Damping system for compressor

Abstract

A damping system (100) for a heating, ventilation, air conditioning, and refrigeration (HVAC&R) system includes a port (102) integrated with a rotor housing (50) of a compressor (12) of the HVAC&R system, where a rotor of the compressor (12) is disposed within the rotor housing (50), the port (102) is oriented in a radial direction relative to an axis of rotation of the rotor within the rotor housing (50), and the port (102) is orthogonally offset from the axis of rotation. The damping system (100) also includes a valve assembly (104) positioned at least partially within the port (102) and configured to direct working fluid from an economizer (18) of the HVAC&R system into the compressor (12). The valve assembly (104) includes an intake portion (110) positioned proximate a first end of the valve assembly (104) and configured to receive the working fluid from the economizer (18), an insert portion (114) positioned proximate a second end of the valve assembly (104) and configured to direct the working fluid into the compressor (12), and a body portion (112) fluidly coupling the intake portion (110) to the insert portion (114).

Description

New International Application N / JOHCO-179-PCT November 13, 2025 NUGS / nusdDAMPING SYSTEM FOR COMPRESSORCROSS-REFERENCE TO RELATED APPLICATIONS

[0001] This application claims priority to and the benefit of U.S. Provisional Application No.63 / 720,017, entitled “DAMPING SYSTEM FOR COMPRESSOR,” filed November 13, 2024, which is herein 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] Heating, ventilation, air conditioning, and refrigeration (HVAC&R) systems, or vapor compression systems, are utilized in residential, commercial, and industrial environments to control environmental properties, such as temperature and humidity, of a conditioned space. In general, HVAC&R systems circulate a working fluid (e.g., refrigerant), which changes phases between vapor, liquid, and combinations thereof in response to exposure to different temperatures and pressures associated with operation of the HVAC&R system. For example, an HVAC&R system may utilize one or more compressors to circulate the working fluid to a heat exchanger (e.g., evaporator, condenser) which may transfer heat between the working fluid and another fluid (e.g., cooling fluid) flowing through or across the heat exchanger. One type of compressor that may be utilized in an HVAC&R system is a screw compressor, which generally includes one or more cylindrical rotors mounted inside a hollow casing. Twin screw compressor rotors typically have helically extending lobes (or flutes) and grooves (or flanks) on their outer radial surfaces that form threads extending about respective circumferences of the rotors. During operation, the threads of the rotors mesh together, with the lobes of one rotor meshing with the corresponding grooves of the other rotor to form a series of spaced compression cavities (e.g., spaced gaps) between the rotors. The spaced compression cavities cooperatively form a compression chamber that is in fluid communication with a compressor inlet or port and continuously reduces a volume of the fluid as the rotors rotate to compress the fluid. In this manner, the compressor may directNew International Application N / JOHCO-179-PCT November 13, 2025 NUGS / nusd fluid from the compressor inlet to a compressor outlet. In certain cases, compressed gas intermittently discharged from the spaced compression cavities may react against the housing of the compressor and produce gas flow-induced vibration and noise.

[0004] In some cases, HVAC&R systems may employ an economizer to improve performance. For example, condensed working fluid may be directed from a heat exchanger (e.g., a condenser) to the economizer, and at least a portion of the condensed working fluid directed into the economizer may evaporate within the economizer. The resulting vapor may be extracted from the economizer and redirected to the compressor, while the remaining liquid working fluid within the economizer is directed to a second heat exchanger (e.g., evaporator). The compressor may therefore include a port configured to receive the vapor working fluid from the economizer and direct the vapor working fluid into the compressor. It is now recognized that improved systems and methods for introducing working fluid from an economizer into a compressor are desired.SUMMARY

[0005] 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. Embodiments according to the invention are disclosed in particular in the appended claims.

[0006] In an embodiment, a damping system for a heating, ventilation, air conditioning, and refrigeration (HVAC&R) system includes a port integrated with a rotor housing of a compressor of the HVAC&R system, where a rotor of the compressor is disposed within the rotor housing, the port is oriented in a radial direction relative to an axis of rotation of the rotor within the rotor housing, and the port is orthogonally offset from the axis of rotation. The damping system also includes a valve assembly positioned at least partially within the port and configured to direct working fluid from an economizer of the HVAC&R system into the compressor. The valve assembly includes an intake portion positioned proximate a first end of the valve assembly and configured to receive the working fluid from the economizer, an insert portion positioned proximate a second end of the valve assembly and configured to direct the working fluid into the compressor, and a body portion fluidly coupling the intake portion to the insert portion.New International Application N / JOHCO-179-PCT November 13, 2025 NUGS / nusd

[0007] In another embodiment, a compressor for a heating, ventilation, air conditioning, and refrigeration (HVAC&R) system includes a first rotor having one or more lobes and a second rotor having one or more grooves, where the one or more grooves of the second rotor are configured to receive the one or more lobes of the first rotor to form one or more spaced compression cavities. The one or more spaced compression cavities are configured to receive a working fluid, compress the working fluid, and direct the working fluid in a compression direction along a longitudinal axis of the compressor. The compressor also includes a rotor housing configured to enclose the first rotor and the second rotor, and a damping system configured to reduce pulsations, vibrations, or both within the compressor. The damping system includes a port formed in the rotor housing, where the port is oriented in a direction extending crosswise relative to the compression direction, and the port is orthogonally offset from an axis of rotation of the second rotor. The damping system further includes a valve assembly mounted within the port and configured to direct the working fluid from an economizer of the HVAC&R system into the rotor housing in a semi-tangential direction.

[0008] In a further embodiment, a heating, ventilation, air conditioning, and refrigeration (HVAC&R) system includes a compressor having a housing, a first rotor disposed within the housing, and a second rotor disposed within the housing. The first rotor and the second rotor extend in a direction along a rotor plane, and the first rotor and the second rotor are configured to pressurize a working fluid and direct the working fluid along a working fluid circuit. The HVAC&R system also includes a condenser configured to receive the working fluid from the compressor and place the working fluid in a heat exchange relationship with a cooling fluid, and the HVAC&R system includes an economizer configured to receive the working fluid from the condenser and separate the working fluid into a vapor working fluid and a liquid working fluid. The HVAC&R system further includes a damping system configured to mitigate noise, vibrations, pulsations, or any combination thereof associated with operation of the compressor. The damping system includes a port formed in the housing of the compressor, where the port is offset from the rotor plane in a direction along an orthogonal axis of the compressor. The damping system further includes a valve assembly positioned within the port and configured to direct the vapor working fluid from the economizer into a compression chamber defined by the housing of the compressor.New International Application N / JOHCO-179-PCT November 13, 2025 NUGS / nusd BRIEF DESCRIPTION OF THE DRAWINGS

[0009] Various aspects of this disclosure may be better understood upon reading the following detailed description and upon reference to the drawings in which:

[0010] FIG. 1 is a schematic view of an embodiment of a vapor compression system, in accordance with an aspect of the present disclosure;

[0011] FIG. 2 is a cross-sectional view of an embodiment of a compressor having a damping system, in accordance with an aspect of the present disclosure;

[0012] FIG. 3 is a cross-sectional view of a portion of an embodiment of a compressor, illustrating a damping system having an economizer check valve assembly, in accordance with an aspect of the present disclosure;

[0013] FIG. 4 is a perspective view of an embodiment of an insert portion of a valve assembly, in accordance with an aspect of the present disclosure;

[0014] FIG. 5 is a perspective, cross-sectional view of an embodiment of the insert portion of FIG. 4 in an assembled configuration with a valve assembly, in accordance with an aspect of the present disclosure;

[0015] FIG. 6 is a perspective view of an embodiment of an insert portion of a valve assembly, in accordance with an aspect of the present disclosure;

[0016] FIG. 7 is a perspective, cross-sectional view of an embodiment of the insert portion of FIG. 6 in an assembled configuration with a valve assembly, in accordance with an aspect of the present disclosure;

[0017] FIG. 8 is a perspective view of an embodiment of an insert portion of a valve assembly, in accordance with an aspect of the present disclosure;

[0018] FIG. 9 is a perspective, cross-sectional view of an embodiment of the insert portion of FIG. 8 in an assembled configuration with a valve assembly, in accordance with an aspect of the present disclosure;New International Application N / JOHCO-179-PCT November 13, 2025 NUGS / nusd

[0019] FIG. 10 is a perspective, cross-sectional view of an embodiment of a valve assembly of a damping system in an open position, in accordance with an aspect of the present disclosure;

[0020] FIG. 11 is a perspective, cross-sectional view of an embodiment of valve assembly of a damping system in a closed position, in accordance with an aspect of the present disclosure; and

[0021] FIG. 12 is an exploded perspective view of an embodiment of a valve assembly of a damping system, in accordance with an aspect of the present disclosure.DETAILED DESCRIPTION

[0022] One or more specific embodiments of the present disclosure will be described below. These described embodiments are examples of the presently disclosed techniques. Additionally, in an effort to provide a concise description of these embodiments, all features of an actual implementation may not be 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 may 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 appreciated that 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.

[0023] 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.

[0024] As used herein, the terms “approximately,” “generally,” “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 convey that the property value may be within + / - 5%,New International Application N / JOHCO-179-PCT November 13, 2025 NUGS / nusd 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 convey 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. Mathematical terms, such as “parallel” and “perpendicular,” should not be rigidly interpreted in a strict mathematical sense, but should instead be interpreted as one of ordinary skill in the art would interpret such terms. For example, one of ordinary skill in the art would understand that two lines that are substantially parallel to each other are parallel to a substantial degree, but may have minor deviation from exactly parallel.

