Multi-piece resonator insert of valve assembly for refrigerant compressor

Abstract

A resonator insert (30) for a refrigerant compressor including an outer section (72) centered about an axis (A), the outer section including a leading outer ring (90) and a trailing outer ring (91) axially interfaced with one another along the axis. The resonator insert includes an inner section (70) arranged radially inward of the outer section and spaced radially inward from the outer section to define a first annular flow path therebetween. The resonator insert includes a central cone (76) arranged radially inward of the inner section and spaced radially inward from the inner section to define a second annular flow path therebetween. The resonator insert includes a plurality of annular grooves (86A-86F, 88A-88D) open to at least one of the first annular flow path and the second annular flow path, the annular grooves configured to attenuate acoustic noise in refrigerant flowing therethrough. A refrigerant compressor assembly and method are also provided.

Description

MULTI-PIECE RESONATOR INSERT OF VALVE ASSEMBLYFOR REFRIGERANT COMPRESSORSUMMARY

[0001] This application claims the benefit of U.S. Provisional Application No.63 / 762,125, filed February 24, 2025, and U.S. Provisional Application No. 63 / 762,126, filed February 24, 2025, the entirety of which are herein incorporated by reference.BACKGROUND

[0002] Refrigerant compressors are used to circulate refrigerant in a chiller via a refrigerant loop. Refrigerant loops are known to include a compressor, a condenser, an expansion device, and an evaporator. The compressor compresses the fluid, which then travels to the condenser, which in turn cools and condenses the fluid. The refrigerant then goes to the expansion device, which decreases the pressure of the fluid, and to the evaporator, where the fluid is vaporized, completing a refrigeration cycle.SUMMARY

[0003] In some aspects, the techniques described herein relate to a resonator insert for a valve assembly of a refrigerant compressor, including: an outer section centered about an axis, the outer section including a leading outer ring and a trailing outer ring axially interfaced with one another along the axis; an inner section arranged radially inward of the outer section and spaced radially inward from the outer section to define a first annular flow path therebetween; a central cone arranged radially inward of the inner section and spaced radially inward from the inner section to define a second annular flow path therebetween; and a plurality of annular grooves open to at least one of the first annular flow path and the second annularflow path, the annular grooves configured to attenuate acoustic noise in refrigerant flowing therethrough.

[0004] In some aspects, the techniques described herein relate to a resonator insert, wherein the inner section includes a leading inner ring and a trailing inner ring axially interfaced with one another along the axis.

[0005] In some aspects, the techniques described herein relate to a resonator insert, wherein the central cone includes a leading cone section and a trailing cone section axially interfaced with one another along the axis.

[0006] In some aspects, the techniques described herein relate to a resonator insert, wherein the plurality of annular grooves includes a first set of annular grooves formed in a radially inner surface of the outer section and open to the first annular flow path.

[0007] In some aspects, the techniques described herein relate to a resonator insert, wherein the plurality of annular grooves further includes a second set of annular grooves formed in a radially inner surface of the inner section and open to the second annular flow path.

[0008] In some aspects, the techniques described herein relate to a resonator insert, wherein individual grooves of the first set and the second set have different depths, each depth corresponding to a different target noise frequency in a range of 3500 Hz to 9000 Hz.

[0009] In some aspects, the techniques described herein relate to a resonator insert, further including at least one support plate having an outer diameter section, an inner diameter section, and a plurality of radially projecting lugs spacing the outer diameter section from the inner diameter section, wherein the outer diameter section is axially sandwiched between the leading outer ring and the trailing outer ring.

[0010] In some aspects, the techniques described herein relate to a resonator insert, wherein at least one annular groove of the plurality of annular grooves is partially defined bya recess in one of the leading outer ring and the trailing outer ring and partially defined by an axial wall of the outer diameter section of the support plate.

[0011] In some aspects, the techniques described herein relate to a resonator insert, further including a plurality of circumferentially spaced-apart chevron-shaped projections arranged on a downstream portion of the inner section.

[0012] In some aspects, the techniques described herein relate to a resonator insert, wherein the leading outer ring and the trailing outer ring are press-fit together, and optionally laser welded at an axial interface therebetween.

[0013] In some aspects, the techniques described herein relate to a refrigerant compressor assembly including: a refrigerant compressor having an outlet centered about a compressor outlet axis; and a valve assembly mounted downstream of the outlet, the valve assembly including a housing defining an inlet fluidly coupled to the outlet and centered about an inlet axis aligned with the compressor outlet axis, an outlet downstream of the inlet, and a resonator insert.

[0014] In some aspects, the techniques described herein relate to a refrigerant compressor assembly, wherein the housing of the valve assembly has a fixed orientation relative to the refrigerant compressor.

[0015] In some aspects, the techniques described herein relate to a refrigerant compressor assembly, wherein the housing includes a spacer defining a bore open toward an exterior housing of the refrigerant compressor, the resonator insert is received within the bore, and further including a wave spring arranged in the bore and axially urging the resonator insert toward the exterior housing of the refrigerant compressor.

[0016] In some aspects, the techniques described herein relate to a refrigerant compressor assembly, further including a swivel joint permitting selective rotation of at least a portion of the housing about the inlet axis.

[0017] In some aspects, the techniques described herein relate to a refrigerant compressor assembly, wherein the housing includes a first housing sub-assembly rigidly mounted to the refrigerant compressor and containing the resonator insert, and a second housing sub-assembly downstream of the first housing sub-assembly, and further including a swivel joint connecting the first housing sub-assembly to the second housing sub-assembly and permitting selective rotation of the second housing sub-assembly about the inlet axis.

