Damping system for a compressor

Abstract

A squeeze film damper assembly (100) for a compressor (12) includes a damper sleeve (112) configured to be disposed about a rotor shaft (72) of the compressor (12). The damper sleeve (112) includes a pressure dam recess (166) formed in an inner circumference (145) of the damper sleeve (112). The pressure dam recess (166) is configured to receive a flow of lubricant (24) and pressurize the flow of lubricant (24) via rotation of the rotor shaft (72). The damper sleeve (112) includes an outlet passage (142) extending from the pressure dam recess (166) to an outer circumference (134) of the damper sleeve (122). The squeeze film damper assembly (100) also includes a bearing housing (110) disposed about the damper sleeve (112) to form a damper gap (116) extending between the outer circumference (134) of the damper sleeve (112) and the bearing housing (110). The damper gap (116) is fluidly coupled to the outlet passage (142) and configured to receive the flow of lubricant (24) from the pressure dam recess (166).

Description

[0001] Cross-reference to related applications

[0002] This application claims priority and benefit to U.S. Provisional Application No. 63 / 024,334, filed May 13, 2020, entitled “Damping System for Compressor,” which is incorporated herein by reference in its entirety for all purposes. Background Technology

[0003] This section is intended to introduce the reader to various aspects of the technology that may be related to the various aspects of the present technology described below and / or claimed. This discussion is intended to help provide the reader with background information to facilitate a better understanding of the various aspects of this disclosure. Therefore, it should be understood that these statements should be read in this context and not as an endorsement of any kind.

[0004] Heating, ventilation, air conditioning, and / or refrigeration (HVAC&R) systems typically maintain temperature control in a structure or other controlled space by circulating a fluid (e.g., refrigerant) through a loop via a compressor to exchange heat with one or more additional fluids (e.g., water and / or air). One type of compressor that can be used in HVAC&R systems is a screw compressor, which typically comprises one or more cylindrical rotors mounted inside a hollow housing. Twin-screw compressor rotors typically have helically extending lobes (or grooves) and recesses (or sides) forming threads extending circumferentially around the rotor on their outer radial surfaces. During operation, the rotor threads mesh together, with the lobes on one rotor engaging with corresponding recesses on the other rotor to create a series of gaps between the rotors. These gaps cooperate to form a compression chamber that communicates with the compressor inlet or port and continuously reduces the volume of fluid as the rotors rotate to compress it. In this way, the compressor directs fluid from the compressor inlet to the compressor outlet. In some cases, the rotation of the rotors can generate vibrations that propagate through the compressor housing during compressor operation. Summary of the Invention

[0005] In some embodiments, a squeeze-film damper assembly for a compressor includes a damper sleeve configured to be disposed around a rotor shaft of the compressor. The damper sleeve includes a pressure dam pocket formed in the inner circumference of the damper sleeve, wherein the pressure dam pocket is configured to receive a lubricant flow and pressurize the lubricant flow via rotation of the rotor shaft. The damper sleeve includes an outlet passage extending from the pressure dam pocket to the outer circumference of the damper sleeve. The squeeze-film damper assembly also includes a bearing housing disposed around the damper sleeve to form a damper gap extending between the outer circumference of the damper sleeve and the bearing housing. The damper gap is fluidly coupled to the outlet passage and configured to receive a lubricant flow from the pressure dam pocket.

[0006] In some embodiments, a compressor includes a shaft configured to rotate about an axis and a damper sleeve disposed around the shaft. The damper sleeve includes a pressure dam recess formed in an inner diameter of the damper sleeve and an outlet passage fluidly coupled to the pressure dam recess. The outlet passage extends from the pressure dam recess to an outer diameter of the damper sleeve. The pressure dam recess is configured to receive lubricant from a lubricant supply of the compressor. The shaft, when rotated about the axis, is configured to pressurize the lubricant within the pressure dam recess to produce pressurized lubricant. The compressor also includes a bearing housing disposed around the damper sleeve to form a damper gap extending between the damper sleeve and the bearing housing. The damper gap is fluidly coupled to the outlet passage and configured to receive pressurized lubricant from the outlet passage.

[0007] In some embodiments, a screw compressor includes a rotor shaft configured to rotate about an axis and a damper sleeve disposed around the rotor shaft. The damper sleeve includes an inlet passage, an outlet passage, and a pressure dam recess extending between the inlet passage and the outlet passage. The inlet passage is configured to receive lubricant at a first pressure and guide the lubricant into the pressure dam recess. The rotor shaft and the pressure dam recess are configured to cooperatively pressurize the lubricant within the pressure dam recess during rotation of the rotor shaft about the axis to produce a pressurized lubricant having a second pressure greater than the first pressure. The screw compressor also includes a bearing housing disposed around the damper sleeve to form a damper gap between the damper sleeve and the bearing housing. The damper gap is fluidly coupled to the outlet passage, and the outlet passage is configured to guide pressurized lubricant from the pressure dam recess into the damper gap. Attached Figure Description

[0008] Figure 1 This is a schematic diagram of an embodiment of a screw compressor kit for a heating, ventilation, air conditioning and / or refrigeration (HVAC&R) system according to one aspect of this disclosure;

[0009] Figure 2This is a cross-sectional plan view of an embodiment of a screw compressor that can be used in an HVAC&R system according to one aspect of this disclosure;

[0010] Figure 3 This is a cross-sectional axial view of an embodiment of a squeeze film damper assembly and rotor shaft in a screw compressor that can be used in an HVAC&R system, according to one aspect of this disclosure.

[0011] Figure 4 It is based on one aspect of this disclosure. Figure 3 A cross-sectional side view of an embodiment of a portion of the extruded membrane damper assembly, taken within line 4-4.

[0012] Figure 5 This is a schematic diagram of an embodiment of a portion of a damper sleeve that may be included in a screw compressor extrusion film damper assembly, according to one aspect of this disclosure.

[0013] Figure 6 This is a cross-sectional axial view of an embodiment of a squeeze film damper assembly and rotor shaft in a screw compressor that can be used in an HVAC&R system, according to one aspect of this disclosure.

[0014] Figure 7 It is based on one aspect of this disclosure. Figure 6 A cross-sectional side view of an embodiment of a portion of the extruded membrane damper assembly taken within line 7-7;

[0015] Figure 8 This is a cross-sectional plan view of an embodiment of a screw compressor that can be used in an HVAC&R system according to one aspect of this disclosure;

[0016] Figure 9 This is a cross-sectional axial view of an embodiment of a squeeze film damper assembly and rotor shaft in a screw compressor that can be used in an HVAC&R system, according to one aspect of this disclosure.

[0017] Figure 10 It is based on one aspect of this disclosure. Figure 9 A cross-sectional side view of an embodiment of the extruded membrane damper assembly, taken within line 10-10. Detailed Implementation

[0018] One or more specific embodiments of this disclosure will be described below. These described embodiments are merely examples of the technology currently disclosed. Furthermore, in an effort to provide a concise description of these embodiments, not all features of actual implementations may be described in the specification. It should be understood that, as in any engineering or design project, numerous implementation-specific decisions must be made to achieve the developer's specific goals, such as consistency with system-related and enterprise-related constraints, which may vary from one implementation to another. Moreover, it should be understood that such development efforts can be complex and time-consuming, but these are routine tasks in design, manufacture, and production for those of ordinary skill in the art who benefit from this disclosure.

[0019] In describing the elements of various embodiments of this disclosure, the articles “a / an” and “described” are intended to mean that one or more of the described elements are present. The terms “comprising,” “including,” and “having” are intended to be inclusive and mean that additional elements may be present in addition to the listed elements. Furthermore, it should be understood that references to “an embodiment” or “an embodiment” in this disclosure are not intended to exclude the existence of additional embodiments that are also incorporated with the described features.

