or the evaporator 38. The motor 50 may drive the compressor 32 during a normal operating mode and may be powered by a variable speed drive (VSD) 52. The VSD 52 receives alternating current (AC) power during the normal operating mode, where the AC power includes a particular fixed line voltage and fixed line frequency from an AC power source, and provides power having a variable voltage and frequency to the motor 50. In other embodiments, the motor 50 may be powered directly from an AC or direct current (DC) power source. The motor 50 may include any type of electric 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.

[0032] The compressor 32 compresses a working fluid vapor and delivers the vapor to the condenser 34 through a discharge passage. In some embodiments, the compressor 32 may be a centrifugal compressor. The working fluid vapor delivered by the compressor 32 to the condenser 34 may transfer heat to a cooling fluid (e g., water or air) in the condenser 34. The working fluid vapor may condense to a working fluid liquid in the condenser 34 as a result of thermal heat transfer with the cooling fluid. The liquid working fluid fromthe condenser 34 may flow through the expansion device 36 to the evaporator 38. In the illustrated embodiment of FIG. 3, the condenser 34 is water cooled and includes a tube bundle 54 connected to a cooling tower 56, which supplies the cooling fluid to the condenser 34.

[0033] The liquid working fluid delivered to the evaporator 38 may absorb heat from a conditioning fluid that is subsequently routed to a load 62 (e.g., the building 12 of FIG. 1). For example, the conditioning fluid may be cooled by the working fluid in the evaporator 38, and then may be utilized in the building 12 of FIG. 1 to condition an air flow provided to condition a space in the building 12. The liquid working fluid in the evaporator 38 may undergo a phase change from the liquid working fluid to a working fluid vapor. As shown in the illustrated embodiment of FIG. 3, 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. The conditioning fluid of the evaporator 38 (e.g., water, ethylene glycol, calcium chloride brine, sodium chloride brine, or any other suitable fluid) enters the evaporator 38 via return line 60R and exits the evaporator 38 via supply line 60S. The evaporator 38 may reduce the temperature of the conditioning fluid in the tube bundle 58 via thermal heat transfer with the working fluid. The tube bundle 58 in the evaporator 38 can include a plurality of tubes and / or a plurality of tube bundles. In any case, the vapor working fluid exits the evaporator 38 and returns to the compressor 32 by a suction line to complete the cycle.

[0034] FIG. 4 is a schematic of an embodiment of the vapor compression system 14 with an intermediate circuit 64 incorporated between the condenser 34 and the expansion device 36. The intermediate circuit 64 may have an inlet line 68 that is directly fluidly connected to the condenser 34. In other embodiments, the inlet line 68 may be indirectly fluidly coupled to the condenser 34. As shown in the illustrated embodiment of FIG. 4, the inlet line 68 includes a first expansion device 66 positioned upstream of an intermediate vessel 70. In some embodiments, the intermediate vessel 70 may be a flash tank (e.g., a flash intercooler). In other embodiments, the intermediate vessel 70 may be configured asa heat exchanger or a "surface economizer." In the illustrated embodiment of FIG. 4, the intermediate vessel 70 is used as a flash tank, and the first expansion device 66 is configured to lower the pressure of (e.g., expand) the liquid working fluid received from the condenser 34. During the expansion process, a portion of the liquid working fluid may vaporize, and thus, the intermediate vessel 70 may be used to separate the vapor working fluid from the liquid working fluid received from the first expansion device 66. Additionally, the intermediate vessel 70 may provide for further expansion of the liquid working fluid due to a pressure drop experienced by the liquid working fluid when entering the intermediate vessel 70 (e g., due to a rapid increase in volume experienced when entering the intermediate vessel 70). The vapor working fluid in the intermediate vessel 70 may be drawn by the compressor 32 through a suction line 74 of the compressor 32. In other embodiments, the vapor working fluid in the intermediate vessel 70 may be drawn to an intermediate stage of the compressor 32 (e.g., not the suction stage). The liquid working fluid that collects in the intermediate vessel 70 may be at a lower enthalpy than the liquid working fluid exiting the condenser 34 due to expansion of the working fluid at the expansion device 66 and / or in the intermediate vessel 70. The liquid working fluid from intermediate vessel 70 may then flow through line 72 and through a second expansion device 36 to the evaporator 38.