[0018] In some aspects, the techniques described herein relate to a refrigerant compressor assembly, wherein the swivel joint includes a flange of the first housing subassembly axially sandwiched between a flange of the second housing sub-assembly and a plate, and a plurality of fasteners configured to selectively clamp the flanges and plate together to prevent rotation or loosen to permit rotation.

[0019] In some aspects, the techniques described herein relate to a refrigerant compressor assembly, wherein the swivel joint includes a segmented connector assembly axially sandwiching a flange of the second housing sub-assembly, the segmented connector assembly including at least two segmented plates that together fully encircle the inlet axis.

[0020] In some aspects, the techniques described herein relate to a method of assembling a resonator insert for a valve assembly downstream of a refrigerant compressor, the method including: providing a leading outer ring and a trailing outer ring; axially sliding the leading outer ring and the trailing outer ring relative to one another along an axis to form an outer section; positioning an inner section radially inward of the outer section such that the inner section is spaced radially inward from the outer section to define a first annular flow path therebetween; and positioning a central cone radially inward of the inner section such that the central cone is spaced radially inward from the inner section to define a second annular flow path therebetween, wherein, when assembled, the resonator insert includes a plurality ofannular grooves open to at least one of the first annular flow path and the second annular flow path for attenuating acoustic noise.

[0021] In some aspects, the techniques described herein relate to a method, further including axially sliding a leading inner ring and a trailing inner ring relative to one another to form the inner section prior to positioning the inner section radially inward of the outer section.

[0022] In some aspects, the techniques described herein relate to a method, further including laser welding at least one axial interface selected from the group consisting of an interface between the leading outer ring and the trailing outer ring, an interface between components of the inner section, and an interface between components of the central cone.BRIEF DESCRIPTION OF THE DRAWINGS

[0023] Figure 1 schematically illustrates a refrigerant system.

[0024] Figure 2 is a cross-sectional view of an example valve assembly.

[0025] Figure 3 is a perspective view of an example resonator insert.

[0026] Figure 4 is an end view of the example resonator insert.

[0027] Figure 5 is a cross-sectional view of the example resonator insert.

[0028] Figure 6 is a disassembled view of the pieces of example resonator insert.

[0029] Figure 7 is a schematic, partial cross-sectional view of a compressor.

[0030] Figure 8 is a cross-sectional view taken along line 8-8.

[0031] Figure 9 is a side perspective view of the compressor and an example valve assembly.

[0032] Figure 10 is a cross-sectional view of the valve assembly of Figure 9.

[0033] Figure 11 is a side view of the compressor and valve assembly of Figure 9.

[0034] Figure 12 illustrates another example of the valve assembly without a first sub-assembly and with a segmented connector assembly.

[0035] Figure 13 is a perspective view of another example resonator insert.

[0036] Figure 14 is a view from a radially inner location of a portion of the resonator insert of Figure 13.DETAILED DESCRIPTION

[0037] This disclosure relates generally to refrigerant compressors, and more particularly to a valve assembly including a multi-piece resonator insert. The assemblies, systems, and methods disclosed herein have been found to attenuate noise in refrigerant systems.

[0038] Figure 1 illustrates a refrigerant system 10. The refrigerant system 10 includes a main refrigerant loop, or circuit, 12 in communication with a compressor 14, a condenser 16, an evaporator 18, and an expansion device 20. This refrigerant system 10 may be used in a chiller, for example. In that example, a cooling tower may be in fluid communication with the condenser 16. While a particular example of the refrigerant system 10 is shown, this application extends to other refrigerant system configurations, including configurations that do not include a chiller. For instance, the main refrigerant loop 12 can include an economizer downstream of the condenser 16 and upstream of the expansion device 20. The refrigerant system 10 may be an oil-free refrigerant system in one implementation. Further, the compressor 14 may be an oil-free compressor.

[0039] Figure 2 illustrates an example valve assembly 22. The valve assembly includes a first sub-assembly 24 and a second sub-assembly 26 downstream of the first subassembly 24. The first sub-assembly 24 includes a spacer 28 and an assembly providing a multipiece resonator insert 30 (“resonator insert 30”) inside the spacer 28. The second sub-assembly 26 includes a check valve 32, and may be referred to as a check valve assembly. In otherexamples, this disclosure extends to valve assemblies including either a ball valve assembly, a check valve assembly, or both.

[0040] The valve assembly 22 includes a housing 33 defining an inlet 34 and an outlet 36. In this example, the housing 33 is provided as a two-piece structure, with one piece providing a housing of the first sub-assembly 24 and the other piece providing a housing of the second sub-assembly 26. The housing 33 may include one or more structures that are connected together to establish the housing 33.

[0041] The housing 33 defines a flow path for fluid F exiting the compressor 14 to flow relative to the resonator insert 30 and check valve 32. The housing 33 supports the resonator insert 30 and the check valve 32 relative to the fluid F flowing downstream of the compressor 14.

[0042] The housing 33 is configured so as to facilitate mounting of the valve assembly 22 downstream of the compressor 14. In an example, the housing 33 is configured to be directly attached to an exterior housing of the compressor 14.

[0043] During normal operating conditions, fluid F, which in this example is refrigerant, exits the compressor 14, enters the valve assembly 22 via inlet 34, flows through a flow path defined by the housing 33, and exits the valve assembly 22 via outlet 36. In these normal conditions, the check valve 32 is in an open position.

[0044] In some conditions, fluid F may tend to flow in an opposite direction, such as by entering the valve assembly 22 via outlet 36. The check valve 32 is configured to move to a closed position to prevent such flow from reaching the compressor 14. The check valve 32 is therefore configured to permit fluid F to flow from the inlet 34 to the outlet 36, and to prevent fluid F from flowing from the outlet 36 toward the inlet 34.