[0025] As briefly discussed above, a heating, ventilation, air conditioning, and refrigeration (HVAC&R) system may be configured to operate to satisfy heating and / or cooling demands within a building, home, or other conditioned space. For example, the HVAC&R system may include a vapor compression system (e.g., chiller system, heat pump system) that transfers thermal energy between a working fluid (e.g., refrigerant, ammonia) and a fluid to be conditioned (e.g., air, water, brine). The vapor compression system may include one or more vapor compression circuits (e.g., heat pumps) that each include a condenser and an evaporator that are fluidly coupled to one another via one or more conduits (e.g., vapor compression circuit, working fluid circuit, refrigeration circuit). Further, each vapor compression circuit may include a compressor configured to pressurize and circulate the working fluid through the conduit and, thus, enable the transfer of thermal energy between the working fluid and the fluid to be conditioned via the condenser and / or the evaporator. For example, the compressor may direct the working fluid to a condenser, which may cool and condense the working fluid. The condensed working fluid may be directed toward an expansion device, which may reduce a pressure of 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 compressor may then receive the working fluid from the evaporator for pressurization to restart the vapor compression cycle.

[0026] In some embodiments, the vapor compression system may include an economizer configured to receive the working fluid from the condenser. The economizer may be configured to reduce a pressure of the working fluid and separate the working fluid into liquid working fluidNew International Application N / JOHCO-179-PCT November 13, 2025 NUGS / nusd and vapor working fluid. For example, as the working fluid is introduced into the economizer, the increase in volume may enable at least a portion of the working fluid to vaporize (e.g., flash) such that the working fluid is separated into a liquid working fluid and a vapor working fluid. The economizer may direct the liquid working fluid to the evaporator (e.g., via an expansion device) to enable the evaporator to place the liquid working fluid in a heat exchange relationship with the conditioning fluid. The vapor working fluid may be directed from the economizer to the compressor. In certain embodiments, for example when the compressor is a screw compressor, the vapor working fluid may be introduced at an intermediate pressure.

[0027] Screw compressors may include one or more cylindrical rotors that are disposed within a hollow rotor housing or casing of the compressor. The rotors generally have helically extending lobes and grooves disposed on respective outer radial faces of the rotors that form threads extending about respective circumferences of the rotors. During compressor operation, the rotors mesh at an interface between the rotors to form a series of spaced compression cavities (e.g., spaced gaps) extending between the lobes and the grooves of the rotors. The spaced compression cavities cooperatively form a compression chamber that extends along a length of the rotor housing. The compression chamber is in fluid communication with a suction inlet (e.g., axial and / or radial port near the compressor inlet) at one end of the rotor housing and a discharge port (e.g., an axial and / or radial port near the compressor outlet) at an opposite end of the rotor housing. When the rotors rotate, the spaced compression cavities between the lobes and grooves may continuously decrease in volume from the suction inlet toward the discharge port. In other words, the compression chamber may continually decrease in volume during a compression cycle. In this manner, the compressor may direct fluid from the suction inlet and through the rotor housing. In certain cases, the compressed fluid (e.g., gas) intermittently discharged from the spaced compression cavities acts on the rotor housing of the compressor and is delivered downstream, thereby producing gas flow-induced vibration and noise, which may be undesirable.

[0028] Further, in some vapor compression systems employing an economizer, the compressor may include an additional inlet port (e.g., economizer inlet port) configured to receive vapor working fluid from the economizer. Various intermediate pressures in the compression process may be accessed via the economizer inlet port. For example, the economizer may operate at a pressure (e.g., intermediate pressure) that is greater than the suction inlet pressure but less than the discharge port pressure of the compressor. In this way, the economizer may drive a working fluidNew International Application N / JOHCO-179-PCT November 13, 2025 NUGS / nusd flow (e.g., superfeed a working fluid flow) into the compressor at an intermediate pressure (e.g., pressure between the suction inlet pressure and the discharge port pressure). For example, the economizer inlet port may enable vapor working fluid to be introduced into the compressor (e.g., at an intermediate pressure that is higher than the suction pressure and lower than the discharge pressure), thereby enabling an additional vapor working fluid flow (e.g., from the economizer) to be compressed by the compressor and delivered to downstream components of the vapor compression system (e.g., condenser).

[0029] In some cases, rotation of the rotors may generate vibrations (e.g., rotor vibrations) and / or pulsations (e.g., working fluid pressure pulsations) during the compression process. For example, during a compression cycle, the compression chamber may decrease in volume from an upper limit capacity to a lower limit capacity before restarting the compression cycle. Thus, the pressure within the compression chamber may vary as a function of the varying compression chamber volume, thereby generating vibrations and pulsations as the compressor transitions between compression cycles. Additionally, introduction of vapor working fluid from an economizer inlet port may increase an amount of gas flow-induced vibrations and / or pulsations due to the varying economizer port pressure (e.g., as a function of the varying compression chamber volume during a compression cycle). In turn, the vibrations and pulsations may propagate from the rotor housing to other components of the compressor. In certain instances, transmission of excess rotor vibrations to certain compressor components may cause these components to incur mechanical wear and / or performance degradation over time. Further, excess rotor vibrations may decrease an operating efficiency of the compressor. Additionally, such rotor vibrations and pulsations may propagate from the compressor to other components of the HVAC&R system disposed upstream (e.g., toward the economizer via an economizer line extending between the economizer inlet port of the compressor and the economizer) and / or downstream of the compressor relative to a flow direction of working fluid through the compressor, thereby causing such components to incur mechanical wear and / or performance degradation over time as well and / or reducing an operating efficiency of the HVAC&R system.

[0030] For example, some systems may orient and / or position economizer inlet ports such that working fluid from the economizer is discharged axially toward the rotors relative to a rotational axis of a respective rotor. However, the economizer inlet port may open and close (e.g., due to rotation of the rotors), such that working fluid from the economizer is introduced intermittently.New International Application N / JOHCO-179-PCT November 13, 2025 NUGS / nusd That is, introduction of the working fluid in an axial direction (e.g., via an economizer inlet port) may generate a shuttering effect that increases an amount of noise and vibration within the compressor. Additionally, some economizer inlet porting may not accommodate certain geometrical characteristics of the rotors of the compressor, thereby further adding to the vibration and noise (e.g., by introducing working fluid from an economizer in a manner that disrupts the working fluid flow already within the compressor). Further still, some economizer inlet ports may be fixed in size, thereby limiting an operating envelope of the compressor. For example, economizer inlet porting may be installed to enable a particular flow rate of working fluid from the compressor to the economizer. However, load fluctuations on the compressor may call for the compressor to operate at different capacities (e.g., decreased capacity, increased capacity). Unfortunately, some economizer inlet porting may limit an amount of adaptability and / or flexibility of the economizer porting to meet the adjusted load demands of the system. Thus, it is now recognized that improved systems and methods for introducing vapor working fluid from an economizer to a compressor (e.g., a screw compressor, to a compression cavity of a screw compressor) while minimizing an amount of vibrations and / or pulsations within a vapor compression system are desired.

[0031] Accordingly, embodiments of the present disclosure are directed toward an economizer inlet port system (e.g., economizer flow compressor inlet system, economizer inlet port damping system) for a compressor. The economizer inlet port system may include a damping system that includes a valve assembly (e.g., economizer port valve, check valve, pulsation damping valve, damping assembly) that is configured to introduce working fluid from an economizer into a compressor (e.g., a screw compressor) in a manner that reduces vibrations and / or noise in the compressor and / or in a vapor compression system employing the compressor. Additionally, the valve assembly may be configured to limit and / or block an amount of working fluid from traveling in an upstream direction from the compressor toward the economizer (e.g., relative to a direction of working fluid from the economizer to the compressor via an economizer discharge conduit), thereby further limiting an amount of pulsations, vibration, and / or noise generated during operation of the vapor compression system. Further still, the valve assembly may be configured to limit and / or block an amount of lubricant (e.g., oil) from reaching the economizer when the compressor is inoperative (e.g., during a shutdown mode, standby mode, idle mode). The damping system may be integrated into a compressor housing or manifold, thereby increasing the structural integrity of the valve assembly (e.g., compared to traditional systems that employ check valves asNew International Application N / JOHCO-179-PCT November 13, 2025 NUGS / nusd discrete components) and facilitating improved packaging and / or assembly of the vapor compression system.

[0032] In certain embodiments, the damping system and the valve assembly may be oriented in a radial direction relative to a rotational axis of a rotor of the compressor such that working fluid introduced from the economizer flows at least partially in the radial direction toward the rotor (e.g., female rotor) of the compressor. In certain embodiments, the valve assembly may also be oriented in a direction that at least partially extends along a longitudinal axis of the compressor (e.g., toward the discharge section of the compressor), thereby enabling the valve assembly to direct vapor working fluid into a compression cavity of the compressor in a direction that is at least partially along the flow direction of working fluid within the compression cavity (e.g., direction from the suction inlet of the compressor to the discharge outlet of the compressor, a direction within a threshold degree of similarity, less than a ninety-degree difference). Further, the damping system may be positioned within the compressor housing such that the valve assembly is radially offset from a center or central axis of a rotor that defines the compression cavities configured to receive the working fluid from the economizer. For example, the valve assembly may be offset (e.g., vertically offset, horizontally offset) from a rotor plane of the rotors (e.g., a plane on which each rotor axis extends) such that the valve assembly injects working fluid into the compression cavity at least partially in a tangential direction relative to the direction of rotation of the rotor. In this way, the vapor working fluid directed from the economizer to the compressor may be introduced in a manner that reduces an amount of turbulence within the compression cavities, thereby decreasing an amount of noise, vibration, and / or pulsations during operation of the vapor compression system.