[0035] In accordance with present embodiments, the compressor 32, which may be employed in any of the systems illustrated in FIGS. 1-4 and / or any other suitable HVAC&R system, may be a centrifugal compressor having an impeller and a diffuser that pressurizes the working fluid prior to delivery of the working fluid into, for example, a collector of the compressor 32. A variable geometry diffuser (VGD) assembly including a VGD ring may be employed to selectively modify a width of the diffuser to vary or control, for example, an amount of the working fluid flowing through the compressor 32 and / or a pressure differential created by the compressor 32. In accordance with present embodiments, the VGD assembly of the compressor 32 may include an actuation mechanism (e.g., linear actuation mechanism, actuator, actuation system) configured to impart motion (e.g., linear motion, a linear force) to drive actuation of various aspects and / or components of the VGDassembly, such as the VGD ring to move the VGD ring to various positions (e g., a first position extending into the diffuser a first amount, a second position extending into the diffuser a second amount, a third position retracted from the diffuser, etc.). The actuation mechanism (e.g., linear actuation mechanism, linear actuator, actuation system) of presently disclosed embodiments may reduce an amount of space (e.g., axial space and / or radial space) devoted to componentry for actuating (e.g., moving) aspects of the VGD assembly, such as the VGD ring of the VGD assembly, thereby reducing a footprint of the compressor 32 relative to traditional configurations. Additionally or alternatively, presently disclosed embodiments may more accurately and / or precisely modify the width of the diffuser relative to traditional configurations, thereby improving operational control of the compressor 32. These and other aspects of the present disclosure are described in detail below with reference to the drawings.

[0036] FIG. 5 is a schematic cross-sectional view of a portion of an embodiment of the compressor 32 (e.g., centrifugal compressor) employable in any of the systems illustrated in FIGS. 1-4 and / or any other suitable HVAC&R system (e.g., chiller system, heat pump, etc.). As shown, the compressor 32 includes an impeller 100 configured to accelerate the working fluid, a diffuser 102 (e.g., a vane or vaneless diffuser) configured to receive the working fluid downstream of the impeller 100 and slow (e.g., diffuse and / or pressurize) the working fluid, and a diffuser plate 104 and a nozzle base plate 106 that cooperatively define at least a portion of the diffuser 102, although other arrangements are also possible. That is, the diffuser 102 may be include a space or gap between the diffuser plate 104 and the nozzle base plate 106. Although not shown in FIG. 5, in some embodiments, the compressor 32 includes a collector fluidly coupled with the diffuser 102 and configured to receive the slowed, pressurized working fluid from the diffuser 102.

[0037] The compressor 32 in the illustrated embodiment also includes a variable geometry diffuser (VGD) assembly 108 having a VGD ring 110 configured to be actuated or moved to various positions (e.g., a first position retracted entirely from the diffuser 102 and at least one second position in which the VGD ring 110 extends into the diffuser 102),at least one drive pin 112, a linear actuation mechanism 114 (e.g., linear actuator, linear actuator system), and one or more linkages 115 extending between (e.g., operatively connecting) the linear actuation mechanism 114 and the drive pin 112. In some embodiments, the drive pin 112 and / or the linkage(s) 115 (or a portion thereof) may be considered components of the linear actuation mechanism 114. While only one instance of the drive pin 112 is illustrated in FIG. 5, it should be understood that multiple drive pins (e.g., two, three, four, five, six, seven, or more drive pins) may be employed in certain embodiments, such as the embodiment illustrated in FIG. 6, which includes a first drive pin 112a, a second drive pin 112b, and a third drive pin 112c.

[0038] Continuing with FIG. 5, aspects of the linear actuation mechanism 114, the linkage(s) 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 greater detail below, the linear actuation mechanism 114 employs at least linear actuation to ultimately actuate or move the VGD ring 110 to selectively modify a cross-sectional width of a portion of the diffuser 102, thereby controlling, for example, an amount of the working fluid flowing through the compressor 32 and / or a pressure differential created by the compressor 32.