[0045] A flow path 38 fluidly coupling the inlet 34 to the outlet 36 is substantially straight within the first sub-assembly 24. Within the second sub-assembly 26, the flow path 38exhibits a gradual curvature such that fluid F exiting the outlet 36 has turned substantially 90°, relative to the direction of flow as the fluid F enters the inlet 34. The outlet 36 is fluidly coupled to a location, other than the compressor 14, within the refrigerant circuit 12.

[0046] The check valve 32 is shown in an open position in Figure 2. The check valve 32 includes a disc 40, a stem 42 projecting from the disc 40 and into a guide 44, and a spring 46 biasing the disc 40 toward a seat portion 48 of the housing 33, which is configured to abut a seal 50 supported by the disc 40 when the check valve 32 is in the closed position. In the closed position, fluid F cannot flow from the outlet 36 toward the inlet 34 past the disc 40. During normal operation of the compressor 14, the force of the fluid F overcomes the bias of the spring 46 such that the disc 40 is not in contact with the seat portion 48, and such that fluid F can flow past the check valve 32 toward the outlet 36.

[0047] The guide 44 is surrounded by a flow guide 52. The flow guide 52 supports the guide 44 and establishes a boundary of the flow path 38. The flow guide 52 is supported relative to the housing 33 via one or more arms. In this example, there is an arm 54 supporting the flow guide 52. The flow guide 52 converts dynamic pressure into static pressure with relatively minimal losses.

[0048] The resonator insert 30 is configured to attenuate noise. In particular, the resonator insert 30 is configured to attenuate noises of certain frequencies, which correspond to known noise frequencies associated with operation of the compressor 14.

[0049] The resonator insert 30 is adjacent the inlet 34. The resonator insert 30 could be provided in another location along the flow path 38, including in a location adjacent the outlet 36 or at a location between the inlet 34 and outlet 36. Further, while one resonator is shown, the valve assembly 22 could include more than one resonator. In that case, each of the plurality of resonators may be configured to attenuate noises of a unique frequency or set of frequencies. Providing the resonator insert 30 in the valve assembly 22 attenuates noise withinthe fluid F that has exited from the compressor 14, without requiring a modification to the design of the compressor 14 itself.

[0050] With reference to Figures 2-6, an example resonator insert 30 is shown. The resonator insert 30 is located within the first subassembly 24, and is specifically within a bore of the spacer 28 that is open facing toward the exterior housing of the compressor 14. The spacer 28 has a fixed orientation relative to a remainder of the valve assembly 22 and relative to the compressor 14. The resonator insert 30 is insertable and removable relative to the spacer 28. Specifically, the resonator insert 30 is insertable from a location on the left-hand side of the spacer 28 by moving the resonator insert 30 in the right-hand direction, relative to the orientation in Figure 2. The resonator insert 30 can be replaced by another, similarly-sized resonator if a user desires to attenuate noises of a different frequency, for example.

[0051] The resonator insert 30 is centered about axis A and includes a first axial end 56 and a second axial end 58 opposite the first axial end 56. The first axial end 56 is configured to directly abut an exterior housing of compressor 14, in an example. The second axial end 58 is configured to abut a wave spring 60, which is arranged in a bore of the spacer 28 and is configured to urge the resonator insert 30 toward the exterior housing of the compressor 14, and generally toward the left-hand direction, with reference to Figure 2. The wave spring 60 is configured to hold the resonator insert 30 in compression against the exterior housing of the compressor 14. As will be discussed below, the resonator insert 30 in this disclosure is formed of a number of separate structures. In this way, the resonator insert 30 may be referred to as a multi -piece resonator insert. The wave spring 60 therefore serves to maintain the relative position of the multiple pieces, or structures, of the resonator insert 30. The wave spring 60 also takes up tolerances relative to the resonator insert 30 and / or the bore of the spacer

[0052] The resonator insert 30 in this example includes an inner section 70 arranged radially inward of an outer section 72. The inner section 70 includes an inner ring 74 spacedapart radially inward of the outer section 72, and a cone 76 spaced-apart radially inward of the inner ring 74. In particular, the radially outer surface 78 of the inner ring 74 is spaced-apart from the radially inner surface 80 of the outer section 72 such that fluid can flow between radially outer surface 78 and radially inner surface 80 to interface with the grooves of the outer section 72. Further, a radially inner surface 82 of the inner ring 74 is spaced-apart radially from the cone 76 such that fluid can flow between the cone 76 and the radially inner surface 82 to interface with grooves of the inner ring 74.

[0053] The cone 76 is supported relative to inner ring 74 by one or more radially projecting lugs 84. The inner ring 74 is supported relative to the outer section 72 by one or more radially projecting lugs 85. Here, there are three lugs 84 spaced-apart from one another by substantially 60° about axis A, and there are three lugs 85 spaced-apart from one another by substantially 60° about axis A. The inner ring 74 and cone 76 exhibit curved leading and trailing edges.

[0054] Providing the resonator insert 30 with the inner section 70 and outer section 72 breaks up the fluid F passing through resonator insert 30 into smaller volumes, which increases the likelihood and ability of fluid to interact with one or more of the grooves. In this regard, while one inner section with an additional, dedicated set of grooves is shown, there could be additional inner sections, such as one or more sections radially inward of inner section 70, each with an additional, dedicated set of grooves.