[0033] Additionally, the valve assembly discussed herein may be assembled using a split or segmented design. For example, valve assembly may include a valve portion (e.g., a valve body [e.g., ball and seat]) and an insert portion separated by a spring. The insert portion may define a passage configured to receive working fluid from the valve portion and discharge the working fluid into the compressor. In certain embodiments, the insert portion may be coupled to (e.g., mounted to, inserted into) the compressor casing (e.g., via a port formed through the casing) via an interference fit, and other components of the valve assembly may be assembled with (e.g., coupled to) the insert portion. A downstream end of the insert portion may be contoured based on the geometry of the rotors of the compressor and / or an inner surface of the compressor casing,New International Application N / JOHCO-179-PCT November 13, 2025 NUGS / nusd thereby encouraging a smooth flow of working fluid into the compressor. Notably, because the valve assembly is assembled using a split design, features of the valve assembly may be interchangeable and / or easily replaced, thereby increasing an operating envelope of the compressor. For example, different insert portions that define passages with different sizes may be readily installed, replaced, and / or interchanged, thereby enabling working fluid from the economizer to be introduced into the compressor at different flow rates and / or volumes (e.g., introduced at different intermediate pressures). Additionally, or alternatively, the insert portions may include outlets or slots configured to align with a particular location along a compression cavity, thereby enabling a particular intermediate pressure to be accessed within the compression cavity. For example, the different insert portions may have different geometries that define the respective passages, thereby enabling the respective passages to align with a particular location along a compression cavity. Thus, different insert portions having outlets or slots positioned and / or formed (e.g., machined) in different locations may be readily interchanged and / or installed into the port formed through the casing, thereby enabling different intermediate pressures within the compression cavity to be accessed (e.g., based on a particular location of the outlet or slot of the insert portion relative to the compression cavity). That is, an operator may select the size of the insert portion and / or an insert portion having an outlet or slot at a particular location or with a particular geometry based on current or expected load demands of the system, thereby providing greater operating flexibility compared to some systems having a fixed economizer inlet port.

[0034] The spring may be employed within the valve assembly to bias various components of the valve assembly away from one another. In this way, the valve assembly may absorb pulsations traveling in an upstream direction (e.g., from the compressor back to the economizer), thereby further limiting pulsation propagation through the vapor compression system. Further, the split design may mitigate wear and / or degradation that would otherwise be induced in the compressor and / or vapor compression system, and may increase clearances and lower tolerances, thereby increasing installation and maintenance flexibility. Further still, by employing the valve assembly discussed herein, fewer separate discrete components may be incorporated with the vapor compression system, thereby reducing costs associated with manufacture, transportation, assembly, and maintenance of HVAC&R systems.

[0035] Turning now to the drawings, FIG. 1 is a schematic view of an embodiment of a vapor compression system 10 that may be utilized in a heating, ventilation, air conditioning, andNew International Application N / JOHCO-179-PCT November 13, 2025 NUGS / nusd refrigeration (HVAC&R) system. In certain embodiments, the vapor compression system 10 (e.g., chiller) may supply a chilled liquid, which may be used to cool a building, for example. The vapor compression system 10 may circulate a working fluid (e.g., a heat transfer fluid, a refrigerant) through a circuit starting with a compressor 12 (e.g., a screw compressor). The circuit may also include a condenser 14, a first expansion valve or device 16, an economizer 18, a second expansion valve or device 20, a liquid chiller or an evaporator 22, and an economizer outlet conduit 24 fluidly coupling the economizer 18 to the compressor 12 (e.g., via an economizer inlet port 19). In some embodiments, the vapor compression system 10 may include a motor 26 to drive the compressor 12. The motor 26 may be powered by a variable speed drive (VSD) 28 that receives alternating (AC) power having 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 26. In other embodiments, the motor 26 may be powered directly from an AC or direct current (DC) power source. The motor 26 may include any type of motor that can be powered by the VSD 28 or directly from an AC or DC power source, such as a switched reluctance motor, an induction motor, an electronically commutated motor, a permanent magnet motor, another suitable motor (e.g., a driver, a combustion engine), or any combination thereof. In certain embodiments, the vapor compression system 10 may include a control panel 30 (e.g., controller) configured to control operation of the vapor compression system 10. For example, the controller 30 may be coupled to the VSD 28 and may be configured to control operation of the VSD 28, and thus, the compressor 12.

[0036] The compressor 12 compresses a working fluid vapor and delivers the vapor to the condenser 14 through a discharge outlet. In some embodiments, the compressor 12 may be a screw compressor. The working fluid vapor delivered by the compressor 12 to the condenser 14 may transfer heat to a cooling fluid (e.g., water or air) in the condenser 14. The working fluid vapor may condense to a working fluid liquid in the condenser 14 due to thermal heat transfer with the cooling fluid. The working fluid liquid may be directed from the condenser 14 through the first expansion device 16 positioned upstream of the economizer 18 (e.g., flash tank, intercooler). The first expansion device 16 is configured to lower the pressure of (e.g., expand) the liquid working fluid received from the condenser 14. During the expansion process, a portion of the liquid may vaporize, and thus, the economizer 18 may be used to separate the working fluid received from the first expansion device 16 into vapor working fluid and liquid working fluid.New International Application N / JOHCO-179-PCT November 13, 2025 NUGS / nusd

[0037] Additionally, the economizer 18 may provide for further expansion of the liquid working fluid due to a pressure drop experienced by the liquid working fluid when entering the economizer 18 (e.g., due to a rapid increase in volume experienced when entering the economizer 18). The vapor in the economizer 18 may be drawn by the compressor 12 through the economizer outlet conduit 24 (e.g., suction line, economizer line, economizer conduit) and into the compressor 12 via the economizer inlet port 19. In some embodiments, the vapor in the economizer 18 may be drawn to an intermediate stage of the compressor 12. For example, the economizer inlet port 19 may be positioned such that working fluid directed into the compressor 12 is introduced at a pressure that is greater than the pressure of working fluid at the suction inlet of the compressor and lower than the pressure of the working fluid discharged via the discharge port of the compressor 12. The liquid that collects in the economizer 18 may be at a lower enthalpy than the liquid working fluid exiting the condenser 14 due to expansion via the first expansion device 16 and / or in the economizer 18. In this way, the liquid in the economizer 18 is further subcooled. The liquid from the economizer 18 may then flow through the second expansion device 20 to the evaporator 22.

[0038] The liquid working fluid delivered to the evaporator 22 may absorb heat from a conditioning fluid, which may or may not be the same cooling fluid used in the condenser 14. The liquid working fluid in the evaporator 22 may undergo a phase change from the liquid working fluid to a working fluid vapor. For example, the evaporator 22 may reduce the temperature of the conditioning fluid via thermal heat transfer with the working fluid directed through the evaporator 22. Thus, liquid working fluid directed to the evaporator 22 may absorb heat from the conditioning fluid, which may cause the liquid working fluid to evaporate to become vapor working fluid. Thereafter, the vapor working fluid may be directed from the evaporator 22 to the compressor 12 to complete and restart the vapor compression cycle.

[0039] As noted above, some systems employing an economizer may inefficiently direct vapor working fluid from the economizer to the compressor. For example, some systems may orient and / or position economizer inlet ports such that working fluid from the economizer is discharged axially toward the rotors relative to a rotational axis of a respective rotor. However, the economizer inlet port may open and close (e.g., due to rotation of the rotors), such that working fluid from the economizer is introduced into the compressor intermittently. That is, introduction of the working fluid from an economizer inlet port in an axial direction may generate a shutteringNew International Application N / JOHCO-179-PCT November 13, 2025 NUGS / nusd effect that increases an amount of noise and vibration within the compressor. Additionally, some economizer porting may not accommodate certain geometrical characteristics of the rotors of the compressor, thereby further adding to the vibration and noise (e.g., by introducing working fluid from the economizer in a manner that disrupts the working fluid flow already within the compressor). Further still, some economizer inlet ports may be fixed in size, thereby limiting an operating envelope of the compressor. For example, specialized porting may be installed to enable a particular flow rate of working fluid from the economizer to the compressor. However, various operating conditions on the compressor may call for the compressor to operate at different pressures (e.g., decreased suction or discharge pressure, increased suction or discharge pressure). Unfortunately, some economizer inlet porting may limit an amount of adaptability of the economizer inlet porting to meet variable load demands of the system. Thus, it is now recognized that improved systems and methods for introducing vapor working fluid from an economizer to a compressor (e.g., a screw compressor, to a compression cavity of a screw compressor) while minimizing an amount of vibration and / or pulsations within the compressor and / or vapor compression system are desired.

[0040] With the preceding in mind, FIG. 2 is an overhead, cross-sectional view of an embodiment of the compressor 12 that includes a damping system 100 (e.g., integrated economizer intake port and valve assembly, economizer inlet port system) configured to mitigate noise and vibration in the compressor 12. For example, a valve assembly of the damping system 100 may be positioned and / or oriented such that working fluid from the economizer 18 is introduced and mixed with working fluid in the compressor 12 in a more harmonious (e.g., less turbulent) manner relative to some systems. Additionally, the damping system 100 discussed herein provides greater operating adaptability and flexibility by employing a valve assembly having an insert portion that can be switched or readily replaced based on a current load demand of the compressor 12. For example, the damping system 100 discussed herein (e.g., the valve assembly) may be configured to operate with a number of different insert portions, each insert portion having different features, sizes, and / or geometries that enable the different insert portions to introduce working fluid from an economizer at different intermediate pressures based on the operating demands of the compressor 12.