[0020] Heating, ventilation, air conditioning, and / or refrigeration (HVAC&R) systems may include vapor compression systems having compressors (e.g., screw compressors) configured to circulate fluid through pipes or ducts in the vapor compression system. For example, a screw compressor may draw in a relatively low-pressure vapor stream (e.g., a refrigerant stream) through its compressor inlet and discharge a vapor stream at a relatively high pressure through its compressor outlet. Thus, the screw compressor facilitates fluid circulation through the vapor compression system.

[0021] Typically, a screw compressor comprises one or more drum-shaped rotors housed within a hollow rotor housing or casing. The rotors typically have helically extending lobes and grooves formed by threads extending around the respective circumference of the rotor on their respective outer radial surfaces. During compressor operation, the rotors engage at junctions between themselves to form a series of gaps extending between the lobes and grooves. These gaps cooperate to form a compression chamber extending along the length of the rotor housing. The compression chamber is in fluid communication with a suction port at one end of the rotor housing (e.g., an axial or radial port near the compressor inlet) and a discharge port at the opposite end of the rotor housing (e.g., an axial or radial port near the compressor outlet). As the rotor rotates, the gaps between the lobes and grooves continuously decrease in volume from the suction port toward the discharge port. In this way, low-pressure vapor entering the compressor inlet is compressed in the compression chamber and discharged as high-pressure vapor through the compressor outlet.

[0022] Each compressor rotor includes a rotor shaft extending from opposite ends of the rotor. Typically, one or more bearings (e.g., anti-friction bearings, such as ball bearings, roller or rolling element bearings, and / or thrust bearings) engage the rotor shaft to rotatably couple the rotor to the rotor housing. Thus, the bearings facilitate rotation of the rotor relative to the rotor housing. In some cases, the rotating rotor can generate vibrations (e.g., rotor vibration) due to high-pressure fluid flow in the compression chamber and / or unbalanced eccentricities that may exist in the rotor. Typical bearings have relatively low or negligible damping coefficients, such that rotor vibrations generated during compressor operation are transmitted from the rotor, through the bearings, and into the rotor housing. Rotor vibrations can propagate from the rotor housing to other components of the compressor.

[0023] In some cases, the transmission of excessive rotor vibration to certain compressor components can lead to mechanical wear and / or performance degradation in these components over time. Therefore, damping devices, such as squeeze-film dampers, can be installed between each rotor shaft and the rotor housing to reduce rotor vibrations that may occur during compressor operation. A squeeze-film damper typically comprises a damper sleeve arranged circumferentially around the rotor shaft. A layer of lubricant (e.g., an oil film) is disposed within a damper gap that extends between the damper sleeve and the damper housing of the squeeze-film damper. A dedicated lubricant pump is used to pressurize the lubricant within the damper gap. During compressor operation, the pressurized lubricant within the damper gap prevents radial movement of the damper sleeve (e.g., relative to the damper housing), and thus allows the damper sleeve to apply a reaction force to the rotor shaft, thereby reducing rotor shaft vibrations (e.g., radial vibrations). Thus, the squeeze-film damper mitigates or substantially eliminates the propagation of rotor vibrations from the rotor to the compressor housing. Disadvantages include the costly use of a lubricant pump to pressurize the lubricant within the damper clearance, which can increase the overall production, maintenance, and / or operating costs of the screw compressor. Furthermore, the lubricant pump is prone to performance degradation, which can lead to less efficient operation of the extruded diaphragm damper over time.

[0024] It is now recognized that operating a squeeze-film damper without utilizing a dedicated lubricant pump that supplies pressurized lubricant to the squeeze-film damper can reduce the overall production, maintenance, and / or operating costs of screw compressors and improve compressor reliability. Therefore, embodiments of this disclosure are directed to a squeeze-film damper assembly configured to pressurize (e.g., self-pressurize) lubricant received from a lubricant supplier and guide the pressurized lubricant into the damper clearance of the squeeze-film damper assembly. In this way, the squeeze-film damper assembly can operate to reduce rotor vibration of a screw compressor without utilizing a dedicated lubricant pump configured to pressurize the damper clearance with lubricant. That is, the disclosed squeeze-film damper assembly can generate a sufficiently pressurized lubricant supply to avoid or mitigate the formation of air bubbles in the lubricant, thus achieving effective operation of the squeeze-film damper without utilizing an external pump or pressure generating device. These and other features will be described below with reference to the figures.

[0025] Now turn to diagrams, Figure 1 This is a schematic diagram of an embodiment of a portion of a vapor compression system 10. The vapor compression system 10 includes a compressor 12, as discussed above, which circulates a fluid stream (e.g., refrigerant, another suitable gas) through various loops or conduits of the vapor compression system 10. A motor 14 may be integrated with or otherwise coupled to the compressor 12 and is used to drive the operation of the compressor 12. The compressor 12 may receive a low-pressure refrigerant or gas stream 18 via a suction conduit 16 and may discharge a pressurized refrigerant or gas stream 20 via a discharge conduit 22. In some embodiments, a portion of the lubricant 24 used to facilitate the operation of the compressor 12 may be mixed with the pressurized refrigerant 20 discharged from the compressor 12. Therefore, the vapor compression system 10 may include an oil separator 26 configured to separate the lubricant 24 from the pressurized refrigerant stream 20. The oil separator 26 allows the lubricant 24 to be separated from the pressurized refrigerant 20 (e.g., gas) and coalesce in the collection chamber 28 of the oil separator 26, while allowing the pressurized refrigerant 20 to be discharged through the discharge port 30. Thus, the pressurized refrigerant 20 can flow from the discharge port 30 to the rest of the vapor compression system 10.

[0026] In some embodiments, lubricant 24 separated from the pressurized refrigerant 20 within the collection chamber 28 may be discharged toward a lubricant supply 32, which supplies lubricant 24 to the compressor 12. Thus, the lubricant 24 collected in the collection chamber 28 may be directed back toward the compressor 12 for reuse after being filtered and / or cooled. For example, in some embodiments, the vapor compression system 10 may include a filter 31 (e.g., an oil filter) and a lubricant cooler 33 fluidly coupled between an oil separator 26 and a lubricant supply 32. The filter 31 is configured to filter contaminants from the lubricant stream 24. The lubricant cooler 33 is configured to reduce the temperature of the lubricant 24. In some embodiments, a pump 35 may be fluidly coupled between the oil separator 26 and the filter 31 and configured to direct lubricant 24 from the collection chamber 28 to the filter 31. The compressor 12 may include a shaft seal and one or more bearings and a squeeze-film damper assembly 34 configured to receive at least a portion of lubricant 24 from a lubricant supply 32. As discussed in detail below, the squeeze-film damper assembly 34 is configured to pressurize the lubricant 24 received from the lubricant supply 32 (e.g., without utilizing a dedicated lubricant pump) to reduce vibrations (e.g., rotor vibrations) that may occur during the rotation of one or more rotors 36 of the compressor 12.

[0027] Figure 2 A cross-sectional view illustrating an embodiment of compressor 12 is provided. For ease of discussion, compressor 12 and its components may be described with reference to longitudinal axis 40, vertical axis 42, and transverse axis 44. It should be noted that vertical axis 42 and transverse axis 44 extend radially relative to longitudinal axis 40. Compressor 12 includes a compressor housing 46 containing the working components of compressor 12 (e.g., bearings, rotor). Compressor housing 46 may include a suction 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).