[0055] With specific reference to Figure 5, and with continued reference to Figure 2, the resonator insert 30, in this example, includes grooves 86A-86F formed in radially inner surface 80 and grooves 88A-88D formed in radially inner surface 82. While six grooves 86A-86F are shown relative to the radially inner surface 80 and four grooves 88A-88D are shownrelative to radially inner surface 82, the resonator insert 30 could include one or more grooves formed in each of the surfaces 80, 82. Additionally, while there are grooves in both surfaces 80 and 82, this disclosure extends to configurations where only one of the surfaces 80, 82 includes grooves. In this example, the grooves 86A-86F extend continuously about a circumference of the radially inner surface 80, and grooves 88A-88D extend continuously about a circumference of the radially inner surface 82. While different quantities of grooves are shown relative to the surfaces 80, 82, the resonator insert 30 could include a like quantity of grooves in the surfaces 80, 82.

[0056] The grooves 86A-86F are spaced-apart from one another along the flow path 38 (i.e., in the left-to-right direction, relative to Figure 2). Likewise, grooves 88A-88D are spaced-apart from one another along the flow path 38.

[0057] Each of the grooves 86A-86F, 88A-88D may be configured to attenuate noise of a different frequency. In particular, each of the grooves 86A-86F, 88A-88D may exhibit a unique depth relative to the other grooves 86A-86F, 88A-88D, and the depth of each groove 86A-86F, 88A-88D corresponds to the frequency of noise that the groove is configured to attenuate. As fluid F passes through the resonator insert 30, some of that fluid enters grooves 86A-86F, 88A-88D, and the sound waves inside the grooves 86A-86F, 88A-88D interfere with the incoming sound waves from the fluid flow, leading to destructive interference and a reduction in the overall amplitude of the sound waves. The resonator insert 30 may be referred to as a noise attenuator.

[0058] Each of the grooves 86A-86F, 88A-88D exhibits a rectangular cross-sectional shape, in this example. This disclosure extends to grooves 86A-86F, 88A-88D of different cross-sectional shapes.

[0059] The resonator insert 30 may be configured to attenuate noise frequencies within a range from 3500 Hz to 9000 Hz. Such frequencies may experience at least a 16 dBreduction in acoustic noise. Such noise frequencies are known to occur in certain centrifugal refrigerant compressors. In particular, the range of noise frequencies targeted by the abovediscussed arrangement corresponds to the noises generated based on the speeds, capacity, etc., corresponding to centrifugal refrigerant compressors, as opposed to other types of compressors, such as those associated with turbochargers, which operate at significantly higher speeds, among other differences.

[0060] With specific reference now to Figures 5 and 6, and example arrangement of the resonator insert 30 will now be described.

[0061] As shown, the outer section 70 is provided by a leading outer ring 90 and a trailing outer ring 91. The term “leading” generally refers to an upstream component, and the term “trailing” refers generally to a downstream component. The leading outer ring 90 and trailing outer ring 91 are configured to interface with one another by sliding axially relative to one another, specifically along axis A. Specifically, the leading outer ring 90 and trailing outer ring 91 interface such that radially inner surfaces thereof establish at least a portion of the radially inner surface 80. Further, leading outer ring 90 and trailing outer ring 91 are concentric about axis A.

[0062] In this example, the leading outer ring 90 includes a recessed outer diameter section 92 configured to fit within an increased inner diameter section 93 of the trailing outer ring 91. In this example, a plate 89 including an outer diameter section 94 radially spaced-apart from an inner diameter section 95 via lugs 85 is arranged such that outer diameter section 94 is sandwiched axially between a trailing edge 96 of the leading outer ring 90 and a lip 97 of trailing outer ring 91. A radially inner surface of outer diameter section 94 establishes a portion of the radially inner surface 80. Outer diameter section 94 and inner diameter section 95 are solid, in this example. The plate 89 is hollow between outer and inner diameter sections 94, 95, except for lugs 85.

[0063] In this example, groove 86A is partially defined by a recess formed in leading outer ring 90 and is further partially defined by a leading wall 98 of outer diameter section 94. Groove 86B is partially defined by a recess formed in trailing outer ring 91 and is further partially defined by a trailing wall 99 of outer diameter section 94. Grooves 86C and 86D are formed entirely in trailing outer ring 91.

[0064] Inner section 72 is provided by a leading inner ring 100 and a trailing inner ring 101. The leading inner ring 100 and trailing inner ring 101 are configured to axially interface relative to one another by sliding axially relative to one another. The leading inner ring 100 and trailing inner ring 101 establish at least a portion of the radially inner surface 82. Further, leading inner ring 100 and a trailing inner ring 101 are concentric about axis A.

[0065] In this example, the leading inner ring 100 includes a recessed outer diameter section 102 configured to fit within an increased inner diameter section 103 of the trailing inner ring 101. Further, inner diameter section 95 is sandwiched axially between a lip 104 of leading inner ring 100 and a leading edge 105 of trailing inner ring 101. An outer diameter of the inner diameter section 95, leading inner ring 100, and trailing inner ring 101 are all substantially radially aligned adjacent the inner diameter section 95.

[0066] In this example, a plate 106 including an outer diameter section 107 radially spaced-apart from an inner diameter section 108 via lugs 84 is arranged such that outer diameter section 107 is sandwiched axially between a trailing edge 109 of the leading inner ring 100 and a lip 110 of trailing outer ring 101. A radially inner surface of outer diameter section 107 establishes a portion of radially inner surface 82. Outer diameter section 107 and inner diameter section 108 are solid, in this example. The plate 106 is hollow between outer and inner diameter sections 107, 108, except for lugs 84.

[0067] In this example, grooves 88A and 88B are formed entirely in leading inner ring 100. Groove 88C is partially defined by a recess formed in leading inner ring 100 and isfurther partially defined a leading wall 111 of outer diameter section 107. Groove 88D is partially defined by a recess formed in trailing inner ring 101 and is further partially defined by a trailing wall 112 of outer diameter section 107.