[0039] In some embodiments, a controller 90 having memory circuitry 92 (e.g., memory, memory device) storing instructions thereon and processing circuitry 94 configured to execute the instructions to perform various functions. For example, the 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 drives, hard disc drives, solid-state drives, or any other non-transitory computer-readable medium that includes instructions (e.g., processor input instructions) to perform various functions. The processing circuitry 94 may be configured to execute such instructions. For example, the 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. In executing the instructions, theprocessing circuitry 94 may be configured to control an aspect (e.g., operation) of the VGD assembly 108, such as an aspect of the linear actuation mechanism 114, to control a position of the VGD ring 110 relative to the diffuser 102. For example, the controller 90 may receive one or more inputs 96, such as sensor feedback from a sensor 98 (e.g., temperature sensor, pressure sensor, etc.), and control the VGD assembly 108 based on the one or more inputs 96. Other control schemes and / or arrangements are also possible in accordance with the present disclosure.

[0040] By employing the linear actuation mechanism 1 14, rotary and / or axial space (e.g., radial footprint, axial footprint) in the compressor 32 devoted to the VGD assembly 108 and actuation or movement thereof may be reduced compared to traditional configurations, thereby reducing a footprint of the compressor 32. Additionally or alternatively, the presently disclosed VGD assembly 108, including the linear actuation mechanism 114, may improve an accuracy of controlling a position of the VGD ring 110. The VGD assembly 108, including the VGD ring 110, the linear actuation mechanism 114, and componentry of the linkage(s) 115 will be described in detail below with reference to later drawings.

[0041] FIG. 6 is a schematic view of an embodiment of a portion of the VGD assembly 108, including the linear actuation mechanism 114 thereof, employed in the compressor 32 of FIG. 5. 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, the push rod 116 may be coupled to a rocker arm 119, which is coupled to a casing wall 120 of the compressor 32 in the illustrated embodiment. In some embodiments, the rocker arm 119 is actuated (e.g., pushed or pulled) in a direction 122, causing it to rotate (e.g., in a circumferential or rotational direction 123) about a pivot 124. A slot 125 in the rocker arm 119 may enable the rotational movement of the rocker arm 119 to impart the translational movement to the push rod 116 in the first linear direction 118. That is, the slot 125 in the rocker arm 119 may move relative to an end section 127 of the push rod 116 as the rocker arm 119 rotates about the pivot 124. In some embodiments, a pin 129 is coupled to the endsection 127 of the push rod 116 and extends within the slot 125 in the rocker arm 119, such that a position of the pin 129 within the slot 125 changes as the rocker arm 119 is rotated about the pivot 124. In this way, the rotation of the rocker arm 119 about the pivot 124 may cause actuation or movement of the push rod 116 in the first linear direction 118. Actuation of the rocker arm 119, the push rod 116, or both may be controlled by the controller 90, previously described with respect to FIG. 5, based on one or more inputs 96 to the controller 90 (e.g., sensor feedback from the sensor 98).

[0042] As shown, the push rod 116 may extend through an opening 126 in the casing wall 120, where one or more bearings 128 (e.g., rod guide bearings) are positioned within the opening 126 and between the push rod 116 and the casing wall 120. Further, a housing gland 130 coupled to (or forming a part of) the casing wall 120 may include one or more O-ring seals 132 forming a seal on the push rod 116. The push rod 116 may extend from the rocker arm 119, through the opening 126 in the casing wall 120, and to a drive ring 134 of the VGD assembly 108. In the illustrated embodiment, a radial slot 136 (also referred to as a groove) formed in the drive ring 134 is configured to receive a first cam follower 138 coupled to the push rod 116 (e.g., via an arm 139), noting that the first cam follower 138 and the arm 139 are illustrated in an additional cross-sectional view just under the drive ring 134. As the push rod 116 is actuated or moved in the first linear direction 118, a position of the first cam follower 138 relative to the radial slot 136 may change.

[0043] In some embodiments, the VGD assembly 108 may also include an additional slot 140 (e.g., transverse slot) disposed in a diffuser plate. While the additional slot 140 is illustrated for context in FIG. 6, it should be understood that the additional slot 140 may be formed in componentry, such as a diffuser plate, not shown in FIG. 6. For example, FIG. 7 is a cross-sectional schematic illustration of a portion of the VGD assembly 108 of FIG. 7, taken along line 8-8 in FIG. 7, employed in the compressor 32 of FIG. 5. The additional slot 140 is disposed in a diffuser plate 160 illustrated in FIG. 7. A second cam follower 142 illustrated in FIGS. 6 and 7 may be disposed in the additional slot 140 of the diffuser plate 160 illustrated in FIG. 7, where the second cam follower 142 is coupled tothe push rod 116 via an additional arm 143. As the push rod 116 is actuated in the first linear direction 118 illustrated in FIG. 6, the push rod 116 may drive the drive ring 134 into rotation (e.g., in a circumferential direction 144). However, such rotation may be limited in scope to a range 146 by way of the cam follower 138, the arm 139, the second cam follower 142, and / or the additional arm 143 (e.g., via interference with respective componentry, such as the drive ring 134 and / or the diffuser plate 160 illustrated in FIG. 7). Further, in response to such rotation, the cam follower 138 and / or the arm 139 may move to different relative positions within the radial slot 136, as shown.