[0028] In the illustrated embodiment, the compressor 12 includes a male rotor 56 and a female rotor 58, which are disposed within a rotor housing 50 and configured to rotate about a first axis 60 and a second axis 62, respectively. The male rotor 56 and female rotor 58 each extend from at least the suction portion 48 to the discharge portion 52 in a direction generally parallel to the longitudinal axis 40, such that the first axis 60 and the second axis 62 also extend parallel to the longitudinal axis 40. The male rotor 56 includes one or more protruding flaps 64 arranged circumferentially around the male rotor 56. Similarly, the female rotor 58 includes one or more corresponding recesses 66 arranged circumferentially around the female rotor 58. The recesses 66 of the female rotor 58 are configured to receive and / or engage with the flaps 64 of the male rotor 56.

[0029] The suction section 48 includes a suction port configured to receive fluid (e.g., low-pressure refrigerant or gas 18) from the fluid circuit of the vapor compression system 10. Specifically, fluid can be drawn into the suction port and directed toward rotors 56, 58 housed within the rotor housing 50. A lobe 64 of the male rotor 56 can engage with a corresponding groove 66 on the female rotor 58 to form a series of gaps between the rotors 56, 58. These gaps cooperate to continuously compress the fluid received by the compressor 12 and can direct the compressed fluid toward a discharge port formed within the discharge section 52. For example, during operation of the compressor 12, the gaps can continuously decrease in volume (e.g., along the longitudinal axis 40) as the rotors 56, 58 rotate about a first axis 60 and a second axis 62 to compress fluid from the suction section 48 to the discharge section 52 along the length of the rotors 56, 58. The compressed fluid can then subsequently exit the compressor 12 via the discharge port of the discharge section 52.

[0030] During operation of the compressor 12, an axial force 70 may be applied to the male rotor shaft 72 of the male rotor 56 and / or the 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 a thrust bearing 76, which are radially arranged around the male rotor shaft 72 and / or the female rotor shaft 74. Although Figure 2 The illustrated embodiment shows a 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. However, it should be noted that the compressor 12 may include two, three, four, five, six or more thrust bearings 76 arranged (e.g., adjacent to each other) around one or two of the male rotor shaft 72 and the female rotor shaft 74.

[0031] In some embodiments, a force-applying device, such as a balance piston 80 (e.g., a balance piston assembly), may be housed within a portion of the compressor housing 46 (e.g., the suction portion 48) and configured to apply a regulating force 82 (e.g., a reaction force) to the male rotor shaft 72, the female rotor shaft 74, or both. Thus, the balance piston 80 can reduce the magnitude of the axial force 70 applied to the thrust bearing 76. For example, the balance piston 80 may be housed within a chamber 84 of the suction portion 48 and may divide the chamber 84 into a first chamber 86 and a second chamber 88. In some embodiments, the first chamber 86 may be configured (e.g., from the pump 35) to receive a pressurized flow of lubricant 24, and the lubricant 24 within the first chamber 86 may enable the balance piston 80 to generate and apply the regulating force 82 to the male rotor shaft 72. As discussed below, in some cases, a portion of the pressurized lubricant 24 within the first chamber 86 may flow through the balance piston 80 (e.g., via a leakage orifice of the balance piston 80). As a result, the lubricant 24 may flow into the second chamber 88 and / or toward other components of the compressor 12.

[0032] As illustrated in the described embodiments, the compressor 12 may also include a plurality of bearings 94 (e.g., anti-friction bearings) configured to support the male rotor 56 and the female rotor 58. Specifically, a first set of bearings 94 may be disposed around and configured to support the male rotor shaft 72 of the male rotor 56, and a second set of bearings 94 may be disposed around and configured to support the female rotor shaft 74 of the female rotor 58. The bearings 94 enable more efficient rotation of the male rotor 56 and the female rotor 58 about a first axis 60 and a second axis 62. In some embodiments, a plurality of conduits 98 (e.g., channels or passages within the compressor housing 46, external conduits) may extend from the lubricant supply 32 to allow lubricant 24 to flow toward and / or within the compressor 12. In this manner, lubricant 24 may be supplied to the bearings 94, the thrust bearing 76, the rotors 56, 58, and / or various other compressor components.

[0033] As mentioned above, the damping coefficient of bearing 94 is relatively negligible, which can cause vibrations generated by rotors 56, 58 during compressor 12 operation to be transmitted from rotors 56, 58, through bearing 94, and to compressor housing 46. Therefore, compressor 12 may be equipped with squeeze film damper assemblies 34 configured to attenuate vibrations generated by rotors 56, 58 in order to reduce or substantially eliminate the propagation of rotor vibrations to compressor housing 46. In the illustrated embodiment, two squeeze film damper assemblies 34 are arranged around the male rotor shaft 72, and two squeeze film damper assemblies 34 are arranged around the female rotor shaft 74. It should be understood that in other embodiments, any suitable number of squeeze film damper assemblies 34 may be arranged around the male rotor shaft 72 and the female rotor shaft 74. Furthermore, it should be understood that the squeeze film damper assemblies 34 may be located at any suitable position along the male rotor shaft 72 and the female rotor shaft 74, and are not limited to these locations. Figure 2 The corresponding positions shown in the illustrated embodiments.

[0034] To better illustrate the features of the extruded diaphragm damper assembly 34 and to facilitate the following discussion Figure 3 This is a cross-sectional axial view of one embodiment of the extruded film damper assembly 34 of the male rotor 56, which is referred to herein as extruded film damper assembly 100. More specifically, extruded film damper assembly 100 may be disposed around a male rotor shaft 72, which is also referred to herein as shaft 72. Although extruded film damper assembly 100 is described below as being implemented together with male rotor shaft 72, it should be understood that extruded film damper assembly 100 may be implemented together with female rotor shaft 74 or on any other suitable drive shaft or power transmission shaft.

[0035] exist Figure 3 In the illustrated embodiments, the extruded diaphragm damper assembly 100 includes a bearing housing 110 or damper housing circumferentially disposed around the shaft 72. The bearing housing 110 may include a metal sleeve that is press-fitted, threaded, or otherwise coupled to a portion of the compressor housing 46, such as the suction portion 48. In other embodiments, the bearing housing 110 may comprise a portion of the compressor housing 46. That is, the bearing housing 110 may comprise a portion of the compressor housing 46 that has been machined or otherwise manufactured to include the features of the bearing housing 110 discussed herein. For example, one or more features of the bearing housing 110 may be integrated into the compressor housing 46.

[0036] A damper sleeve 112 (e.g., a hydrodynamic bearing) is positioned between a bearing housing 110 and a shaft 72 and extends about the circumference of the shaft 72. The damper sleeve 112 forms a first gap extending between the damper sleeve 112 and the shaft 72, referred to herein as bearing gap 114, and a second gap extending between the damper sleeve 112 and the bearing housing 110, referred to herein as damper gap 116. The damper sleeve 112 and the bearing housing 110 may each be positioned substantially concentrically about a first axis 60 such that bearing gap 114 and damper gap 116 extend axially along at least a portion of the first axis 60. In the illustrated embodiment, an anti-rotation pin 120 extends radially between the bearing housing 110 and the damper sleeve 112 (e.g., relative to the first axis 60). As discussed in detail below, the anti-rotation pin 120 can substantially prevent the damper sleeve 112 from rotating relative to the bearing housing 110, while allowing the damper sleeve 112 to move radially relative to the bearing housing 110 (e.g., relative to the first axis 60).