[0068] Cone 76 is provided by a leading cone section 113 and a trailing cone section 114. The leading cone section 113 and trailing cone section 114 are configured to axially interface relative to one another. Leading cone section 113 and a trailing cone section 114 are concentric about axis A.

[0069] In this example, the leading cone section 113 includes a recess 115 receiving a projection 116 of trailing cone section 114. Inner diameter section 108 is sandwiched axially between a trailing edge 117 of the leading cone section 113 and a lip 118 of trailing cone section 114. Radially outer surfaces of the leading cone section 113, trailing cone section 114, and inner diameter section 108 are substantially radially aligned adjacent inner diameter section 108.

[0070] The various components (i.e., the “pieces” of the resonator insert 30) described above may be assembled relative to one another and held in place as relatively snug press-fit components, held under compression by wave spring 60. Alternatively or additionally, various components may be affixed to one another via known techniques, such as laser welding. As examples, one or more laser welds may be provided at the axial interfaces of the leading and trailing outer rings 90, 91, the leading and trailing inner rings 100, 101, and / or the inner and outer cone sections 113, 114. The various components of the multi-piece resonator insert 30 may be formed as turned parts, sintered parts, or using additive manufacturing, as examples.

[0071] The above-described multi -piece arrangement of the resonator insert 30 increases the ease of manufacturing and assembling the resonator insert 30, and further provides opportunity for increased customization, as a user may select one or more componentshaving a desired groove depth or shape such that the resonator insert 30 can be tailored to attenuate noises of desired frequencies.

[0072] Another implementation of this disclosure relates to a swivel joint for use with connecting a valve assembly to a refrigerant compressor. The swivel joint may be used relative to valve assembly 22. The other implementation will be shown and described relative to Figures 7-12.

[0073] Figure 7 illustrates, in cross-section, a portion of an example compressor 214, which may provide the compressor 14 in Figure 1. The compressor 214 is a centrifugal refrigerant compressor in this example. The compressor 214 includes a housing 221. The housing 221 may be made of one or more interconnected pieces. The housing 221 defines a flow path through which fluid F, which here is refrigerant, flows through the compressor 214 and provides an enclosure for the components of the compressor 214.

[0074] Within the housing 221, the compressor 214 includes an electric motor 222 having a stator 224 arranged radially outside of a rotor 226. The rotor 226 is connected to a shaft 228, which rotates to drive at least one compression stage 230 of the compressor 214, which in this example includes at least one impeller 232. The compressor 214 may include multiple compression stages.

[0075] The shaft 228 and impeller 232 are rotatable by the electric motor 222 about an axis A to compress fluid F. The shaft 228 may be rotatably supported by a plurality of bearing assemblies, which in some examples are magnetic bearing assemblies.

[0076] During operation of the compressor 214, fluid F flows axially along axis A toward the impeller 232 and is expelled radially outwardly, relative to axis A, to a diffuser 234 downstream of the impeller 232. The diffuser 234 is arranged between the outlet 246 of the compressor 214 and a volute 240. The volute 240 may be in fluid communication with thecondenser 16 or another compression stage of the compressor 214. As shown in Figure 3, which will now be described, the volute 240 is in direct fluid communication with the outlet 246.

[0077] With reference to Figure 8, as the volute 240 approaches the outlet 246, the volute 240 transitions from establishing a spiral flow path (i.e., the “spiral section” of the volute 240) to a substantially linear flow path (i.e., a “linear section” of the volute 240). The outlet 246 is centered about an axis X. Refrigerant exiting the compressor 214 via outlet 246 flows along axis X. The axis X and the axis A are skew lines, and specifically are non-parallel, nonintersecting lines that exist in different planes.

[0078] In this example, fluid F exiting the compressor 214 via outlet 246 flows into a valve assembly 248, which is shown in Figures 9-12. The valve assembly 248 includes a first sub-assembly 250 (Figure 10) and a second sub-assembly 252 downstream of the first subassembly 250. The first sub-assembly 250 includes an assembly providing a multi-piece resonator insert 254 (“resonator insert 254”) therein. The second sub-assembly 252 includes a check valve 256, and may be referred to as a check valve assembly. In other examples, this disclosure extends to valve assemblies including either a ball valve assembly, a check valve assembly, or both. This disclosure extends to valve assemblies without a resonator. In other words, the first sub-assembly 250 could exclude resonator insert 254. Further, this disclosure extends to assemblies without the first sub-assembly 250.

[0079] The valve assembly 248 includes a housing 258 defining an inlet 260 and an outlet 262. In this example, the inlet 260 is centered about axis X. The outlet 262 is centered about an axis Z, which is substantially perpendicular to axis X and intersects axis X.

[0080] In this example, the housing 258 is provided as a multi-piece structure, with a first housing sub-assembly 264 providing a housing of the first sub-assembly 250 and a second housing sub-assembly 266 providing a housing of the second sub-assembly 252.

[0081] The first housing sub-assembly 264 is rigidly-mountable to the housing 221 of the compressor 214. The second housing sub-assembly 266 is able to swivel relative to the first housing sub-assembly 264 to rotate the second housing sub-assembly 266 about the axis X. Permitting rotation of the second housing sub-assembly 266 increases the ease of positioning of the valve assembly 48, and / or piping that is to attach to outlet 262, relative to the compressor 214. For this reason, the valve assembly 248 may be particularly beneficial when used relative to compressors that were not originally designed or laid-out to accommodate a downstream valve assembly. In other words, the valve assembly 248 may be relatively easily retrofit to existing systems, regardless of how those systems were originally designed and laid out.

