Shaft sealing components, compressors and refrigerant circulation systems

Abstract

The present disclosure provides a shaft sealing component, a compressor and a refrigerant circulation system. The shaft sealing component includes: a shaft sealing disc body, the center of the shaft sealing disc body has an axial hole, and the wall of the axial hole is provided with a shaft sealing structure; a shaft sealing positioning stop, which is coaxially and integrally arranged at one axial end of the shaft sealing disc body, and the shaft sealing positioning stop is provided with a first fluid channel connecting the radial inner side and the radial outer side of the shaft sealing positioning stop. The shaft sealing component provided by the present disclosure has the functions of shaft sealing, positioning and fluid discharge. The shaft sealing positioning stop is conducive to improving the matching accuracy between the shaft sealing component and the sealed rotating shaft, and can more effectively prevent fluid leakage. The first fluid channel is conducive to preventing the components adjacent to the shaft sealing component from retaining fluid, and is conducive to stabilizing the back pressure of related components, thereby helping to improve the stability of the bearing rotor system.

Description

Technical Field

[0001] The present disclosure relates to a compressor and a refrigerant circulation system, and in particular to a shaft sealing component, a compressor and a refrigerant circulation system. Background Art

[0002] Static pressure gas bearings have the advantages of ultra-high precision, ultra-low friction, ultra-low vibration, ultra-low noise, long life and no pollution. They are also suitable for high speed and high precision occasions and have broad application prospects in centrifugal compressors, especially miniaturized centrifugal compressors.

[0003] Static pressure gas bearings require an external gas source to supply gas and require the bearing working back pressure to be stable to prevent the bearing back pressure fluctuation from causing damage to the gas film and causing the bearing rotor system to become unstable and damaged. Summary of the Invention

[0004] An object of the present disclosure is to provide a shaft sealing component, a compressor, and a refrigerant circulation system.

[0005] A first aspect of the present disclosure provides a shaft sealing component, comprising:

[0006] A shaft sealing disc body, wherein the center of the shaft sealing disc body has a shaft hole, and a shaft sealing structure is provided on the hole wall of the shaft hole;

[0007] The shaft seal positioning stop is coaxially and integrally arranged at one axial end of the shaft seal disc body. The shaft seal positioning stop is provided with a first fluid channel communicating the radial inner side and the radial outer side of the shaft seal positioning stop.

[0008] In some embodiments, the shaft sealing structure includes a comb-teeth structure.

[0009] In some embodiments, the end of the shaft seal positioning stop away from the shaft seal disc body has a bearing positioning end surface for axially positioning the radial bearing.

[0010] In some embodiments, the first fluid channel comprises:

[0011] At least one through hole provided on the side wall of the shaft seal positioning stop; and / or

[0012] A groove is recessed from an end of the shaft seal positioning stop away from the shaft seal disc body to an end close to the shaft seal disc body.

[0013] In some embodiments, the shaft sealing component includes a plurality of the first fluid channels.

[0014] In some embodiments, the plurality of first fluid channels are evenly arranged along the circumference of the shaft seal positioning stop.

[0015] In some embodiments, the plurality of first fluid channels are uniformly arranged at an angular interval of 360° / (n+1) along the circumference of the shaft seal positioning stop, where n is the number of the plurality of first fluid channels.

[0016] In some embodiments, the shaft sealing component includes a shaft sealing connection hole and / or a shaft sealing positioning hole provided on the shaft sealing disc body.

[0017] In some embodiments, the diameter of the inner circumference of the shaft seal positioning stop is larger than the diameter of the shaft hole.

[0018] A second aspect of the present disclosure provides a compressor, comprising:

[0019] compressor rotor, including main shaft;

[0020] a radial bearing for carrying the main shaft; and

[0021] The shaft sealing component is the shaft sealing component described in the first aspect of the present disclosure, the main shaft is inserted into the shaft hole of the shaft sealing component, the shaft sealing structure of the shaft sealing component cooperates with the main shaft, and the first fluid channel of the shaft sealing component is connected to the gap between the radial bearing and the main shaft.

[0022] In some embodiments, the compressor further comprises a bearing support component, the bearing support component comprising:

[0023] A diffuser having a shaft seal mounting hole, a diffuser structure being provided at one axial end of the diffuser, and the shaft seal component being provided in the shaft seal mounting hole;

[0024] A bearing seat is integrally arranged at the other axial end of the diffuser. The bearing seat is provided with a bearing chamber that is coaxial with and communicates with the shaft seal mounting hole, and the radial bearing is arranged in the bearing chamber.