[0037] In the illustrated embodiment, the bearing housing 110 includes a first inlet passage 126 and a second inlet passage 128 extending radially across the width of the bearing housing 110. Thus, the first inlet passage 126 and the second inlet passage 128 may terminate at corresponding openings formed in the inner circumference 129 or diameter (e.g., inner surface) of the bearing housing 110. The damper sleeve 112 includes a first inlet channel 130 and a second inlet channel 132, each extending from the outer circumference 134 or diameter (e.g., outer surface) of the damper sleeve 112 to the bearing clearance 114. The first inlet passage 126 and the second inlet passage 128 are fluidly coupled to the first inlet channel 130 and the second inlet channel 132. The flow of lubricant 24 from the first inlet passage 126 and the second inlet passage 128 to the first inlet channel 130 and the second inlet channel 132 is further facilitated by a set of seals 136 (e.g., “O” rings). Specifically, seal 136 may be positioned around the respective openings of the first inlet passage 126, the second inlet passage 128, the first inlet channel 130, and the second inlet channel 132, and may extend between the bearing housing 110 and the damper sleeve 112. In this way, seal 136 may isolate (e.g., fluid seal) the corresponding portion of the damper gap 116 extending between the inlet passages 126, 128 and the inlet channels 130, 132, referred to herein as the transmission passage 140, from the remainder of the damper gap 116. Thus, seal 136 may facilitate fluid flow from the first inlet passage 126 and the second inlet passage 128, through the first inlet channel 130 and the second inlet channel 132, and into the bearing gap 114, while preventing a large amount of fluid from flowing directly from the first inlet passage 126 and the second inlet passage 128 into the damper gap 116.

[0038] As illustrated in the described embodiments, the damper sleeve 112 includes (e.g., relative to the first axis 60) a first outlet channel 142 or passageway and a second outlet channel 144 or passageway extending radially from the bearing clearance 114 to the damper clearance 116. Specifically, the first outlet channel 142 and the second outlet channel 144 may extend from the inner circumference 145 or diameter (e.g., the inner surface) of the damper sleeve 112 to the outer circumference 134 or diameter (e.g., the outer surface) of the damper sleeve 112. Thus, the first outlet channel 142 and the second outlet channel 144 fluidly couple the damper clearance 116 to the bearing clearance 114. An outlet port 146 is formed within the bearing housing 110 and, as discussed below, fluidly couples the damper clearance 116 to another area of ​​the compressor 12. The first inlet passage 126 and the second inlet passage 128, the first inlet channel 130 and the second inlet channel 132, the bearing clearance 114, the first outlet channel 142 and the second outlet channel 144, the damper clearance 116 and the outlet port 146 together form a lubricant circuit 160 that realizes the circulation of lubricant through the extrusion membrane damper assembly 100.

[0039] For example, as shown in the illustrated embodiment, the first inlet passage 126 and the second inlet passage 128 can be fluidly coupled to the lubricant supply 32 via conduit 98. Thus, the first inlet passage 126 and the second inlet passage 128 can receive lubricant flow 24 from the lubricant supply 32 and can guide the lubricant 24 into the transfer passage 140. The transfer passage 140 guides the lubricant 24 through the first channel 130 and the second inlet channel 132 and into the bearing clearance 114. The lubricant 24 can then flow from the bearing clearance 114, through the first outlet channel 142 and the second outlet channel 144, through the damper clearance 116, and into the outlet port 146. The outlet port 146 can be fluidly coupled to the lubricant supply 32 so that the used lubricant from the damper clearance 116 is circulated back towards the lubricant supply 32 for reuse in the compressor 12.

[0040] Although Figure 3In the illustrated embodiments, the first inlet passage 126 and the second inlet passage 128 are shown as being directly fluidly coupled to the lubricant supply 32. However, it should be understood that in other embodiments, the first inlet passage 126 and the second inlet passage 128 may be fluidly coupled to any other suitable area or component of the compressor 12 or the vapor compression system 10 to receive the lubricant flow 24 from another area or component. For example, in some embodiments, the first inlet passage 126 and the second inlet passage 128 may be fluidly coupled to the first chamber 86 of the balance piston 80, the second chamber 88 of the balance piston 80, or both. Therefore, in such embodiments, the first inlet passage 126 and the second inlet passage 128 may be configured to receive the lubricant 24 from the first chamber 86 and / or the second chamber 88 of the balance piston 80, rather than from the conduit 98.

[0041] In the illustrated embodiment, the damper sleeve 112 includes a first pressure dam recess 166 extending between a first inlet channel 130 and a first outlet channel 142, and a second pressure dam recess 168 extending between a second inlet channel 132 and a second outlet channel 144. The first inlet channel 130 and the second inlet channel 132 may be located at or near a corresponding first end portion 167 of the first pressure dam recess 166 and the second pressure dam recess 168, and the first outlet channel 142 and the second outlet channel 144 may be located at or near a corresponding second end portion 169 of the first pressure dam recess 166 and the second pressure dam recess 168. The first pressure dam recess 166 and the second pressure dam recess 168 may be formed via grooves, channels, or arcuate slots formed within the damper sleeve 112 and extending (e.g., circumferentially) along the inner circumference 145 or at least a portion of the diameter of the damper sleeve 112. Furthermore, the first pressure dam recess 166 and the second pressure dam recess 168 may extend along the axial length 170 of the damper sleeve 112 (e.g., as shown in the figure). Figure 4 The section extension (shown in the diagram). As discussed in detail below, during operation of the compressor 12, the first pressure dam recess 166 and the second pressure dam recess 168 enable the lubricant 24 received from the lubricant supply 32 to be pressurized via the rotation of the shaft 72, thereby promoting the flow of the lubricant 24 into the damper gap 116. In this way, a pressurized lubricant layer 24 surrounding the damper sleeve 112 is formed within the damper gap 116.

[0042] To better illustrate one of the pressure dam recesses 166 and 168 (e.g., the first pressure dam recess 166) and to facilitate the following discussion, Figure 4 Is Figure 3 A partial cross-sectional view of an embodiment of the extruded diaphragm damper assembly 100, taken within line 4-4. For clarity, it should be noted that... Figure 4In the illustrated embodiment, the outlet port 146 is positioned within the bearing housing 110. Figure 3 The different locations described in the illustrated embodiments. Furthermore, although the first pressure dam recess 166 is discussed primarily below, it should be understood that the second pressure dam recess 168 may include some or all of the features of the first pressure dam recess 166 discussed herein.

[0043] Considering the foregoing, such as Figure 4 As illustrated in the described embodiments, the bearing clearance 114 may include a first portion 180 and a second portion 182 extending from a respective end portion 184 (e.g., an axial end portion) of the damper sleeve 112 to a first pressure dam recess 166. Thus, the first pressure dam recess 166 defines a third portion 186 of the bearing clearance 114 extending between the first portion 180 and the second portion 182 of the damper clearance 114. In some embodiments, the radial dimensions of the first portion 180 and the second portion 182 of the bearing clearance 114 may be relatively small compared to the radial dimension of the first pressure dam recess 166 (e.g., along the third portion 186 of the bearing clearance 114). As described herein, the radial dimension may refer to the radial distance between the outer circumference 194 or diameter of the shaft 72 and the inner circumference 145 or diameter of the damper sleeve 112. For example, in some embodiments, the radial dimensions of the first portion 180 and the second portion 182 of the bearing clearance 114 may be approximately five-thousandths of an inch. The radial dimension of the first pressure dam recess 166 of the bearing clearance 114 may be two, three, or more than three times the radial dimension of the first portion 180 and the second portion 182. Therefore, the radial dimension of the bearing clearance 114 varies between the end portions 184 of the damper sleeve 112 (e.g., along the first axis 60).