[0082] The first housing sub-assembly 264 includes a leading housing component 268 and a trailing housing component 270. The term “leading” generally refers to an upstream component, and the term “trailing” refers generally to a downstream component. The term “component” is not intended to be a generic or nonce term, but instead refers to a structure providing a portion of the first housing sub-assembly 264.

[0083] Adjacent inlet 260, leading housing component 268 includes a flange 272 configured to directly interface with the housing 221 of compressor 214 adjacent the outlet 246. In an example, flange 272 is configured to interface with fasteners 274 (Figure 9), such as bolts, which are configured to directly interface with the housing 221 to hold the valve assembly 248 relative to the housing 221.

[0084] The leading housing component 268 defines a bore 276 centered about axis X within which resonator insert 254 is received. The resonator insert 254 is also centered about axis X and includes a first axial end 278 and a second axial end 280 opposite the first axial end 278. The first axial end 278 is configured to directly abut an exterior of the housing 221, in an example. The second axial end 280 is configured to abut a wave spring 282, which is arrangedin bore 276 and is configured to urge the resonator insert 254 toward the exterior of housing 221, and generally toward the left-hand direction, with reference to Figure 10. The wave spring 282 is configured to hold the resonator insert 254 in compression against the exterior housing of the compressor 214. The resonator insert 254 in this disclosure may be formed of a number of separate structures, or pieces, which may be press-fit relative to one another. The wave spring 282 therefore serves to maintain the relative position of the multiple pieces, or structures, of the resonator insert 254. The wave spring 282 also takes up tolerances relative to the resonator insert 254 and / or the bore 276.

[0085] Downstream of bore 276, the leading housing component 268 is connected to the trailing housing component 270. In this example, the leading housing component 68 threadingly engages the trailing housing component 270. Alternatively, or in addition to being threadingly engaged with one another, the leading and trailing housing components 268, 270 may be connected via other known techniques, such as welding. Here, the leading and trailing housing components 68, 70 are both threaded and welded together.

[0086] The trailing housing component 270 includes a flange 284 adjacent a trailing edge of the first housing sub-assembly 264. The flange 284 is axially sandwiched (i.e., relative to axis X) between a flange 286 of the second housing sub-assembly 266 and a plate 288. Flange 286 is adjacent a leading edge of the second housing sub-assembly 266. Plate 288 is on an opposite axial side (i.e., relative to axis X) of flange 284 as flange 286.

[0087] Flanges 284, 286, 2plate 88, and fasteners 290 establish a swivel joint S.The swivel joint S may include one or more seals, such as O-ring 91, to establish a fluid-tight interface between flanges 284, 286 and plate 288. Fasteners 290 are configured to directly engage flange 286 and plate 288. The fasteners 290 may be configured as bolts including threaded shanks. In particular, flange 286 is configured to support fasteners 290 and includes through-bores through which threaded shanks of the fasteners 290 may extend, and plate 288may include threaded openings for engaging with threaded shanks of the fasteners 290. Alternatively, nuts arranged adjacent plate 88 may receive the shanks of the fasteners.

[0088] When the fasteners 290 are tightened, a compressive force is applied, squeezing flange 286 and plate 288 against flange 284 such that the second housing subassembly 266 is prevented from rotating about axis X via the swivel joint S, and such that a fluid-tight seal is established between the first and second housing sub-assemblies 264, 266. When the fasteners 290 are loosened, a user may rotate the second housing sub-assembly 266 about axis X via swivel joint X. Movement of the second housing sub-assembly 266 about axis X via swivel joint S does not result in corresponding movement of the first housing subassembly 264, which is rigidly mounted to housing 221. When the second housing subassembly 266 is in a desired position, fasteners 290 may be tightened, thereby holding the relative position of the second housing sub-assembly 266.

[0089] In an example, the swivel joint S permits rotation of the second housing subassembly 266 about axis X by an angle 9 (Figure 6). The angle 9 is measured between axis Z and a gravity axis GA. The gravity axis GA is a vertically up-and-down axis on which the direction of the force of gravity lies. The gravity axis GA may be coincident with a plumb line. The gravity axis GA intersects axis X and is substantially perpendicular to axis A, and is skew relative to axis A. The gravity axis GA may lie in a common plane with axis Z. When the angle 9 is 0°, axis Z and the gravity axis GA may be coincident.

[0090] The angle 9 may be an angle greater than 0° and less than 90° measured relative to a gravity axis GA. In a particular example, the angle 9 may be an angle greater than 0°, less than 90°, and not equal to 45°, measured relative to a gravity axis GA. In an even further example, the angle 9 may be an angle within a range of 15° to 20°. In a still-further example, the angle 9 may be 17°. In another example, the angle 9 may be greater than 90°. While the angle 9 is shown on the right-hand side of the gravity axis GA in Figure 6, the secondhousing sub-assembly 266 can swivel to the left-hand side of the gravity axis GA by the same aforementioned angles. The aforementioned angles facilitate a compact and effective layout for the compressor 214, the valve assembly 48, and related piping.

[0091] The housing 258, and in particular to the first housing sub-assembly 64 and second housing sub-assembly 266, defines a flow path 292 for fluid F exiting the compressor 214 to flow relative to the resonator insert 254 and check valve 256. During normal operating conditions, fluid F exits the compressor 214, enters the valve assembly 248 via inlet 260, flows through a flow path 292 defined by the housing 258, and exits the valve assembly 248 via outlet 262. In these normal conditions, the check valve 256 is in an open position.