[0041] To facilitate discussion, the compressor 12 and its components may be described with reference to a longitudinal axis 40, an orthogonal axis 42, and a lateral axis 44. It should be notedNew International Application N / JOHCO-179-PCT November 13, 2025 NUGS / nusd that the orthogonal axis 42 and the lateral axis 44 extend in radial directions relative to the longitudinal axis 40. Further, in the illustrated embodiment, the orthogonal axis 42 corresponds to a vertical axis. However, in embodiments in which the rotors of the compressor 12 are oriented along a vertical plane, the orthogonal axis 42 may correspond to a horizontal axis. The compressor 12 includes a compressor housing 46 (e.g., casing, manifold) that contains working components of the compressor 12. The compressor housing 46 may include an intake portion 48 (e.g., a suction side portion), a rotor housing 50 (e.g., a compression portion), and a discharge portion 52 (e.g., a discharge side portion).

[0042] In the illustrated embodiment, the compressor 12 includes a male rotor 56 and a female rotor 58 that are disposed within the rotor housing 50 and are configured to rotate about a first axis 60 and a second axis 62, respectively. The male rotor 56 and the female rotor 58 each extend from at least the intake portion 48 to the discharge portion 52 in a direction substantially along (e.g., parallel) to the longitudinal axis 40, such that the first axis 60 and the second axis 62 also extend along (e.g., parallel to) the longitudinal axis 40. The male rotor 56 includes one or more protruding lobes 64 disposed circumferentially about the male rotor 56. Similarly, the female rotor 58 includes one or more corresponding grooves 66 (e.g., compression chambers, compression cavities) disposed circumferentially about the female rotor 58. The grooves 66 of the female rotor 58 are configured to receive and / or engage with the lobes 64 of the male rotor 56.

[0043] The intake portion 48 includes an intake port configured to receive a working fluid (e.g., the suction pressure working fluid or gas) from a fluid circuit of the vapor compression system 10 (e.g., from the evaporator 22). Particularly, the fluid may be drawn into the intake port and directed toward the rotors 56, 58 disposed within the rotor housing 50. The lobes 64 of the male rotor 56 may mesh with the corresponding grooves 66 of the female rotor 58 to form a series of gaps (e.g., spaced gaps, spaced compression cavities) between the rotors 56, 58. The gaps may cooperate to continuously compress the working fluid received by the compressor 12 and may direct the compressed working fluid toward a discharge port formed within the discharge portion 52. For example, during compressor 12 operation, the gaps may continuously reduce in volume (e.g., along the longitudinal axis 40) as the rotors 56, 58 rotate about the first and second axes 60, 62 to compress the working fluid along the length of the rotors 56, 58 from the intake portion 48 to the discharge portion 52. Thereafter, the compressed working fluid may subsequently flow out of the compressor 12 via the discharge port of the discharge portion 52.New International Application N / JOHCO-179-PCT November 13, 2025 NUGS / nusd

[0044] During operation of the compressor 12, an axial force 70 may be imposed on a male rotor shaft 72 of the male rotor 56 and / or on a female rotor shaft 74 of the female rotor 58. In some embodiments, the axial force 70 may be transmitted to one or more bearings, such as thrust bearings 76, which are radially disposed about the male rotor shaft 72 and / or the female rotor shaft 74. While the illustrated embodiment of FIG. 2 shows the compressor 12 having one thrust bearing 76 associated with the male rotor shaft 72 and one thrust bearing 76 associated with the female rotor shaft 74, it should be noted that the compressor 12 may include two, three, four, five, six, or more than six thrust bearings 76 disposed about (e.g., adjacent to one another) one or both of the male and female rotor shafts 72, 74.

[0045] In certain embodiments, a force application device, such as a balance piston 80 (e.g., a balance piston assembly), may be disposed within a portion of the compressor housing 46 (e.g., the intake portion 48) and may be configured to impose a regulating force 82 (e.g., a counter-force) on the male rotor shaft 72, the female rotor shaft 74, or both. As such, the balance piston 80 may reduce a magnitude of the axial force 70 applied to the thrust bearings 76. The compressor 12 may also include a plurality of bearings 84 (e.g., anti-friction bearings) that are configured to support the male and female rotors 56, 58. Particularly, a first set of the bearings 84 may be disposed about and configured to support the male rotor shaft 72 of the male rotor 56, and a second set of the bearings 84 may be disposed about and configured to support the female rotor shaft 74 of the female rotor 58. The bearings 84 enable more efficient rotation of the male and female rotors 56, 58 about the first and second axes 60, 62.

[0046] As mentioned above, some vapor compression systems employing screw compressors and economizers may introduce vapor working fluid from an economizer into a compression cavity of a compressor such that vibration and noise within the compressor is increased and / or is not adequately attenuated. Additionally, some vapor compression systems may be fixed and / or inflexible systems that have limited adjustability and / or flexibility with respect to an amount of working fluid introduced into a compressor from an economizer, thereby limiting an operating envelope of the compressor. Therefore, the compressor 12 may be equipped with the damping system 100 configured to discharge working fluid from the economizer 18 into the compressor 12 in a more desirable manner (e.g., in a manner that enables a more harmonious mixing of working fluid within the rotor housing 50), thereby decreasing an amount of noise and / or vibration within the compressor 12. As a result, propagation of rotor vibrations to the compressor housing 46New International Application N / JOHCO-179-PCT November 13, 2025 NUGS / nusd and / or to other components of the vapor compression system 10 may be reduced, thereby limiting an amount of wear and / or degradation on the compressor 12 and increasing an operating efficiency of the vapor compression system 10 employing the compressor 12.

[0047] The damping system 100 discussed herein may also provide increased flexibility and / or adjustability with respect to a working fluid flow rate introduced into the compressor 12 from the economizer 18, as discussed in greater detail below. In this way, an operating envelope of the compressor 12 may be increased, thereby further leading to increased operating efficiency. Further still, the damping system 100 discussed herein may utilize the structural robustness of the rotor housing 50 to house various components of the damping system 100, which may otherwise be employed or installed as separate, discrete components along the vapor compression system 10. In this way, an amount of structural support employed to assemble and install such components may be reduced, thereby decreasing costs associated with the manufacture, transportation, assembly, and maintenance of vapor compression systems 10 employing the compressor 12.

[0048] As shown in the illustrated embodiment, the damping system 100 is disposed within the rotor housing 50 on a lateral side of the compressor 12 proximate the female rotor 58. For example, the damping system 100 (e.g., economizer flow inlet system) may include a port 102 (e.g., passage, inlet port, economizer inlet port) formed in (e.g., machined into, drilled into, integrated with) the rotor housing 50, and a valve assembly 104 at least partially positioned (e.g., mounted) within the port 102. In certain embodiments, a contour and / or orientation of the port 102 may be selected to improve working fluid flow (e.g., from the economizer 18) into the compressor 12. For example, the port 102 may be positioned and / or oriented in a direction (e.g., radial direction) that extends crosswise (e.g., transverse) relative to the axis 62 (e.g., extends in a direction along the lateral axis 44). The port 102 may also be offset (e.g., vertically offset, horizontally offset) from a rotor plane (e.g., a plane on which both the first axis 60 and the second axis 62 extend) in a direction along the orthogonal axis 42, such that a working fluid flow directed into the rotor housing 50 via the port 102 may be at least partially tangential to the female rotor 58. For example, in embodiments in which the first axis 60 and the second axis 62 are oriented along a horizontal plane, the port 102 may be offset from (e.g., vertically offset from and positioned below) a horizontal midline (e.g., a diametric dimension) of the female rotor 58 in a direction (e.g., vertical direction) along the orthogonal axis 42. However, in embodiments in which the first axis 60 and the second axis 62 are oriented along a vertical plane, the port 102 mayNew International Application N / JOHCO-179-PCT November 13, 2025 NUGS / nusd be offset from a vertical midline (e.g., a diametric dimension) of the female rotor 58 in a direction (e.g., horizontal direction) along the orthogonal axis 42. Such an orientation of the inlet port 102 may enable working fluid to be injected (e.g., via the valve assembly 104) into the rotor housing 50 in a direction 98 that extends at least partially along a direction of rotation 99 of the female rotor 58. In this way, a more harmonious mixing of working fluid (e.g., economized working fluid flow and main working fluid flow) within the rotor housing 50 may be achieved, thereby decreasing noise and / or vibrations with the compressor 12.

[0049] In certain embodiments, the port 102 may be formed into the rotor housing 50 in a direction (e.g., radial direction, horizontal direction) that extends at least partially along the longitudinal axis 40 (e.g., extends at a non-zero angle relative to the lateral axis 44) toward the discharge portion 52 (e.g., extends at least partially in a direction of compression 97), thereby further encouraging harmonious mixing of working fluid within the compressor 12. Notably, the port 102 may be created or formed without replacing and / or significantly altering the rotor housing 50. Indeed, a positioning and / or orientation of the port 102 may be more precisely selected or determined (e.g., based on desired fluid flow dynamics) and then machined into the rotor housing 50 without altering and / or affecting other compressor 12 components. Thereafter, the valve assembly 104 may be mounted at least partially into the port 102 and may be configured to receive the working fluid flow from the economizer 18 and direct the working fluid flow into the compressor 12.