[0044] In the illustrated embodiment, the first pressure dam recess 166 is fluidly coupled to the lubricant supply 32 via a lubricant supply passage 190, which is generally defined by a first inlet passage 126, a transfer passage 140, and a first inlet channel 130. The lubricant supply passage 190 allows the flow of lubricant 24 from the lubricant supply 32 to the bearing clearance 114, such that the lubricant 24 can flow toward and physically contact the outer surface of the shaft 72. In some embodiments, one or more bearing seals 196 may be located near the end portion 184 of the damper sleeve 112 and configured to inhibit or substantially prevent the flow of lubricant 24 from the bearing clearance 114 into the environment 198 surrounding the extruded membrane damper assembly 100 or outside the extruded membrane damper assembly, such as a portion of the compressor housing 46.

[0045] For example, bearing seal 196 may comprise a labyrinth seal or other suitable seal extending from the inner circumference 145 of damper sleeve 112 toward the outer circumference 194 of shaft 72. Therefore, bearing seal 196 can mitigate or substantially reduce lubricant leakage between damper sleeve 112 and shaft 72 near the end portion 184 of damper sleeve 112. That is, bearing seal 196 can ensure that substantially all lubricant entering bearing clearance 114 from lubricant supply passage 190 is directed through first outlet passage 142 and second outlet passage 144 (see, for example...). Figure 3 And into the damper gap 116.

[0046] In some embodiments, the bearing seal 196 may extend only around a portion of the inner circumference 145 of the damper sleeve 112. For example, as Figure 5 As illustrated in the described embodiments, the bearing seal 196 may extend along (e.g., axially along) a specific section 200 of the inner circumference 145 of the damper sleeve 112, said specific section being close to the outlet of the first inlet passage 130. In other embodiments, some or all of the bearing seal 196 may be omitted from the extruded membrane damper assembly 100, such that a portion of the lubricant 24 entering the bearing clearance 114 may leak from the bearing clearance 114 into the surrounding environment 198. For example, in such embodiments, the lubricant 24 leaking from the bearing clearance 114 may be directed toward components adjacent to the extruded membrane damper assembly 100 (e.g., in an installation configuration within the compressor 12), such as one of the bearings 94.

[0047] refer to Figure 4 Continuing the discussion below, as detailed below, during the rotation of shaft 72 about the first axis 60, the viscous shear force between the outer surface of shaft 72 and the lubricant 24 within the first pressure dam recess 166 allows the pressurized lubricant 24 to exit through the first outlet channel 142 ( Figure 3 The fluid is discharged into the damper gap 116. The extruded diaphragm damper assembly 100 may therefore include a plurality of circumferential seals 206 configured to fluidly seal the damper gap 116 from the surrounding environment 198 to prevent or substantially mitigate leakage of pressurized lubricant 24 from the damper gap 116 into the surrounding environment 198. For example, the extruded diaphragm damper assembly 100 may include a first circumferential seal 208 and a second circumferential seal 210 disposed around the outer circumference 134 of the damper sleeve 112 and extending (e.g., radially) between the bearing housing 110 and the damper sleeve 112. Thus, the first circumferential seal 208 and the second circumferential seal 210 facilitate the formation of a fluid seal that fluidly isolates the damper gap 116 from the surrounding environment 198.

[0048] As discussed above, seal 136 is configured to prevent fluid from flowing directly from transmission passage 140 to damper gap 116 and vice versa. Thus, seal 136 inhibits the flow of high-pressure lubricant from damper gap 116 into lubricant supply passage 190. In other words, seal 136 allows low-pressure lubricant to flow from lubricant supply 32 through transmission passage 140 into bearing gap 114, while high-pressure lubricant within damper gap 116 is prevented from flowing into transmission passage 140. Outlet port 146 allows at least a portion of pressurized lubricant 24 to be discharged from damper gap 116 and flow toward another suitable component of compressor 12, such as bearing 94, lubricant supply 32, or other compressor components.

[0049] refer to Figure 3 Continuing the discussion below, as noted above, bearing 94 is configured to support shaft 72 and guide rotation of shaft 72 about the first axis 60. In some embodiments, the tolerance between bearing 94 and shaft 72 allows shaft 72 to vibrate or oscillate in the radial direction (e.g., relative to the first axis 60) during operation of compressor 12. Because the radial dimension of bearing clearance 114 (e.g., at least along the first portion 180 and the second portion 182 of bearing clearance 114) is relatively small (e.g., less than five-thousandths of an inch), damper sleeve 112 can move radially with shaft 72 during such vibrating or oscillating motion of shaft 72. In other words, because the overall radial dimension of bearing clearance 114 is relatively small and filled with a lubricant film or layer 24, the relative radial movement between shaft 72 and damper sleeve 112 is substantially negligible. Therefore, when the shaft 72 vibrates radially (e.g., relative to the first axis 60), the shaft 72 and the damper sleeve 112 can move together relative to the bearing housing 110.

[0050] Compared to the overall or average radial dimension of the bearing clearance 114 (e.g., at least along the first portion 180 and the second portion 182 of the bearing clearance 114), the radial dimension of the damper clearance 116 can be relatively large. As a non-limiting example, the damper clearance 116 may include a radial dimension extending radially between the damper sleeve 112 and the bearing housing 110, said radial dimension being two, three, or more than three times the overall or average radial dimension of the bearing clearance 114. Therefore, during the vibration and / or oscillating radial movement of the shaft 72, the damper sleeve 112 can move radially within the bearing housing 110 to cyclically increase and decrease the radial dimension of the damper clearance 116 along various sections of it. The pressurized lubricant 24 within the damper clearance 116 can apply a reaction force to the damper sleeve 112, thereby preventing such radial movement of the damper sleeve 112 within the bearing housing 110. Therefore, the pressurized lubricant 24 in the damper gap 116 enables the damper sleeve 112 to apply a force to the shaft 72 that reduces the amplitude of the radial vibration of the shaft 72.

[0051] In some embodiments, the lubricant 24 discharged from the oil separator 26 may have absorbed refrigerant or other gases due to temperature and / or pressure within the oil separator 26. When the pressure of the lubricant 24 drops below a threshold pressure value (e.g., below the pressure within the oil separator 26), the absorbed gas (e.g., refrigerant) can leave the solution and form bubbles in the lubricant 24. As discussed below, bubble formation in the lubricant 24 can be reduced or substantially eliminated by pressurizing the lubricant 24 in the squeeze film damper assembly 100 to a pressure exceeding the pressure at which the gas enters the solution (e.g., in the oil separator 26). The squeeze film damper assembly 100 is configured to self-pressurize the lubricant 24 received from the oil separator 26, and thus ensures that the lubricant 24 within the damper gap 116 is substantially bubble-free. The bubble-free lubricant 24 allows the squeeze film (e.g., the layer of lubricant 24 in the damper gap 116) to effectively dampen compressor shaft vibrations that may occur during compressor operation.

[0052] It should be understood that the radial dimension of the damper clearance 116 can be set such that even if the shaft 72 oscillates at the upper limit threshold of the radial shaft 72 movement permitted by the bearing 94, the damper sleeve 112 does not mechanically contact the bearing housing 110. In this way, the damper clearance 116 ensures that the bearing 94 substantially supports all radial loads of the male rotor 56 during operation of the compressor 12 and does not transfer the radial loads of the male rotor 56 to the components of the extruded diaphragm damper assembly 100.