[0025] In some embodiments, the bearing carrier comprises a fluid inlet channel, wherein the fluid inlet channel connects the bearing chamber with the exterior of the bearing carrier.

[0026] In some embodiments, the bearing support component includes a fluid outflow channel, the fluid outflow channel connects the shaft seal mounting hole and the exterior of the bearing support component, and the first fluid channel connects to the fluid outflow channel.

[0027] In some embodiments, the end of the shaft seal positioning stop away from the shaft seal disc body has a bearing positioning end surface for axially positioning the radial bearing.

[0028] In some embodiments, the shaft seal mounting hole is a stepped hole, including a large diameter section located at one end close to the pressure diffuser structure and a small diameter section at one end away from the pressure diffuser structure, a stepped positioning surface is formed between the large diameter section and the small diameter section, the shaft seal disc body is located in the large diameter section, the shaft seal positioning stop is located in the small diameter section, and the end face of the shaft seal disc body close to the shaft seal positioning stop abuts against the step positioning surface.

[0029] In some embodiments, the radial bearing is a gas bearing.

[0030] A third aspect of the present disclosure provides a refrigerant circulation system, comprising the compressor described in the second aspect of the present disclosure.

[0031] The shaft sealing component provided by the present invention has the functions of shaft sealing, positioning and fluid discharge. The shaft sealing positioning stop is conducive to improving the matching accuracy between the shaft sealing component and the sealed rotating shaft, and can more effectively prevent fluid leakage. The first fluid channel is conducive to preventing fluid from being retained in components adjacent to the shaft sealing component, which is conducive to stabilizing the back pressure of related components, thereby helping to improve the stability of the bearing rotor system.

[0032] The compressor and refrigerant circulation system provided by the present disclosure have the same advantages as the shaft sealing component provided by the present disclosure.

[0033] Other features and advantages of the present disclosure will become apparent from the following detailed description of exemplary embodiments of the present disclosure with reference to the accompanying drawings. BRIEF DESCRIPTION OF THE DRAWINGS

[0034] The drawings described herein are used to provide a further understanding of the present disclosure and constitute a part of this application. The illustrative embodiments of the present disclosure and their descriptions are used to explain the present disclosure and do not constitute an improper limitation of the present disclosure. In the drawings:

[0035] Figure 1 Schematic diagram of the structure of a compressor according to an embodiment of the present disclosure.

[0036] Figure 2 Schematic diagram of the three-dimensional structure of a shaft sealing component according to an embodiment of the present disclosure.

[0037] Figure 3 for Figure 2 Schematic diagram of the side structure.

[0038] Figure 4 for Figure 2 Schematic diagram of the cross-sectional structure.

[0039] Figure 5 This is a schematic diagram of the partial structure of a compressor according to an embodiment of the present disclosure.

[0040] Figure 6Schematic diagram of the bearing structure of a compressor according to an embodiment of the present disclosure. DETAILED DESCRIPTION

[0041] The following will be combined with the drawings in the embodiments of the present disclosure to clearly and completely describe the technical solutions in the embodiments of the present disclosure. Obviously, the described embodiments are only part of the embodiments of the present disclosure, rather than all the embodiments. The following description of at least one exemplary embodiment is actually only illustrative and is in no way intended to limit the present disclosure and its application or use. Based on the embodiments in the present disclosure, all other embodiments obtained by ordinary technicians in this field without making creative work are within the scope of protection of the present disclosure.

[0042] Unless otherwise specifically stated, the relative arrangement of the parts and steps, the numerical expressions and the numerical values ​​set forth in these embodiments do not limit the scope of the present disclosure. At the same time, it should be understood that, for ease of description, the sizes of the various parts shown in the drawings are not drawn according to actual proportional relationships. The techniques, methods and equipment known to those of ordinary skill in the relevant art may not be discussed in detail, but where appropriate, the techniques, methods and equipment should be considered as part of the authorization specification. In all examples shown and discussed herein, any specific values ​​should be interpreted as being merely exemplary and not as limitations. Therefore, other examples of the exemplary embodiments may have different values. It should be noted that similar numbers and letters represent similar items in the following figures, and therefore, once an item is defined in one figure, it does not need to be further discussed in subsequent figures.