[0050] It should be appreciated that the damping system 100 discussed herein may be located at different locations along a length of the rotor housing 50 (e.g., any desired position along the longitudinal axis 40 within the rotor housing 50). For example, the damping system 100 may be located closer to the intake portion 48 of the compressor 12 or closer to the discharge portion 52 relative to the illustrated embodiment. However, the orientation and / or positioning of the damping system 100 may be similar to that discussed above. For example, while embodiments of the damping system 100 may be located at any suitable location along the length of the rotor housing 50, the damping system 100 may be oriented in a radial direction along the lateral axis 44 (and / or partially at an angle relative to the lateral axis 44 toward the discharge portion 52), and may be positioned offset from a diametric dimension (e.g., below a horizontal midline) of the female rotor 58. In this way, a more harmonious mixing of working fluid within the compressor 12 may be achieved, thereby limiting an amount of noise and / or vibration within the compressor 12. FurtherNew International Application N / JOHCO-179-PCT November 13, 2025 NUGS / nusd still, by incorporating the damping system 100 discussed herein, a location of the damping system 100 may be selected based on operating demands of the compressor 12. For example, positioning the damping system 100 closer to the intake portion 48 may enable increased compressor 12 capacity, while positioning the damping system 100 closer to the discharge portion 52 may enable increased compressor 12 efficiency.

[0051] To better illustrate the features of the damping system 100 and to facilitate the following discussion, FIG. 3 is a cross-sectional view of an embodiment of the damping system 100 integrated with the compressor 12. As illustrated, the port 102 of the damping system 100 is formed (e.g., machined, drilled) through the rotor housing 50 (e.g., through the compressor housing 46), and the valve assembly 104 is disposed (e.g., mounted) within the port 102. As noted above, by mounting the valve assembly 104 within the port 102 that is machined into the rotor housing 50, an increased amount of structural support and rigidity may be provided to the valve assembly 104, thereby enabling the valve assembly 104 to withstand greater energy fluctuations. Further, positioning the valve assembly 104 within the port 102 may enable a vapor compression system (e.g., vapor compression system 10) to utilize fewer structural components to support a check valve relative to some systems that employ dedicated structural components along fluid lines to support a check valve, thereby reducing costs associated with manufacture, assembly, and / or maintenance of a vapor compression system employing the damping system 100.

[0052] In the illustrated embodiment, the damping system 100 is positioned offset from the axis 62 in a direction (e.g., vertical direction) along the orthogonal axis 42. For example, as shown in FIG. 3, the damping system 100 is offset (e.g., vertically offset) from a rotor plane 63 in a direction (e.g., vertically downward direction) along the orthogonal axis 42. As noted above, the rotor plane 63 may correspond to a plane on which both the first axis 60 and the second axis 62 extend. Thus, in embodiments in which the first axis 60 and the second axis 62 are oriented along a vertical plane, the damping system 100 may be positioned offset from the axis 62 in a direction (e.g., horizontal direction) along the orthogonal axis 42. In this way, working fluid may be injected in a tangential or semi-tangential direction 98 relative to the direction of rotation 99. Further, as noted above, in certain embodiments, the port 102 may be contoured or oriented such that the valve assembly 104 discharges working fluid in a direction at least partially along the longitudinal axis 40 (e.g., port 102 oriented at a non -zero angle relative to the lateral axis 44) toward the discharge portion 52 of the compressor 12. The valve assembly 104 at least partially extendsNew International Application N / JOHCO-179-PCT November 13, 2025 NUGS / nusd within the port 102 and includes a first end 106 (e.g., upstream end, suction end, receiving end, inlet) extending beyond and / or outward from the rotor housing 50 (e.g., extending beyond a lateral boundary of the rotor housing 50), and a second end 108 extending through the port 102 toward a compression chamber 66 (e.g., groove, compression cavity) of the female rotor 58. The valve assembly 104 may be configured to receive working fluid from an economizer via the first end 106, direct the working fluid therethrough, and direct the working fluid into the compression chamber 66 of the female rotor 58 via the second end 108.

[0053] In certain embodiments, the valve assembly 104 may have a split design (e.g., split configuration, separable configuration) such that the valve assembly 104 includes various sections and / or portions fluidly and / or operably coupled to one another and configured to provide a flow path for working fluid from the economizer to the compressor 12. For example, the valve assembly 104 may include an intake portion 110 (e.g., seat portion), a body portion 112, and an insert portion 114. The intake portion 110 may be positioned proximate the first end 106 of the valve assembly 104 and may include a housing 115 that defines a passage 116 (e.g., intake passage) configured to receive working fluid from the economizer 18. In certain embodiments, a diameter of the passage 116 may progressively decrease along the lateral axis 44 in a direction (e.g., direction 98) toward the female rotor 58. For example, the passage 116 may have a tapered profile such that a cross-sectional area of the passage 116 decreases in a direction from the first end 106 to the second end 108 of the valve assembly 104. The tapered profile may be configured to reduce and / or attenuate pulsations from the compressor 12, thereby reducing noise and / or vibrations with the compressor 12 and / or the other components of the vapor compression system 10, as discussed in greater detail below.

[0054] The housing 115 of the intake portion 110 may also define a seat 118 of the valve assembly 104 (e.g., at a distal or downstream end of the passage 116). The seat 118 may be configured to receive or supporta valve member 120 (e.g., a ball) of the valve assembly 104, which may be disposed within the body portion 112. In certain embodiments, the housing 115 may include a collar 122 (e.g., a flange) that defines a plurality of secondary passages 124 configured to receive fasteners 126 (e.g., bolts) to couple (e.g., mount) the valve assembly 104 into the port 102. For example, the fasteners 126 may extend through respective secondary passages 124 and into the rotor housing 50 to secure the valve assembly 104 within the port 102 (e.g., via a threaded connection, bolted connection, etc.).New International Application N / JOHCO-179-PCT November 13, 2025 NUGS / nusd

[0055] The body portion 112 may include a housing 130 that defines an interior volume 131 of the body portion 112, which may be further divided into various passages and / or chambers configured to house components of the valve assembly 104 and / or direct working fluid therethrough. For example, the housing 130 may define a chamber 132 (e.g., cavity), a central passage 134 fluidly coupled to the chamber 132, and a plurality of secondary passages 136 fluidly coupled to the chamber 132. In certain embodiments, the secondary passages 136 may be disposed circumferentially around a central axis of the central passage 134. The housing 130 may also include a protrusion 138 extending in a direction (e.g., radial direction, direction 98) toward the insert portion 114 and configured to interact and / or engage with components of the insert portion 114. The protrusion 138 may define a secondary chamber 140 that may serve to dampen vibrations and / or pulsations, as discussed in greater detail below.

[0056] The ball 120 may be disposed within the chamber 132, and the chamber 132 may be sized to enable the ball 120 to move into and out of engagement with the seat 118. In certain embodiments, the body portion 112 may include a screw 142 (e.g. a shoulder screw) having a first end 144 (e.g., head, shoulder), a second end 146 opposite the first end 144, and a shaft 148 extending from the first end 144 to the second end 146. The first end 144 may be positioned (e.g., housed) within the secondary chamber 140 of the protrusion 138, the second end 146 may be coupled to the ball 120 (e.g., via a threaded connection), and the shaft 148 may extend through or within the central passage 134. The body portion 112 may also include a spring 150 disposed within the secondary chamber 140. The spring 150 may be configured to bias the ball 120 toward the seat 118 when the compressor 12 is inoperative (e.g., shut down). For example, the inherent elasticity in the spring 150 may cause a first end of the spring to engage with the insert portion 114 and a second end of the spring 150 to engage with the first end 144 of the screw 142. When the compressor 12 is inoperative and no working fluid is flowing through the valve assembly 104 in the direction 98, the spring 150 may bias the screw 142, and thus, the ball 120 (e.g., in a direction 101, opposite the direction 98) into engagement with the seat 118, thereby providing a fluid seal that limits an amount of lubricant from traveling in an upstream direction toward the economizer 18.

[0057] The secondary passages 136 may be configured to receive working fluid from the chamber 134 and may direct the working fluid therethrough in the direction 98 toward the insert portion 114. The insert portion 114 may include an insert block 160 configured to receive theNew International Application N / JOHCO-179-PCT November 13, 2025 NUGS / nusd working fluid from the body portion 110 and direct the working fluid into the compression chamber 66 of the female rotor 58. For example, the insert block 160 may include a recess 162 (e.g., cavity) configured to receive the protrusion 138. The insert block 160 may also define one or more passages 164 extending through the insert block 160. The one or more passages 164 may fluidly couple to one another at an outlet 166 of the insert block 160. Notably, a profile 168 (e.g., outer profile, interfacing profile, surface, outer surface) of the insert block 160 that at least partially defines the outlet 166 may be contoured based on a geometry of the female rotor 58, thereby limiting an amount of interference with rotation of the female rotor 58. The outlet 166 may be configured to discharge the working fluid into one of the compression chambers 66, as discussed above, thereby enabling a more harmonious (e.g., less turbulent) mixing of working fluids within the compressor 12. In certain embodiments, the valve assembly 104 may include an alignment pin 170 coupled to the insert block 160 and configured to facilitate proper alignment of the outlet 166 with the compression chamber 66 of the female rotor 58.