[0053] As noted above, the extruded membrane damper assembly 100 can be configured to self-pressurize the damper gap 116 with lubricant 24 without the need for a dedicated lubricant pump. Therefore, the extruded membrane damper assembly 100 can operate to reduce vibration of the compressor 12 shaft according to the techniques described above, without the need for a dedicated lubricant pump configured to facilitate and maintain the supply of pressurized lubricant within the damper gap 116.

[0054] For example, in Figure 3 In the illustrated embodiment, the shaft 72 is configured to rotate counterclockwise 204 about a first axis 60 during operation of the compressor 12. As noted above, the anti-rotation pin 120 suppresses rotational movement of the damper sleeve 112 (e.g., about the first axis 60), which could otherwise be induced by rotation of the shaft 72. Thus, the anti-rotation pin 120 ensures that the first inlet channel 130 and the second inlet channel 132 of the damper sleeve 112 remain circumferentially and radially aligned with the first inlet passage 126 and the second inlet passage 128 of the bearing housing 110 during operation of the extruded membrane damper assembly 100. That is, the anti-rotation pin 120 ensures that the damper sleeve 112 remains rotationally stationary relative to the bearing housing 110, while the shaft 72 can rotate relative to the bearing housing 110 and the damper sleeve 112 (e.g., about the first axis 60). It should be understood that seal 136 can accommodate slight radial movement of damper sleeve 112 relative to bearing housing 110 while still maintaining a fluid seal between damper sleeve 112 and bearing housing 110.

[0055] As discussed above, the lubricant 24 entering the first pressure dam recess 166 and the second pressure dam recess 168 (e.g., via corresponding inlet channels 130, 132) can physically contact the outer surface of the shaft 72. Rotation of the shaft 72 about the first axis 60 (e.g., in a counterclockwise direction 204) generates a viscous shear force between the outer surface of the shaft 72 and the lubricant 24 within the pressure dam recesses 166, 168, sufficient to force the lubricant 24 along the pressure dam recesses 166, 168 in the direction of rotation of the shaft 72. In other words, the viscous shear force between the shaft 72 and the lubricant 24 enables the shaft 72 to force the lubricant 24 along the first pressure dam recesses 166 and the second pressure dam recesses 168 in a counterclockwise direction 204, thereby drawing additional lubricant 24 into the first pressure dam recesses 166 and the second pressure dam recesses 168 via the first inlet channel 130 and the second inlet channel 132. The shaft 72 can continuously force (e.g., via viscous shear) lubricant 24 along the first pressure dam recess 166 and the second pressure dam recess 168 (e.g., in a counterclockwise direction 204) and guide the lubricant 24 onto the corresponding impact surfaces 220, 222 of the pressure dam recesses 166, 168. The impact surfaces 220, 222 can be walls 224 of the damper sleeve 112 defining the portions of the first outlet passage 142 and the second outlet passage 144. The walls 224 can extend generally radially relative to the first axis 60 such that the walls 224 abruptly terminate the contours (e.g., arcuate contours) of the pressure dam recesses 166, 168. When the lubricant 24 abruptly impacts the ends of the pressure dam recesses 166, 168, a higher pressure is generated, thereby allowing the lubricant 24 to be discharged from the pressure dam recesses 166, 168 at a pressure greater than the pressure at which the lubricant 24 enters the pressure dam recesses 166, 168.

[0056] Because the overall or average radial dimension of the damper clearance 116 can be relatively small compared to the radial dimension of the pressure dam recesses 166, 168, substantially all of the lubricant 24, sheared or otherwise forced along the pressure dam recesses 166, 168 (e.g., in the counterclockwise direction 204) by the shaft 72, can impact the impact surfaces 220, 222 and stagnate near the outlet channels 142, 144, while a small portion of the lubricant 24 can bypass the outlet channels 142, 144 and continue to flow along the bearing clearance 114 (e.g., in the counterclockwise direction 204). The stagnation of the lubricant 24 near the outlet channels 142, 144, combined with the continuous shearing of the lubricant 24 by the shaft 72, pressurizes the lubricant 24 within the pressure dam recesses 166, 168, particularly near the outlet channels 142, 144. Therefore, outlet channels 142, 144 can discharge pressurized lubricant 24 into damper clearance 116 at a pressure greater than the pressure received by lubricant 24 through bearing clearance 114 at inlet channels 130, 132. As a non-limiting example, the viscous shear between lubricant 24 and shaft 72 allows outlet channels 142, 144 to discharge pressurized lubricant 24 at discharge pressures greater than the suction pressure of lubricant 24 entering bearing clearance 114 through inlet channels 130, 132, by 5 psi, 10 psi, 20 psi, 30 psi, 40 psi, 50 psi, 60 psi, 70 psi, or exceeding 70 psi. Thus, the extruded diaphragm damper assembly 100 can self-pressurize damper clearance 116 with lubricant 24 without the need for an external lubricant pump. In other words, the extruded membrane damper assembly 100 can receive lubricant 24 at a first pressure from, for example, a lubricant supply 32, and can pressurize the lubricant 24 in the damper gap 116 to a second pressure greater than the first pressure.

[0057] Although Figure 3 The squeeze-film damper assembly 100 in the illustrated embodiment includes two pressure dam recesses 166, 168; however, it should be understood that the squeeze-film damper assembly 100 may include any other suitable number of pressure dam recesses. For example, the squeeze-film damper assembly 100 may include one, two, three, four, or more than four pressure dam recesses formed within the damper sleeve 112 and arranged circumferentially around the shaft 72. Furthermore, it should be understood that the arc length of the pressure dam recesses 166, 168 (e.g., the arcuate dimension between the corresponding inlet channels 130, 132 and the corresponding outlet channels 142, 144) may include any suitable size and is not limited to these dimensions. Figure 3 The dimensions shown in the illustrated embodiments. For example, each of the pressure dam recesses 166, 168 may extend approximately 20%, approximately 30%, approximately 40%, or more than 40% of the outer circumference 194 of the shaft 72.

[0058] In some embodiments, the radial dimensions of the first pressure dam recess 166 and the second pressure dam recess 168 may be substantially constant along the circumference of the shaft 72. In other embodiments, the radial dimensions of the first pressure dam recess 166 and the second pressure dam recess 168 may vary along the circumference of the shaft 72. For example, in such embodiments, the radial dimensions of the first pressure dam recess 166 and the second pressure dam recess 168 near the inlet channels 130, 132 may be greater than or less than the radial dimensions of the pressure dam recesses 166, 168 near the outlet channels 142, 144.

[0059] Outlet port 146 is configured to receive a portion of pressurized lubricant 24 from damper gap 116 and to discharge pressurized lubricant 24 from damper gap 116. Specifically, outlet port 146 may direct pressurized lubricant 24 back toward lubricant supply 32, toward oil cooler, or toward compressor 12 or another suitable component or area of ​​vapor compression system 10. In this way, outlet port 146 allows for continuous flow of lubricant through damper gap 116, such that the lubricant 24 used (e.g., heated lubricant) can be replaced by fresh, cooler-pressurized lubricant 24 received from outlet channels 142, 144, to avoid overheating of the lubricant 24 in damper gap 116, which could allow air bubble formation within the lubricant 24.