[0092] In some conditions, fluid F may tend to flow in an opposite direction, such as by entering the valve assembly 248 via outlet 262. The check valve 256 is configured to move to a closed position to prevent such flow from reaching the compressor 214. The check valve 256 is therefore configured to permit fluid F to flow from the inlet 260 to the outlet 262, and to prevent fluid F from flowing from the outlet 262 toward the inlet 260.

[0093] The flow path 292 is substantially straight within the first sub-assembly 250. Within the second sub-assembly 252, the flow path 292 exhibits a gradual curvature such that fluid F gradually turns from flowing along axis X to flowing along axis Z by the time the fluid F reaches the outlet 262. The outlet 262 is fluidly coupled to a location, other than the compressor 14, within the refrigerant circuit 12.

[0094] The check valve 256 is shown in an open position in Figure 10. The check valve 256 is configured substantially the same as check valve 32.

[0095] The resonator insert 254 is configured to attenuate noise. In particular, the resonator 54 is configured to attenuate noises of certain frequencies, which correspond to known noise frequencies associated with operation of the compressor 14.

[0096] The resonator insert 254 is adjacent the inlet 260. The resonator insert 254 could be provided in another location along the flow path 292, including in a location adjacent the outlet 262 or at a location between the inlet 260 and outlet 262. Further, while one resonator is shown, the valve assembly 248 could include more than one resonator. In that case, each of the plurality of resonators may be configured to attenuate noises of a unique frequency or set of frequencies. Providing the resonator insert 254 in the valve assembly 248 attenuates noise within the fluid F that has exited from the compressor 214, without requiring a modification to the design of the compressor 214 itself.

[0097] The resonator insert 254 may include one or more radially-extending grooves. The grooves may each be configured to attenuate noise of a different frequency. In particular, each groove may exhibit a unique depth, and the depth of each groove corresponds to the frequency of noise that the groove is configured to attenuate. As fluid F passes through the resonator insert 254, some of that fluid enters grooves, and the sound waves inside the grooves interfere with the incoming sound waves from the fluid flow, leading to destructive interference and a reduction in the overall amplitude of the sound waves. The resonator insert 254 may be referred to as a noise attenuator.

[0098] The resonator insert 254 may be configured to attenuate noise frequencies within a range from 3500 Hz to 9000 Hz. Such frequencies may experience at least a 16 dB reduction in acoustic noise. Such noise frequencies are known to occur in certain centrifugal refrigerant compressors. In particular, the range of noise frequencies targeted by the abovediscussed arrangement corresponds to the noises generated based on the speeds, capacity, etc., corresponding to centrifugal refrigerant compressors, as opposed to other types of compressors, such as those associated with turbochargers, which operate at significantly higher speeds, among other differences.

[0099] Figure 12 illustrates another example of the valve assembly 248 without the first sub-assembly 250. In this example, flange 286 is sandwiched between a segmented connector assembly 299 including a first segmented plate 295 and a second segmented plate 297. Each plate extends only partially about axis X. In other words, plates 295, 297 do not completely encircle axis X. When the plates 295, 297 are arranged together, however, the segmented connector assembly 299 does completely encircle the axis X. When assembled, one of the plates 295, 297 is on a first side of the flange 286, and the other of the plates 295, 297 is on an opposite side of the flange 86. Fasteners project through openings in the plates 295, 297 to hold the segmented connector assembly 297 relative to the compressor 14, and to selectively apply a compressive force to the flange 286. When the fasteners are loosened, the second subassembly 252 is rotatable about axis X.

[0100] Figures 13 and 14 illustrate another implementation of resonator insert 330 including like parts corresponding to resonator insert 30 preappended with a “3.” Resonator insert 330 is substantially similar to resonator insert 30, except where described below. Resonator insert 330 may be used in place of resonator insert 30 or resonator insert 254 in the foregoing valve assemblies.

[0101] With reference to Figures 13 and 14, the resonator insert 330 includes a plurality of circumferentially spaced-apart, chevron-shaped projections 301 incorporated into inner section 370- and arranged adjacent a downstream location of inner section 370, such that points of the projections 301 provide the downstream -most edge 303 and such that each projection 301, when viewed from a radially inner location (as in Figure 14), is defined by two walls 305, 307 that gradually converge and meet at downstream most edge 303. Radially inner and radially outer surfaces 309, 311 of each projection 301 may be axially spaced-apart from one another along an axial length of the projections 301. In some implementations, the radiallyinner and radially outer surfaces 309, 311 may gradually converge toward one another moving axially downstream.

[0102] The projections promote enhanced mixing of the flow of fluid F such that streams exiting the spaces between the outer section 372, inner section 370, and cone 376, which reduces downstream turbulence and flow separation compared to arrangements without such projections, thereby minimizing pressure losses across the resonator insert 330 and improving overall noise attenuation efficiency. Specifically, vortices created by the suspended geometry or grooves in the resonator insert 330 can be mitigated and thus reduce the acoustic level of the fluid F exiting the resonator insert 330. As shown in Figure 14, vortices may be formed in opposing directions at the projections 301 and cancel one another out.

[0103] It should be understood that directional terms such as “axial,” “radial,” “circumferential,” “leading,” and “trailing” are used above with reference to the normal operational attitude of the compressor 14, the valve assembly 22, and / or the resonator insert 30, 254, or 330. Further, these terms have been used herein for purposes of explanation, and should not be considered otherwise limiting. Terms such as “generally,” “substantially,” and “about” are not intended to be boundaryless terms, and should be interpreted consistent with the way one skilled in the art would interpret those terms.