[0043] In the description of the present disclosure, it should be understood that the use of words such as "first" and "second" to limit components is only for the convenience of distinguishing the corresponding components. Unless otherwise stated, the above words have no special meaning and therefore cannot be understood as limiting the scope of protection of the present disclosure.

[0044] In the description of the present disclosure, it should be understood that directional words such as "front, back, up, down, left, right", "horizontal, vertical, vertical, horizontal" and "top, bottom", etc., are only for the convenience of describing the present disclosure and simplifying the description. Unless otherwise specified, these directional words do not indicate or imply that the device or element referred to must have a specific orientation or be constructed and operated in a specific orientation, and therefore cannot be understood as limiting the scope of protection of the present disclosure; the directional words "inside and outside" refer to the inside and outside relative to the outline of each component itself.

[0045] like Figures 1 to 5As shown, the present embodiment provides a shaft seal component 70. The shaft seal component 70 includes a shaft seal disc 71 and a shaft seal locating stop 72. The shaft seal disc 71 has an axial hole at its center, and a shaft seal structure is provided on the wall of the axial hole. The shaft seal locating stop 72 is coaxially and integrally disposed at one axial end of the shaft seal disc 71. The shaft seal locating stop 72 is provided with a first fluid passage connecting the radially inner and radially outer sides of the shaft seal locating stop 72.

[0046] The shaft seal component 70 of the embodiment of the present disclosure has the functions of shaft sealing, positioning and fluid discharge. The shaft seal positioning stop 72 is conducive to improving the matching accuracy between the shaft seal component 70 and the sealed rotating shaft (such as the main shaft 21 of the compressor), and can more effectively prevent fluid leakage. The first fluid channel is conducive to preventing the components (such as radial bearings) that match the shaft seal component 70 from retaining fluid, which is conducive to stabilizing the back pressure of related components, thereby helping to improve the stability of the bearing rotor system.

[0047] like Figures 1 to 5 As shown, in some embodiments, the shaft sealing structure includes a comb-tooth structure 711. The comb-tooth structure 711 is more suitable for sealing gas, suitable for use in compressors, and can effectively prevent pressurized gas from leaking.

[0048] like Figures 1 to 5 As shown, in some embodiments, the end of the shaft seal positioning stop 72 away from the shaft seal disc 71 has a bearing positioning end surface 721 for axially positioning the radial bearing. Bearing positioning end surface 721 enables the shaft seal component 70 to also perform the axial positioning function of the radial bearing, which helps simplify the structure of the device and shorten the length of the rotor of the device.

[0049] The first fluid channel can have various structural forms, for example, Figures 1 to 5 As shown, in some embodiments, the first fluid passage includes a groove 722 that extends from an end distal to the shaft seal disc body 71 toward an end proximal to the shaft seal disc body 71. In embodiments not shown, the first fluid passage may include at least one through-hole provided on a sidewall of the shaft seal positioning stop 72. Alternatively, both a groove and a through-hole may be provided as the first fluid passage.

[0050] like Figure 3 and Figure 4 As shown, in some embodiments, the shaft sealing component 70 includes multiple first fluid channels. Providing multiple first fluid channels facilitates rapid and uniform discharge of fluid near related components, such as radial bearings, and helps prevent fluid from stagnating near related components.

[0051] like Figure 3 and Figure 4As shown, in some embodiments, multiple first fluid channels are evenly arranged along the circumference of the shaft seal positioning stop 72. This arrangement facilitates rapid and even discharge of fluid near related components such as radial bearings, and helps prevent fluid from stagnating near related components.

[0052] In some embodiments, the plurality of first fluid channels are evenly arranged at an angle interval of 360° / n+1 along the circumference of the shaft seal positioning stop 72, where n is the number of the plurality of first fluid channels. The number n can be 2, 3, 4, 5, 6 or more. Figure 3 and Figure 4 In the illustrated embodiment, n = 5. The number and distribution of the first fluid channels advantageously correspond to the number and distribution of the fluid outlet channels 64 provided on the bearing support member 60. This arrangement facilitates forming fluid outlet passages in conjunction with related components, such as the bearing support member 60 described below, and also provides space for the provision of fluid inlet channels in related components.