[0044] Continuing with FIG. 6, as the drive ring 134 is driven into rotation in the circumferential direction 144, one or more drive pins - such as a first drive pin 112a, a second drive pin 112b, and a third drive pin 112c in the illustrated embodiment - may 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 may be coupled with the drive ring 134 via respective cam followers 150a, 150b, 150c and respective arms 152a, 152b, 152c coupling the respective cam followers 150a, 150b, 150c with the drive pins 112a, 112b, 112c. The cam followers 150a, 150b, 150c may be disposed in respective ramped cam slots 154a, 154b, 154c disposed in an outer diameter 156 of the drive ring 134. One instance (i.e., the ramped cam slot 154a) will be described with respect to another drawing of the present disclosure. As the drive ring 134 is driven into rotation in the circumferential direction 144, positions of the cam followers 150a, 150b, 150c with respect to the ramped cam slots 154a, 154b, 154c change, which forces the drive pins 112a, 112b, 112c to be moved in the second linear direction 148. The movement of the drive pins 112a, 112b, 112c may cause actuation of a VGD ring (not shown in FIG. 6, but illustrated in FIG. 5), such as actuation in the second linear direction 148, as previously described.

[0045] For still further added context, FIG. 8 is a perspective view of an embodiment of the drive ring 134 including one instance of the ramped cam slot 154 disposed in the outer diameter 156 of the drive ring 134. As shown, the ramped cam slot 154 follows a ramped path between a first face 170 and a second face 172 of the drive ring 134. Forexample, an opening 174 to the ramped cam slot 154 may be formed in the second face 172, where the ramped cam slot 154 extends from the opening 174, toward the first face 170, and along the outer diameter 156. When the drive ring 134 is driven into rotation as previously described, the cam follower (not shown in FIG. 8, but illustrated in FIGS. 6 and 7) extending into the ramped cam slot 154 is moved to a different position within the ramped cam slot 154 causing the cam follower (and the drive pin associated with the cam follower) to move in the second linear direction 148.

[0046] FIG. 9 is a process flow diagram illustrating an embodiment of a method 200 of operating the compressor of FIG. 5, such as operating a linear actuation mechanism for a VGD assembly. In the illustrated embodiment, the method 200 includes translating (block 202) a push rod in a linear direction. For example, as previously described, the push rod may be translated in the linear direction via actuation of a rocker arm about a pivot, where the rocker arm is coupled to the push rod (e.g., via a pin of the push rod extending through a slot in the rocker arm) and to a casing wall of the compressor.

[0047] The method 200 also includes driving (block 204) rotation of a drive ring in response to translation of the push rod in the linear direction. For example, the push rod may be coupled to the drive ring via a cam follower disposed in a radial slot of the drive ring. The push rod may also be coupled to a diffuser plate of the compressor via an additional cam follower disposed in an additional slot (e.g., transverse slot) formed in the diffuser plate.

[0048] The method 200 also includes translating (block 206) a drive pin in an additional 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 a ramped cam slot formed in an outer diameter of the drive ring. As the drive ring is driven into rotation, the drive pin cam follower and the drive pin coupled thereto may be actuated or moved in the additional linear direction (e.g., between faces of the drive ring).

[0049] The method 200 also includes actuating (block 208) a VGD ring to change a width of a diffuser (e.g., a space or gap between a diffuser plate and a nozzle base plate) in response to translation of the drive pin in the additional linear direction. For example, the drive pin may be coupled to, or otherwise abut, the VGD ring. As the drive pin is moved in the additional linear direction described above, the drive ring may actuate the VGD ring (e.g., in the additional linear direction), for example, into the diffuser. In general, the VGD ring may be actuated between various positions via the above-described features, including a first position that is retracted from the diffuser and one or more second positions extending into the diffuser. In doing so, an amount of working fluid moving through the diffuser and / or a pressure differential generated by the compressor may be selectively controlled.