[0104] Although the different examples have the specific components shown in the illustrations, embodiments of this disclosure are not limited to those particular combinations. It is possible to use some of the components or features from one of the examples in combination with features or components from another one of the examples. In addition, the various figures accompanying this disclosure are not necessarily to scale, and some features may be exaggerated or minimized to show certain details of a particular component or arrangement.

[0105] One of ordinary skill in this art would understand that the above-described embodiments are exemplary and non-limiting. That is, modifications of this disclosure would come within the scope of the claims. Accordingly, the following claims should be studied to determine their true scope and content.

Claims

CLAIMS1. A resonator insert for a valve assembly of a refrigerant compressor, comprising:an outer section centered about an axis, the outer section including a leading outer ring and a trailing outer ring axially interfaced with one another along the axis;an inner section arranged radially inward of the outer section and spaced radially inward from the outer section to define a first annular flow path therebetween;a central cone arranged radially inward of the inner section and spaced radially inward from the inner section to define a second annular flow path therebetween; anda plurality of annular grooves open to at least one of the first annular flow path and the second annular flow path, the annular grooves configured to attenuate acoustic noise in refrigerant flowing therethrough.

2. The resonator insert as recited in claim 1, wherein the inner section includes a leading inner ring and a trailing inner ring axially interfaced with one another along the axis.

3. The resonator insert as recited in claim 2, wherein the central cone includes a leading cone section and a trailing cone section axially interfaced with one another along the axis.

4. The resonator insert as recited in claim 1, wherein the plurality of annular grooves includes a first set of annular grooves formed in a radially inner surface of the outer section and open to the first annular flow path.

5. The resonator insert as recited in claim 4, wherein the plurality of annular grooves further includes a second set of annular grooves formed in a radially inner surface of the inner section and open to the second annular flow path.

6. The resonator insert as recited in claim 5, wherein individual grooves of the first set and the second set have different depths, each depth corresponding to a different target noise frequency in a range of 3500 Hz to 9000 Hz.

7. The resonator insert as recited in claim 1, further comprising at least one support plate having an outer diameter section, an inner diameter section, and a plurality of radially projecting lugs spacing the outer diameter section from the inner diameter section, wherein the outer diameter section is axially sandwiched between the leading outer ring and the trailing outer ring.

8. The resonator insert as recited in claim 7, wherein at least one annular groove of the plurality of annular grooves is partially defined by a recess in one of the leading outer ring and the trailing outer ring and partially defined by an axial wall of the outer diameter section of the support plate.

9. The resonator insert as recited in claim 1, further comprising a plurality of circumferentially spaced-apart chevron-shaped projections arranged on a downstream portion of the inner section.

10. The resonator insert as recited in claim 1 , wherein the leading outer ring and the trailing outer ring are press-fit together, and optionally laser welded at an axial interface therebetween.

11. A refrigerant compressor assembly comprising:a refrigerant compressor having an outlet centered about a compressor outlet axis; and a valve assembly mounted downstream of the outlet, the valve assembly including a housing defining an inlet fluidly coupled to the outlet and centered about an inlet axis aligned with the compressor outlet axis, an outlet downstream of the inlet, and a resonator insert.

12. The refrigerant compressor assembly as recited in claim 11, wherein the housing of the valve assembly has a fixed orientation relative to the refrigerant compressor.

13. The refrigerant compressor assembly as recited in claim 12, wherein the housing includes a spacer defining a bore open toward an exterior housing of the refrigerant compressor, the resonator insert is received within the bore, and further comprising a wave spring arranged in the bore and axially urging the resonator insert toward the exterior housing of the refrigerant compressor.

14. The refrigerant compressor assembly as recited in claim 11, further comprising a swivel joint permitting selective rotation of at least a portion of the housing about the inlet axis.

15. The refrigerant compressor assembly as recited in claim 11, wherein the housing comprises a first housing sub-assembly rigidly mounted to the refrigerant compressor and containing the resonator insert, and a second housing sub-assembly downstream of the first housing sub-assembly, and further comprising a swivel joint connecting the first housing subassembly to the second housing sub-assembly and permitting selective rotation of the second housing sub-assembly about the inlet axis.

16. The refrigerant compressor assembly as recited in claim 15, wherein the swivel joint comprises a flange of the first housing sub-assembly axially sandwiched between a flange of the second housing sub-assembly and a plate, and a plurality of fasteners configured to selectively clamp the flanges and plate together to prevent rotation or loosen to permit rotation.

17. The refrigerant compressor assembly as recited in claim 15, wherein the swivel joint comprises a segmented connector assembly axially sandwiching a flange of the second housing sub-assembly, the segmented connector assembly including at least two segmented plates that together fully encircle the inlet axis.

18. A method of assembling a resonator insert for a valve assembly downstream of a refrigerant compressor, the method comprising:providing a leading outer ring and a trailing outer ring;axially sliding the leading outer ring and the trailing outer ring relative to one another along an axis to form an outer section;positioning an inner section radially inward of the outer section such that the inner section is spaced radially inward from the outer section to define a first annular flow path therebetween; andpositioning a central cone radially inward of the inner section such that the central cone is spaced radially inward from the inner section to define a second annular flow path therebetween, wherein, when assembled, the resonator insert includes a plurality of annular grooves open to at least one of the first annular flow path and the second annular flow path for attenuating acoustic noise.

19. The method as recited in claim 18, further comprising axially sliding a leading inner ring and a trailing inner ring relative to one another to form the inner section prior to positioning the inner section radially inward of the outer section.

20. The method as recited in claim 18, further comprising laser welding at least one axial interface selected from the group consisting of an interface between the leading outer ring and the trailing outer ring, an interface between components of the inner section, and an interface between components of the central cone.

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