[0058] In certain embodiments, the profile 168 of the insert block 160 may be contoured and / or designed such that the outlet 166 discharges fluid into the compressor 12 in a particular manner and / or at a particular intermediate pressure. For example, as mentioned above, the valve assembly 104 may be assembled using a split or segmented design, such that features of the valve assembly 104 may be interchangeable and / or easily replaced, thereby increasing an operating envelope of the compressor 12. In certain embodiments, the valve assembly 104 may be configured to utilize different insert blocks 160, with each insert block 160 having a different profile 168. The varying profiles 168 of the different insert blocks 160 may define respective outlets 166 with different sizes and / or cross-sectional areas. In certain cases, the varying profiles 168 may define respective outlets 166 that are configured to discharge fluid into the compressor 12 at different relative locations within the grooves 66, thereby enabling the different insert blocks 160 to introduce fluid into the compressor 12 at different intermediate pressures. For example, a particular location of the outlet 166 of an insert block 160 may correspond with a particular location along the compression chamber 66 that is associated with a particular intermediate pressure. Thus, by employing different insert blocks 160 having different geometries and / or outlets 166 positioned at different locations (e.g., relative to the chamber 66), different intermediate pressures within the compression chamber 66 may be readily accessed. In this way (e.g., by changing the insert block 160), a capacity and / or efficiency of the compressor 12 may be adjusted based on the load demands of the compressor 12.1New International Application N / JOHCO-179-PCT November 13, 2025 NUGS / nusd

[0059] For example, FIG. 4 illustrates an embodiment of an insert block 160A configured to discharge working fluid into the compressor 12 at a first intermediate pressure (e.g., average intermediate pressure), and FIG. 5 illustrates an embodiment of the insert block 160A in an assembled configuration with the compressor 12. FIG. 6 illustrates an embodiment of an insert block 160B configured to discharge working fluid into the compressor 12 ata second intermediate pressure (e.g., high intermediate pressure), where the second intermediate pressure is greater than the first intermediate pressure, and FIG. 7 illustrates an embodiment of the insert block 160B in an assembled configuration with the compressor 12. FIG. 8 illustrates an embodiment of an insert block 160C configured to discharge working fluid into the compressor 12 at a third intermediate pressure (e.g., low intermediate pressure), where the third intermediate pressure is less than the first intermediate pressure and the second intermediate pressure, and FIG. 9 illustrates an embodiment of the insert block 160C in an assembled configuration with the compressor 12.

[0060] As shown in FIGS. 4 and 5, the insert block 160A may include secondary passages 164A fluidly coupled to the outlet 166A of the insert block 160A. The outlet 166A of the insert block 160A, which may be at least partially defined by the profile 168 A, may be configured to discharge working fluid into the compression chamber 66 at a particular location (e.g., first location) along the compression chamber 66. In certain embodiments, a position and / or orientation of the outlet 166A may enable the insert portion 160A to discharge working fluid into the compression chamber 66 at a particular intermediate pressure (e.g., first intermediate pressure, average intermediate pressure). For example, in certain embodiments, each of the insert blocks (e.g., insert block 160A, insert block 160B, insert block 160C) may include a first side 167 (e.g., first portion, upstream side relative to the direction of compression 97) and a second side 169 (e.g., second portion, downstream side relative to the direction of compression 97). In certain embodiments, the outlet 166A of the insert block 160A may extend between the first side 167 and the second side 169 of the insert block 160A. For example, the outlet 166A may not be positioned proximate the first side 167 or the second side 169, and instead, may be positioned intermediate the first side 167 and the second side 169, thereby enabling the outlet 166A to discharge working fluid into the chamber 66 at a first intermediate pressure (e.g., average intermediate pressure).

[0061] Turning to FIGS. 6 and 7, the insert block 160B may include secondary passages 164B fluidly coupled to the outlet 166B of the insert block 160B. The outlet 166B of the insert block 160B, which may be at least partially defined by the profile 168B, may be configured to dischargeNew International Application N / JOHCO-179-PCT November 13, 2025 NUGS / nusd working fluid into the compression chamber 66 at a particular location (e.g., second location) along the compression chamber 66. In certain embodiments, a position and / or orientation of the outlet 166B may enable the insert portion 160B to discharge working fluid into the compression chamber 66 at a particular intermediate pressure (e.g., second intermediate pressure, high intermediate pressure), where the second intermediate pressure is greater than the first intermediate pressure associated with insert block 160A. For example, the outlet 166B of the insert block 160B may be positioned proximate the second side 169 of the insert block 160B (e.g., at a position more proximate to the second side 169 of the insert block 160 relative to the outlet 166A of the insert block 160A), thereby enabling the outlet 166B to discharge working fluid into the chamber 66 at a second intermediate pressure (e.g., high intermediate pressure). In certain embodiments, the outlet 166B may be positioned and / or configured to discharge working fluid into the chamber 66 further downstream (e.g., further along the direction of compression 97) than working fluid discharged into the chamber 66 via the outlet 166A of the insert block 160 A.

[0062] Turning to FIGS. 8 and 9, the insert block 160C may include secondary passages 164C fluidly coupled to the outlet 166C of the insert block 160C. The outlet 166C of the insert block 160B, which may be at least partially defined by the profile 168C, may be configured to discharge working fluid into the compression chamber 66 at a particular location (e.g., third location) along the compression chamber 66. In certain embodiments, a position and / or orientation of the outlet 166C may enable the insert portion 160C to discharge working fluid into the compression chamber 66 at a particular intermediate pressure (e.g., third intermediate pressure, low intermediate pressure), where the third intermediate pressure is less than the first intermediate pressure associated with insert block 160A and / or the second intermediate pressure associated with the insert block 160B. For example, the outlet 166C of the insert block 160C may be positioned proximate the first side 167 of the insert block 160C (e.g., at a position more proximate to the first side 167 of the insert block 160 relative to the outlet 166A of the insert block 160 A), thereby enabling the outlet 166C to discharge working fluid into the chamber 66 at a third intermediate pressure (e.g., low intermediate pressure). In certain embodiments, the outlet 166C may be positioned and / or configured to discharge working fluid into the chamber 66 further upstream (e.g., along the direction of compression 97) than working fluid discharged into the chamber 66 via the outlet 166A of the insert block 160A.New International Application N / JOHCO-179-PCT November 13, 2025 NUGS / nusd

[0063] Returning to FIG. 3 , the recess 162 of the insert block 160 may be configured to receive the protrusion 138 and thus the secondary chamber 140 containing the screw 142 and the spring 150. As noted above, when the compressor 12 is inactive, the spring 150 may engage with a wall of the recess 162, thereby biasing the screw 142 and thus the ball 120 into engagement with the seat 118. In certain embodiments, one or more rings 172 (e.g., discs, washers, disc springs, Belleville springs) may be employed to facilitate engagement of the body portion 112 with the insert portion 114. For example, the one or more rings 172 may be circumferentially disposed about the protrusion 138 in an assembled configuration of the valve assembly 104, and the rings 172 may be configured to dampen energy fluctuations and / or pulsations during compressor operation. In certain embodiments, the one or more rings 172 may provide a flexible pre-load for coupling the intake portion 110, body portion 112, and insert portion 114. For example, during installation of the valve assembly 104 into the port 102, the fasteners 126 may be threaded into corresponding holes or ports (e.g., threaded holes) within the rotor housing 50. As the fasteners 126 are threaded into the receiving holes, respective heads of the fasteners 126 may interact with (e.g., engage) the collar 122 to draw the collar 122 (e.g., the intake portion 110) into engagement with the body portion 112 of the valve assembly 104. In turn, the body portion 112 may interact with (e.g., engage) the insert portion 114 via the rings 172. In this way, the rings 172 may increase an amount of tolerance associated with the coupling between the body portion 112 and the insert portion 114. Additionally, the valve assembly 104 may include one or more seals 174 (e.g., guiding seals, low friction seals) disposed circumferentially about the shaft 148 of the screw 142 to limit an amount of fluid from traveling through the central passage 134. In certain embodiments, the seals 174 may operate to limit an amount of contact between certain components, thereby reducing wear and / or degradation of such components.

[0064] As noted above, the split design (e.g., separable configuration) may be configured to mitigate damage associated with wear and degradation on the valve assembly 104. For example, by employing the valve assembly 104 discussed herein, certain components of the valve assembly 104 may be contained within features of the valve assembly 104 (e.g., the secondary chamber 140, the recess 162), thereby limiting an amount of wear and / or degradation on the valve assembly 104 and / or components of a vapor compression system employing the valve assembly 104 (e.g., the compressor 12).New International Application N / JOHCO-179-PCT November 13, 2025 NUGS / nusd

[0065] FIG. 10 is a cross-sectional view of an embodiment of a portion (e.g., the body portion 112) of the valve assembly 104 of the damping system 100 in an open position. For example, during compressor operation, working fluid may be directed from an economizer into the valve assembly 104 via the intake portion 110. The working fluid may bias the ball 120 away from the seat 118, thereby enabling the working fluid to enter the chamber 132. For example, the working fluid may impinge against the ball 120, thereby forcing the ball 120 away from the seat 118 and forcing the shaft 148 of the screw 142 to translate through the central passage 134 (e.g., in the direction 98). As the screw 142 translates within the central passage in the direction 98, the first end 144 of the screw 142 positioned within the secondary chamber 140 may engage with a first end 152 (e.g., upstream end) of the spring 150. Notably, because the protrusion 138 is positioned within the recess 162, a second end 154 of the spring 150 may engage with a base 163 of the recess 162, thereby causing the spring 150 to compress. As the spring 150 compresses (e.g., in the direction 98), a size of a volume 180 (e.g., space) between an upstream end 182 of the secondary chamber 140 and the first end 144 of the screw 142 may increase, thereby drawing fluid (e.g., air, lubricant, working fluid) into the volume 180. In this way, the secondary chamber 140 may be configured to provide a damping effect for the components of the valve assembly 104.