[0060] It should be understood that the cross-sectional area of ​​the outlet port 146 may be smaller than the combined cross-sectional area of ​​the first outlet channel 142 and the second outlet channel 144. Therefore, the outlet port 146 may be configured to discharge lubricant 24 at an outflow rate less than the inflow rate at which lubricant 24 can be supplied to the damper gap 116 via the first outlet channel 142 and the second outlet channel 144. Thus, the outlet port 146 ensures that the flow of pressurized lubricant 24 generated by the rotation of the shaft 72 is sufficient to achieve and maintain pressurization of the lubricant 24 within the damper gap 116. In some embodiments, the outlet port 146 may be located near the upper portion (relative to the direction of gravity) of the bearing housing 110. As used herein, the upper portion of the bearing housing 110 may indicate any portion of the bearing housing 110 relative to the direction of gravity above the transverse centerline 228 of the extruded film damper assembly 100, which extends through the first axis 60 and is oriented generally parallel to the transverse axis 44. Therefore, outlet port 146 can receive and discharge gas (e.g., gas or refrigerant bubbles) that may accumulate in the lubricant 24 and gather near the upper portion of the damper gap 116 during operation of the extruded membrane damper assembly 100.

[0061] Figure 6This is a cross-sectional axial view of another embodiment of the extruded membrane damper assembly 100 and shaft 72, wherein the first inlet channel 130 and the second inlet channel 132 are configured to receive lubricant 24 in the axial direction (e.g., along the first axis 60) rather than in the radial direction (e.g., along the transverse axis 44). Figure 7 Is Figure 6 The image shows a cross-sectional view of the extruded diaphragm damper assembly 100 and shaft 72 taken within line 7-7. For clarity, it should be noted that... Figure 7 In the illustrated embodiment, the outlet port 146 is positioned within the bearing housing 110. Figure 6 The different locations in the illustrated embodiments. Figure 6 and 7 This will be discussed below.

[0062] In some embodiments, the first inlet channel 130 and the second inlet channel 132 may include an axial opening 230 formed on the axial surface 232 or axial end face of the damper sleeve 112 and fluidly coupled to the lubricant supply 32 or another suitable lubricant source. Thus, the first inlet channel 130 and the second inlet channel 132 may receive a flow of lubricant 24 at the axial opening 230 and guide the lubricant 24 toward the first pressure dam recess 166 and the second pressure dam recess 168. By enabling the lubricant 24 to enter the first inlet channel 130 and the second inlet channel 132 in the axial direction (e.g., along the first axis 60), the first inlet passage 126, the second inlet passage 128, and the seal 136 may be omitted from the extruded membrane damper assembly 100.

[0063] Figure 8This is a cross-sectional view of an embodiment of compressor 12, wherein the male rotor shaft 72 and female rotor shaft 74 include internal lubricant passages 250 configured to supply lubricant 24 to the extrusion film damper assembly 34. For example, the male rotor shaft 72 includes a first lubricant passage 252 extending from the suction portion 48 of the compressor housing 46 through the body of the male rotor shaft 72 (e.g., along a first axis 60) to the discharge portion 52. Similarly, the female rotor shaft 74 includes a second lubricant passage 254 extending from the suction portion 48 of the compressor housing 46 through the body of the female rotor shaft 74 (e.g., along a second axis 62) to the discharge portion 52. The first passage 252 and the second passage 254 may include axial openings 256 formed in the respective end portions of the male rotor shaft 72 and the female rotor shaft 74 and configured to receive the lubricant flow 24. For example, the axial opening 256 may be fluidly coupled to the lubricant supply 32, fluidly coupled to the first chamber 86 or the second chamber 88 of the balance piston 80, or fluidly coupled to another suitable lubricant source of the compressor 12 configured to supply lubricant 24 to the first passage 252 and the second passage 254. As discussed below, a plurality of radial passages 260 may be formed within the male rotor shaft 72 and the female rotor shaft 74 and configured to guide lubricant 24 from the first passage 252 and the second passage 254 to the extrusion film damper assembly 34.

[0064] To better illustrate Figure 8 The features of the extruded diaphragm damper assembly 34 and, for the purpose of the following discussion Figure 9 This is a cross-sectional axial view of one embodiment of the extruded film damper assembly 34 of the male rotor 56 and the male rotor shaft 72, which is referred to herein as extruded film damper assembly 270. It should be understood that the female rotor shaft 74 and the corresponding extruded film damper assembly 34 may include some or all of the features of the extruded film damper assembly 270 and the male rotor shaft 72 discussed below.

[0065] like Figure 9As illustrated in the described embodiment, the shaft 72 includes a first radial passage 272 and a second radial passage 274 extending radially outward from the first passage 252. The first radial passage 272 and the second radial passage 274 are configured to guide lubricant 24 into the bearing clearance 114, such that the lubricant 24 can fill the bearing clearance 114 and surround the shaft 72. According to the technique discussed above, the shaft 72 can pressurize the lubricant 24 via rotation about a first axis 60 using a first pressure dam recess 166 and a second pressure dam recess 168, and force the pressurized lubricant 24 into the damper clearance 116 via a first outlet passage 142 and a second outlet passage 144. Thus, the extruded film damper assembly 270 is operable to dampen vibrations of the shaft 72 that may occur during operation of the compressor 12. Although in Figure 8 In the illustrated embodiment, shaft 72 includes two radial passages 272, 274, but it should be understood that in other embodiments, shaft 72 may include any suitable number of radial passages.

[0066] Figure 10 Is Figure 9 A cross-sectional view of the extruded diaphragm damper assembly 270 and shaft 72, taken within line 10-10. Figure 10 In the illustrated embodiment, the outlet port 146 is positioned within the bearing housing 110. Figure 9 The different locations in the illustrated embodiments. It should be understood that by enabling the supply of lubricant 24 through shaft 72, the first inlet passage 126 and the second inlet passage 128, the seal 136, and the first inlet channel 130 and the second inlet channel 132 can be omitted from the extruded membrane damper assembly 270. In particular, by enabling the supply of lubricant through shaft 72, the first inlet channel 130 and the second inlet channel 132 can be omitted from the damper sleeve 112. Therefore, the damper sleeve 112 does not contain inlet passages (e.g., one or both of inlet channels 130, 132) for guiding lubricant through the damper sleeve 112 and into the first pressure dam recess 166 and the second pressure dam recess 168.

[0067] In some embodiments, Figure 3 and 6 The extruded membrane damper assembly 100 can surround Figure 9 The shaft 72 is positioned in place of the extruded membrane damper assembly 270. Therefore, it should be understood that the extruded membrane damper assembly 34 can receive lubricant 24 from a combination of lubricant sources and is not limited to the embodiments illustrated and described herein. That is, it should be understood that the embodiments of the extruded membrane damper assemblies 34, 100, and 270 discussed herein are not mutually exclusive.

[0068] As described above, embodiments of this disclosure can provide one or more technical effects that can be achieved in operating a squeeze-film damper without utilizing a dedicated lubricant pump configured to supply pressurized lubricant to the squeeze-film damper. Specifically, embodiments of the squeeze-film damper assembly discussed herein are configured to self-pressurize lubricant received from a lubricant supplier and guide the pressurized lubricant into the damper clearance of the squeeze-film damper assembly. In this way, the squeeze-film damper assembly can operate to reduce rotor vibration of a screw compressor without utilizing a dedicated lubricant pump configured to pressurize the damper clearance of the squeeze-film damper assembly. Consequently, the squeeze-film damper assembly can reduce the overall production, maintenance, and / or operating costs of the screw compressor and can further improve compressor reliability. It should be understood that the technical effects and problems described in this specification are examples and not limitations. In fact, it should be noted that the embodiments described in this specification may have other technical effects and solve other technical problems.