[0050] While only certain features and embodiments have been illustrated and described, many modifications and changes may occur to those skilled in the art, such as variations in sizes, dimensions, structures, shapes and proportions of the various elements, values of parameters, such as temperatures and pressures, mounting arrangements, use of materials, colors, orientations, and so forth, without materially departing from the novel teachings and advantages of the subject matter recited in the claims. The order or sequence of any process or method steps may be varied or re-sequenced according to alternative embodiments. It is, therefore, to be understood that the appended claims are intended to cover all such modifications and changes as fall within the true spirit of the disclosure.

[0051] Furthermore, in an effort to provide a concise description of the exemplary embodiments, all features of an actual implementation may not have been described, such as those unrelated to the presently contemplated best mode, or those unrelated to enablement. It should be appreciated that in the development of any such actual implementation, as in any engineering or design project, numerous implementation specific decisions may be made. Such a development effort might be complex and time consuming, but would nevertheless be a routine undertaking of design, fabrication, and manufacturefor those of ordinary skill having the benefit of this disclosure, without undue experimentation.

[0052] The techniques presented and claimed herein are referenced and applied to material objects and concrete examples of a practical nature that demonstrably improve the present technical field and, as such, are not abstract, intangible or purely theoretical. Further, if any claims appended to the end of this specification contain one or more elements designated as “means for [perform]ing [a function], ..” or “step for [perform]ing [a function]...”, it is intended that such elements are to be interpreted under 35 U.S.C. 112(f). However, for any claims containing elements designated in any other manner, it is intended that such elements are not to be interpreted under 35 U.S.C. 112(f).

Claims

CLAIMS:

1. A compressor, comprising: a vane or vaneless diffuser configured to receive a flow of a fluid; a drive ring; a push rod configured to be translated in a linear direction to drive the drive ring into rotation; a drive pin configured to be translated in an additional linear direction in response to the rotation of the drive ring; and a variable geometry diffuser (VGD) ring configured to be actuated to change a width of the vane or vaneless diffuser in response to translation of the drive pin in the additional linear direction.

2. The compressor of claim 1, comprising: a radial slot or groove formed in the drive ring; and a cam follower disposed in the radial slot or groove and coupled with the push rod.

3. The compressor of claim 2, comprising: a diffuser plate or housing having an additional slot or groove formed therein; and an additional cam follower disposed in the additional slot or groove and coupled with the push rod.

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

5. The compressor of claim 1, comprising: a ramped cam slot disposed in the drive ring; and a cam follower disposed in the ramped cam slot and coupled to the drive pin.

6. The compressor of claim 5, wherein the ramped cam slot is disposed in an outer diameter of the drive ring.

7. The compressor of claim 1, comprising: a rocker arm configured to translate the push rod in the linear direction; and a casing wall, wherein the push rod extends between the drive ring and the rocker arm through an opening in the casing wall.

8. The compressor of claim 7, comprising rod guide bearings disposed between the push rod and the casing wall within or adjacent to the opening in the casing wall.

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

10. The compressor of claim 1, comprising a plurality of drive pins configured to be translated in the additional linear direction in response to the 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: causing a translation of a push rod in a linear direction; causing a rotation of a drive ring in response to the translation of the push rod in the linear direction; causing an additional translation of a drive pin in an additional linear direction in response to the rotation of the drive ring; and actuating a variable geometry diffuser (VGD) ring to change a width of a vane or vaneless diffuser in response to the additional translation of the drive pin in the additional linear direction.

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

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

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

15. The method of claim 11, comprising causing, via a rocker arm, the translation of the push rod in the linear direction relative to a casing wall opening through which the push rod extends.

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

17. A variable geometry diffuser (VGD) assembly, comprising: a VGD ring; a push rod configured to be translated in a linear direction to drive a drive ring into rotation; and a drive pin configured to be translated in an additional linear direction in response to the rotation of the drive ring to cause actuation of the VGD ring, wherein the additional 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 rod guide bearings configured to be disposed in an opening in a compressor casing wall between the push rod and the compressor casing wall.

20. The VGD assembly of claim 17, comprising a plurality of drive pins configured to be translated in the additional linear direction in response to the rotation of the drive ring to cause the actuation of the VGD ring, wherein the plurality of drive pins includes the drive pin.

Images