[0066] For example, when the compressor 12 is inoperative, the spring 150 may generate a force 184 in a direction 101 (e.g., direction opposite the direction 98) that biases the ball 120 toward the seat 118 (e.g., illustrated in FIG. 11). However, fluid within the volume 180 may limit a magnitude of the force 184 (e.g., due to the drag created by the first end 144 moving through the fluid), thereby generating a damping effect and limiting an amount of wear and / or degradation on the valve assembly 104. In certain embodiments, the valve assembly 104 may be configured to receive a pressurized fluid (e.g., lubricant) from a pressurized fluid source (e.g., lubricant tank, lubrication system of the vapor compression system 10) to improve the damping effect provided by the fluid within the volume 180. For example, based on certain operating conditions (e.g., as detected by one or more sensors), a controller (e.g., controller 30) may operate the pressurized fluid source to selectively direct lubricant into the chamber 140 (e.g., when the valve assembly 104 is in the open configuration), thereby further limiting a magnitude of the force 184 (e.g., due to the drag created by the first end 144 moving through the fluid). In certain embodiments, the controller 30 may operate the pressurized fluid source to direct lubricant into the valve assembly 104 (e.g., into the chamber 140), thereby enabling the controller 30 to selectively control (e.g., regulate, modulate) a position of the valve member 120 relative to the seat 118. Further, as notedNew International Application N / JOHCO-179-PCT November 13, 2025 NUGS / nusd above, the split design configuration of the valve assembly 104 may limit damage associated with wear and degradation of the valve assembly 104. For example, certain components (e.g., ball 120, spring 150, screw 142) may be contained within their respective chambers and / or passages should such components suffer damage from wear and degradation.

[0067] Working fluid within the chamber 132 may be directed through the secondary passages 136 toward the insert block 160 of the valve assembly 104. For example, the secondary passages 136 of the body portion 112 may be fluidly coupled to the one or more passages 164 of the insert block 160, thereby enabling the working fluid to be directed through the passages 164 and into a compression cavity (e.g., compression chamber 66) of the compressor 12 via the outlet 166. Notably, the port 102 that receives the valve assembly 104 (e.g., receives the insert portion 114) may be oriented such that the outlet 166 of the insert block 160 is oriented as discussed above (e.g., in a radial direction relative to a rotational axis of a rotor, at least partially in a direction of rotation of a rotor, at least partially in an axial direction toward a discharge section of a compressor, offset from a diametric dimension of the rotor, offset from a rotor plane of a compressor). In this way, at least a semi-tangential direction and / or velocity may be imparted to the working fluid discharged into the compressor 12, thereby encouraging and / or facilitating more harmonious (e.g., less turbulent) mixing of working fluid within the compressor 12. Further, such improved mixing may reduce an amount of pulsations in the compressor 12, thereby further reducing an amount of noise and / or vibrations generated during operation of the compressor 12.

[0068] While in the open position, the valve assembly 104 (e.g., certain components disposed therein) may be configured to limit, reduce, and / or dampen pulsations of fluid (e.g., working fluid, air, lubricant) from flowing in an upstream direction from the compressor 12 to the economizer (e.g., flowing in the direction 101, flowing from the second end 108 to the first end 106 of the valve assembly 104). For example, the screw 142 may occupy the central passage 134 of the body portion 112, and thus, may limit fluid from traveling through the passage 134. Further, the ball 120 may occupy a substantial (e.g., greater than 50 percent) volume of the chamber 132, and thus, fluid flowing upstream through the valve assembly 104 is first directed to travel around the ball 120 before reaching the seat 118. Further still, the tapered profile of the passage 116 that defines the seat 118 may have a reduced cross-sectional area relative to a cross-sectional area of the chamber 132 such that fluid flow in the upstream direction is further restricted. In these ways, the valve assembly 104 may limit, reduce, and / or dampen pulsations of fluid from traveling upstreamNew International Application N / JOHCO-179-PCT November 13, 2025 NUGS / nusd through the valve assembly 104 and propagating to other components of a vapor compression system employing the valve assembly 104.

[0069] FIG. 11 is a cross-sectional view of an embodiment of a portion (e.g., the body portion 112) of the valve assembly 104 of the damping system 100 in a closed position. For example, when the compressor 12 is inoperative (e.g., inactive, not driving working fluid through the vapor compression system), working fluid may no longer flow from the economizer to the valve assembly 104. As a result, the spring 150 may transition to a decompressed (e.g., natural, resting) position, and the force 184 of the spring 150 may cause the shaft 148 of the screw 142 to translate through the central passage 134 in the direction 101. In this way, the ball 120 of the valve assembly 104 may engage with the seat 118, thereby forming a seal configured to limit an amount of fluid (e.g., lubricant) from traveling in the direction 101 through the valve assembly 104 and to upstream components of a vapor compression system employing the valve assembly 104 (e.g., an economizer). For example, during compressor shutdown, lubricant may be inclined to flow out of the compressor 12. By employing the valve assembly 104, lubricant may be limited from traveling out of the compressor 12 via the port 102.

[0070] FIG. 12 is an exploded perspective view of an embodiment of the valve assembly 104 of the damping system 100. As shown, the valve assembly 104 includes the intake portion 110 having the housing 115 that defines the passage 116, the seat 118, and the collar 122 (e.g., flange). The collar 122 may define the passages 124 configured to receive the fasteners 126, thereby enabling the valve assembly 104 to be mounted to the port 102. The valve assembly 104 further includes the ball 120, and the body portion 112 having the housing 130 that defines the chamber 132 configured to receive the ball 120. The housing 130 may also define the central passage 134, the secondary passages 136, and the protrusion 138. The protrusion 138 may define the chamber 140, and the screw 142 may extend through the central passage 134 such that the second end 146 of the screw couples with the ball 120 (e.g., via a threaded connection). The first end 144 of the screw 142 may be positioned within the chamber 140 along with the spring 150. The valve assembly 104 further includes the insert portion 114 having the insert block 160. The insert block 160 may define the recess 162 configured to receive the protrusion 138, and the passages 164 that terminate at the outlet 166. Notably, the outlet 166 has a contoured surface configured to align with a rotor of a compressor. The valve assembly 104 further includes the alignment pin 170 configured to facilitate orientation, positioning, and alignment of the insert block 160, the ringsNew International Application N / JOHCO-179-PCT November 13, 2025 NUGS / nusd 172 configured to facilitate coupling between the components of the valve assembly 104, and seals 174 configured to limit an amount of fluid from traveling through the central passage 134 occupied by the shaft 148 of the screw 142.

[0071] It should be appreciated that while the figures above describe the valve member 120 as a ball, in other embodiments, the valve member 120 may correspond to any suitable valve member or body capable of transitioning between an open configuration and a closed configuration. Additionally, as mentioned above, in certain embodiments, pressurized fluid may be directed toward the valve assembly 104 to control a position of the valve assembly 104. For example, in certain embodiments, the valve assembly 104 may be fluidly coupled to a pressurized fluid source (e.g., lubricant system of the compressor 12), and may be configured to receive pressurized fluid (e.g., lubricant) from the pressurized fluid source to transition the valve assembly 104 from the closed configuration to the open configuration. Thus, the valve assembly 104 may be controlled to regulate an amount of working fluid directed into the compressor 12. For example, upon determining that the compressor 12 is in an operative mode and / or that a threshold amount of vapor working fluid is present within the economizer (e.g., based on data detected by one or more sensors), a controller (e.g., controller 30) may send a control signal to activate the pressurized fluid source to direct the pressurized fluid toward the valve member 120. As the pressurized fluid is directed toward the valve member 120, the valve member 120 may disengage from the seat 118, thereby enabling working fluid from the economizer to be directed through the valve assembly 104 and into the compressor 12. Conversely, upon determining that the compressor 12 is in an idle or standby mode (e.g., shutdown mode, inoperative mode, non-compressing mode) and / or that less than a threshold amount of working fluid is present within the economizer, the controller may control the pressurized fluid source such that the pressurized fluid is not directed toward the valve member 120. In this way, the spring 150 may bias the valve member 120 toward the closed position, thereby limiting an amount of lubricant from traveling in an upstream direction, as described above.

[0072] As set forth above, the present disclosure may provide one or more technical effects useful in operating HVAC&R systems having economizers and compressors (e.g., screw compressors) that may generate noise, pulsations, and / or vibrations during operation of the HVAC&R system. Embodiments of the present disclosure may include a damping system having a port and a valve assembly oriented and / or positioned such that more harmonious (e.g., lessNew International Application N / JOHCO-179-PCT November 13, 2025 NUGS / nusd turbulent) mixing of working fluid from an economizer into a compressor is achieved. For example, the damping system discussed herein may include a port that is oriented in a radial direction relative to an axis of rotation of a rotor. The port may also be positioned offset from a rotor plane of the compressor (e.g., vertically offset from a rotor plane when the rotors are oriented along a horizontal plane, horizontally offset from a rotor plane when the rotors are oriented along a vertical plane, offset from the rotor plane in a direction that is orthogonal to a longitudinal axis and a lateral axis of the compressor). Further, in certain embodiments, the port may be angled in a direction that extends at least partially toward a discharge section of the compressor. Such positioning and / or orientation may enable a valve assembly positioned within the port to deliver working fluid in at least a semi-tangential direction relative to a direction of compression of the working fluid and / or a direction of rotation of the rotor, thereby achieving more harmonious mixing and / or desirable flow dynamics.