[0069] While only certain features and embodiments are illustrated and described, many modifications and alterations will occur to those skilled in the art without substantially departing from the novel teachings and advantages of the subject matter set forth in the claims. These include variations in the size, dimensions, structure, shape and proportions of various elements, parameter values ​​(e.g., temperature and pressure), installation arrangements, the use of materials, color, orientation, etc. The order or sequence of any process or method steps may be varied or rearranged according to alternative embodiments. Therefore, it should be understood that the appended claims are intended to cover all such modifications and alterations that fall within the true spirit of this disclosure.

[0070] Furthermore, in the effort to provide a concise description of exemplary embodiments, not all features of actual implementations may be described, such as features unrelated to the currently anticipated optimal mode or features unrelated to activation. It should be understood that, as in any engineering or design project, numerous implementation-specific decisions may be made in the development of any such actual implementation. Such development efforts may be complex and time-consuming, but for those of ordinary skill in the art who benefit from this disclosure, these are routine tasks in design, manufacture, and production without requiring excessive experimentation.

Claims

1. A squeeze diaphragm damper assembly for a compressor, comprising: A damper sleeve, the damper sleeve being configured to be disposed around the rotor shaft of the compressor and comprising: A pressure dam recess, formed within the inner circumference of the damper sleeve, is configured to receive a lubricant flow and pressurize the lubricant flow via rotation of the rotor shaft; and An outlet passage extending from the pressure dam recess to the outer circumference of the damper sleeve; and A bearing housing disposed around the damper sleeve to form a damper gap extending between the outer circumference of the damper sleeve and the bearing housing, wherein the damper gap is fluidly coupled to the outlet passage and configured to receive the lubricant flow from the pressure dam recess.

2. The extruded membrane damper assembly of claim 1, wherein the pressure dam recess includes an arcuate slot extending at least a portion of the inner circumference of the damper sleeve.

3. The extruded membrane damper assembly of claim 1, comprising an anti-rotation pin extending between the damper sleeve and the bearing housing, wherein the anti-rotation pin prevents rotational movement of the damper sleeve relative to the bearing housing and allows radial movement of the damper sleeve relative to the bearing housing.

4. The extruded diaphragm damper assembly according to claim 1, comprising: A first inlet passage is formed in the bearing housing and extends to the inner circumference of the bearing housing; as well as A second inlet passage is formed in the damper sleeve and extends from the outer circumference of the damper sleeve to the pressure dam recess, wherein the first inlet passage is fluidly coupled to the second inlet passage to form a lubricant supply passage for the extruded membrane damper assembly.

5. The extrusion membrane damper assembly of claim 4, wherein the lubricant supply passage is configured to receive the lubricant flow from the lubricant supply of the compressor and guide the lubricant flow toward the pressure dam recess.

6. The extrusion membrane damper assembly of claim 1, comprising an inlet passage extending between the pressure dam recess and an opening formed on the axial end face of the damper sleeve, wherein the inlet passage is configured to receive the lubricant flow from the lubricant supply of the compressor and guide the lubricant flow toward the pressure dam recess.

7. The extrusion membrane damper assembly of claim 1, wherein the pressure dam recess is configured to receive the lubricant flow from a passage formed in the body of the rotor shaft of the compressor.

8. The extruded membrane damper assembly of claim 1, comprising an outlet port formed in the bearing housing, wherein the outlet port is configured to receive at least a portion of the lubricant flow from the damper gap and to discharge the portion of the lubricant flow from the extruded membrane damper assembly.

9. The extrusion membrane damper assembly of claim 8, wherein the outlet port is formed within a portion of the bearing housing above the transverse centerline of the extrusion membrane damper assembly relative to the direction of gravity.

10. A compressor, comprising: A shaft configured to rotate about an axis; A damper sleeve, the damper sleeve being disposed around the shaft, wherein the damper sleeve includes a pressure dam recess formed in the inner diameter of the damper sleeve and an outlet passage fluidly coupled to the pressure dam recess and extending from the pressure dam recess to the outer diameter of the damper sleeve, wherein the pressure dam recess is configured to receive lubricant from a lubricant supply of the compressor, and wherein the shaft, when rotating about the axis, is configured to pressurize the lubricant within the pressure dam recess to produce pressurized lubricant; as well as A bearing housing disposed around the damper sleeve to form a damper gap extending between the damper sleeve and the bearing housing, wherein the damper gap is fluidly coupled to the outlet passage and configured to receive the pressurized lubricant from the outlet passage.

11. The compressor of claim 10, wherein the pressure dam recess includes an arcuate slot extending at least a portion of the inner diameter of the damper sleeve.

12. The compressor of claim 11, wherein the arcuate slot terminates at the impact surface of the damper sleeve, wherein the impact surface extends radially outward relative to the axis and forms a portion of the outlet passage.

13. The compressor of claim 10, wherein the outlet passage is fluidly coupled to a first end portion of the pressure dam recess, wherein the damper sleeve includes an inlet passage fluidly coupled to a second end portion of the pressure dam recess, the second end portion being opposite to the first end portion, and wherein the inlet passage is configured to guide the lubricant from the lubricant supply into the pressure dam recess.

14. The compressor of claim 13, wherein the inlet passage includes a first opening formed on the outer diameter of the damper sleeve, wherein the bearing housing includes an additional inlet passage, the additional inlet passage including a second opening formed on the inner diameter of the bearing housing, wherein the inlet passage and the additional inlet passage are fluidly coupled to each other, wherein the compressor includes a seal radially disposed between the damper sleeve and the bearing housing and extending around the first opening and the second opening, and wherein the additional inlet passage is configured to guide the lubricant from the lubricant supply to the inlet passage.

15. The compressor of claim 13, wherein the inlet passage includes an axial opening formed in the axial end face of the damper sleeve, wherein the axial opening is fluidly coupled to the lubricant supply to allow flow of the lubricant from the lubricant supply to the inlet passage.

16. The compressor of claim 13, comprising a balance piston assembly configured to apply an axial force to the shaft, wherein the inlet passage is fluidly coupled to the balance piston assembly and configured to receive the lubricant from the balance piston assembly.

17. The compressor of claim 10, wherein the shaft comprises: An internal passage extending along the axis and configured to receive the lubricant from the lubricant supply; as well as A radial passage extends from the internal passage to the outer diameter of the shaft, wherein the internal passage and the pressure dam recess are fluidly coupled to each other via the radial passage to allow the lubricant to flow from the internal passage to the pressure dam recess.

18. A screw compressor, comprising: A rotor shaft configured to rotate about an axis; A damper sleeve disposed around the rotor shaft, wherein the damper sleeve includes an inlet passage, an outlet passage, and a pressure dam recess extending between the inlet passage and the outlet passage, wherein the inlet passage is configured to receive lubricant under a first pressure and guide the lubricant into the pressure dam recess, and wherein the rotor shaft and the pressure dam recess are configured to cooperatively pressurize the lubricant within the pressure dam recess during rotation of the rotor shaft about the axis to produce a pressurized lubricant having a second pressure greater than the first pressure; as well as A bearing housing is disposed around a damper sleeve to form a damper gap between the damper sleeve and the bearing housing, wherein the damper gap is fluidly coupled to the outlet passage and the outlet passage is configured to guide the pressurized lubricant from the pressure dam recess into the damper gap.

19. The screw compressor of claim 18, wherein the second pressure is 5 psi, 10 psi, 20 psi, 30 psi, 40 psi, 50 psi or more than 50 psi greater than the first pressure.

20. The screw compressor of claim 18, comprising an anti-rotation pin extending between the damper sleeve and the bearing housing, wherein the anti-rotation pin is configured to prevent rotational movement of the damper sleeve about the axis and relative to the bearing housing, and is configured to allow radial movement of the damper sleeve relative to the axis and relative to the bearing housing.

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