[0073] Additionally, the damping system discussed herein may also provide increased flexibility and / or adjustability with respect to a working fluid flow rate introduced into the compressor from an economizer. For example, insert blocks having outlets with different cross-sectional areas may be employed and installed depending on the load demands of the compressor. Additionally, the position of such insert blocks relative to a longitudinal axis of the compressor (e.g., the injection position) may be adjusted and / or selected depending on the load demands on the compressor. In this way, an operating envelope of the compressor may be increased, thereby further leading to increased operating efficiency. Further still, the damping system discussed herein may utilize the structural robustness of the compressor housing to house various components of the damping system, which may otherwise be employed or installed as separate, discrete components along a vapor compression system. In this way, an amount of structural support employed to assemble and install such components may be reduced, thereby decreasing costs associated with the manufacture, transportation, assembly, and maintenance of vapor compression systems employing the damping system discussed herein.

[0074] While only certain features and embodiments of the disclosure 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, including temperatures and pressures, mounting arrangements, use of materials, colors, orientations, and so forth without materially departing from the novel teachings andNew International Application N / JOHCO-179-PCT November 13, 2025 NUGS / nusd 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.

[0075] 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 of carrying out the disclosure, or those unrelated to enabling the claimed disclosure. It should be noted 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 manufacture for those of ordinary skill having the benefit of this disclosure, without undue experimentation.

[0076] 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

New International Application N / JOHCO-179-PCT November 13, 2025 NUGS / nusd CLAIMS1. A damping system (100) for a heating, ventilation, air conditioning, and refrigeration (HVAC&R) system, comprising:a port (102) integrated with a rotor housing (50) of a compressor (12) of the HVAC&R system, wherein a rotor of the compressor (12) is disposed within the rotor housing (50), the port (102) is oriented in a radial direction relative to an axis of rotation of the rotor within the rotor housing (50), and the port (102) is orthogonally offset from the axis of rotation; anda valve assembly (104) positioned at least partially within the port (102) and configured to direct working fluid from an economizer (18) of the HVAC&R system into the compressor (12), wherein the valve assembly (104) comprises:an intake portion (110) positioned proximate a first end of the valve assembly (104) and configured to receive the working fluid from the economizer (18);an insert portion (114) positioned proximate a second end of the valve assembly (104) and configured to direct the working fluid into the compressor (12); anda body portion (112) fluidly coupling the intake portion (110) to the insert portion (H4).

2. The damping system (100) of claim 1, wherein the valve assembly (104) is configured to direct the working fluid into the rotor housing (50) of the compressor (12) in at least a semi-tangential direction relative to a direction of rotation of the rotor.

3. The damping system (100) of claim 1 or 2, wherein the insert portion (114) comprises an insert block (160) defining one or more passages (164) configured to receive the working fluid from the body portion (112) and direct the working fluid into a compression chamber of the compressor (12) via an outlet of the insert block (160), and wherein a surface of the outlet is contoured to correspond with a geometry of the rotor.

4. The damping system (100) of claim 3, wherein the insert block (160) is one of a plurality of insert blocks (160) that are interchangeable with the insert portion (114), wherein each insert block (160) of the plurality of insert blocks (160) is configured to introduce the working fluid into the compression chamber (66) at a different pressure.32New International Application N / JOHCO-179-PCT November 13, 2025 NUGS / nusd5. The damping system (100) of claim 3 or 4, wherein the intake portion (110) comprises a housing (115) that defines an intake passage (116) and a seat (118) of the valve assembly (104).

6. The damping system (100) of claim 5, wherein the housing (115) of the intake portion (110) is a first housing, and the body portion (112) comprises:a second housing (130), wherein the second housing (130) defines:a chamber (132), wherein a valve member (120) of the valve assembly (104) is disposed within the chamber;a central passage (134) fluidly coupled to the chamber (132); anda plurality of secondary passages (136) fluidly coupled to the one or more passages of the insert block (160); anda protrusion (138) configured to engage with a recess of the insert portion (114), wherein the protrusion defines a secondary chamber (140).

7. The damping system (100) of claim 6, wherein the body portion (112) comprises: a spring (150) positioned within the secondary chamber (140); anda screw (142) having a first end (144), a second end (146), and a shaft (148) extending between the first end (144) of the screw (142) and the second end (146) of the screw, wherein the first end of the screw (144) is positioned within the secondary chamber (140) and is configured to engage with the spring (150), the second end (146) of the screw (142) is coupled to the valve member (120), and the shaft (148) extends through the central passage (134).

8. The damping system (100) of claim 7, wherein the spring (150) is configured to bias the valve member (120) coupled to the second end (146) of the screw (142) toward the seat (118) of the valve assembly (104) to transition the valve assembly (104) to a closed configuration during suspended operation of the compressor (12).

9. The damping system (100) of claim 6, wherein the plurality of secondary passages (124) is disposed circumferentially around a central axis of the central passage (134).33New International Application N / JOHCO-179-PCT November 13, 2025 NUGS / nusd 10. The damping system (100) of any of claims 5 to 9, wherein a diameter of the intake passage (116) progressively decreases in a direction from the first end of the valve assembly (104) to the second end of the valve assembly (104).

11. The damping system (100) of any of claims 5 to 10, wherein the housing (130) comprises a collar (122) defining a plurality of fastener passages (124), wherein each fastener passage of the plurality of fastener passages (124) is configured to receive a respective fastener (126) to mount the valve assembly (104) within the port (102).

12. The damping system (100) of any of claims 1 to 11, wherein the intake portion (110), the body portion (112), and the insert portion (114) are arranged in a separable configuration.

13. A compressor (12) for a heating, ventilation, air conditioning, and refrigeration (HVAC&R) system, comprising:a first rotor (56) comprising one or more lobes (64);a second rotor (58) comprising one or more grooves (66), wherein the one or more grooves (66) of the second rotor (58) are configured to receive the one or more lobes (64) of the first rotor (56) to form one or more spaced compression cavities, and wherein the one or more spaced compression cavities are configured to receive a working fluid, compress the working fluid, and direct the working fluid in a compression direction along a longitudinal axis of the compressor (12);a rotor housing (50) configured to enclose the first rotor (56) and the second rotor (58); and a damping system (100) configured to reduce pulsations, vibrations, or both within the compressor (12), wherein the damping system (100) comprises:a port (102) formed in the rotor housing (50), wherein the port (102) is oriented in a direction extending crosswise relative to the compression direction, and wherein the port (102) is orthogonally offset from an axis of rotation of the second rotor (58); anda valve assembly (104) mounted within the port (102) and configured to direct the working fluid from an economizer (18) of the HVAC&R system into the rotor housing (50) in a semi-tangential direction.New International Application N / JOHCO-179-PCT November 13, 2025 NUGS / nusd 14. The compressor (12) of claim 13, wherein the valve assembly (104) is configured to transition between an open configuration and a closed configuration, wherein, in the open configuration, the valve assembly (104) is configured to block flow of working fluid pulsations through the valve assembly (104) and out of the rotor housing (50), and wherein, in the closed configuration, the valve assembly (104) is configured to block flow of lubricant through the valve assembly (104) and out of the rotor housing (50).

15. The compressor (12) of claim 13 or 14, wherein the valve assembly (104) comprises an insert block (160), wherein the insert block (160) is mounted to the port (102) via an interference fit.

16. The compressor (12) of claim 15, wherein the insert block (160) defines an outlet (166) configured to discharge a flow of the working fluid into the compressor (12) at an intermediate pressure.

17. The compressor (12) of claim 16, wherein the insert block (160) is one of a plurality of insert blocks (160) configured to be interchangeably coupled to the valve assembly (104), wherein different insert blocks (160) of the plurality of insert blocks (160) define different outlets to enable the valve assembly (104) to direct the flow of working fluid into the compressor (12) at different intermediate pressures.

18. A heating, ventilation, air conditioning, and refrigeration (HVAC&R) system, comprising:a compressor (12) comprising a housing (46), a first rotor (56) disposed within the housing (46), and a second rotor (58) disposed within the housing (46), wherein the first rotor (56) and the second rotor (58) extend in a direction along a rotor plane, wherein the first rotor (56) and the second rotor (58) are configured to pressurize a working fluid and direct the working fluid along a working fluid circuit;a condenser (14) configured to receive the working fluid from the compressor (12) and place the working fluid in a heat exchange relationship with a cooling fluid;an economizer (18) configured to receive the working fluid from the condenser (14) and separate the working fluid into a vapor working fluid and a liquid working fluid; andNew International Application N / JOHCO-179-PCT November 13, 2025 NUGS / nusd a damping system (100) configured to mitigate noise, vibrations, pulsations, or any combination thereof associated with operation of the compressor (12), wherein the damping system (100) comprises:a port (102) formed in the housing (46) of the compressor (12), wherein the port (102) is offset from the rotor plane in a direction along an orthogonal axis of the compressor (12); anda valve assembly (104) positioned within the port (102) and configured to direct the vapor working fluid from the economizer (18) into a compression chamber (66) defined by the housing (46) of the compressor (12).

19. The HVAC&R system of claim 18, wherein the port (102) is oriented in a direction that extends at a non-zero angle relative to a lateral axis of the compressor (12) and toward a discharge port (102) of the housing (46).

20. The HVAC&R system of claim 19, wherein the compression chamber (66) of the compressor (12) is configured to receive the working fluid via a suction inlet of the housing (46) at a first pressure and to discharge the working fluid via the discharge port (102) of the housing (46) at a second pressure, wherein the valve assembly (104) is configured to direct the vapor working fluid into the compression chamber (66) in the direction at a third pressure to mix with the working fluid directed through the compression chamber (66) via the suction inlet, wherein the third pressure is greater than the first pressure and less than the second pressure.36

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