[0053] The shaft seal component 70 includes a shaft seal connection hole 712 and / or a shaft seal positioning hole 713 disposed on the shaft seal disc 71. The shaft seal positioning hole 713 accurately determines the connection position between the shaft seal component 70 and related components, such as the bearing support component 60 described below, facilitating rapid and accurate communication between the first fluid passage and a corresponding fluid passage (e.g., the fluid outflow passage 64 of the bearing support component 60). The shaft seal connection hole 712 facilitates detachable connection with related components via threaded connectors.

[0054] like Figures 1 to 5 As shown, in some embodiments, the diameter of the inner circumference of the shaft seal positioning stop 72 is larger than the diameter of the shaft hole of the shaft seal disc body 71. This arrangement facilitates communication between the first fluid passages and the gap between the radial bearing and the main shaft 21, and facilitates uniform distribution of fluid among the first fluid passages.

[0055] The disclosed embodiment also provides a compressor, comprising a compressor rotor 20, a radial bearing and a shaft sealing component 70. The compressor rotor 20 comprises a main shaft 21. The radial bearing is used to support the main shaft 21. The shaft sealing component 70 is the aforementioned shaft sealing component 70. The main shaft 21 is inserted into the shaft hole of the shaft sealing component 70. The shaft sealing structure of the shaft sealing component 70 cooperates with the main shaft 21. The first fluid channel is connected to the gap between the radial bearing and the main shaft 21. This arrangement is conducive to preventing the fluid from being retained near the radial bearing, and is conducive to maintaining the back pressure of the radial bearing stable, thereby ensuring the stable operation of the compressor.

[0056] like Figure 1 and Figure 5 、 Figure 6As shown, in some embodiments, the compressor further includes a bearing support component 60, which includes a diffuser and a bearing seat. The diffuser has a shaft seal mounting hole 67, and one axial end of the diffuser ( Figure 1 、 Figure 5 and Figure 6 The right end) is provided with a diffuser structure. The diffuser structure can be, for example, a diffuser surface or a diffuser blade. The shaft seal component 70 is arranged in the shaft seal mounting hole 67. The bearing seat is integrally arranged at the other axial end of the diffuser. The bearing seat is provided with a bearing chamber 62 which is coaxial with and connected to the shaft seal mounting hole 67. The radial bearing is arranged in the bearing chamber 62. The bearing support component 60 simultaneously assumes the function of installing the diffuser, the bearing seat and the shaft seal component. The shaft seal component 70 cooperates to install the radial bearing in the bearing support component 60, which is beneficial for the compressor to shorten the compressor rotor length, reduce the compressor rotor weight, and increase the critical speed of the compressor rotor.

[0057] like Figure 1 and Figure 5 、 Figure 6 As shown, in some embodiments, the bearing support component 60 includes a fluid inlet channel 63 that connects the bearing chamber 62 with the exterior of the bearing support component 60. The fluid inlet channel 63 can supply the radial bearing with the fluid required to support the main shaft 21, such as a suspension gas. The fluid inlet channel 63 can be, for example, a channel disposed within the bearing support component 60.

[0058] like Figure 1 and Figure 5 、 Figure 6 As shown, in some embodiments, the bearing support component 60 includes a fluid outflow channel 64 that connects the shaft seal mounting hole 67 with the exterior of the bearing support component 60, and the first fluid channel is connected to the fluid outflow channel 64. This arrangement helps prevent fluid from stagnating near the radial bearing, helps maintain a stable back pressure in the radial bearing, and thus promotes stable operation of the compressor.

[0059] like Figures 1 to 5 As shown, the first fluid passage of the shaft seal component 70 is a plurality of grooves 722 provided on the shaft seal positioning stop 72. The number of grooves 722 is not limited and can be, for example, 3-12. The fluid outflow passages 64 of the bearing support structure 60 have the same number of grooves 722. The fluid outflow passages 64 are channels provided within the bearing support structure 60.

[0060] like Figure 1 and Figure 5As shown, in some embodiments, the end of the shaft seal positioning stop 72, distal from the shaft seal disc 71, has a bearing positioning end surface 721 for axially positioning the radial bearing. This arrangement enables the shaft seal component 70 to simultaneously assume the axial positioning function of the radial bearing, thereby shortening the length of the compressor rotor, reducing the weight of the compressor rotor and the entire compressor, and simplifying the compressor structure. The bearing positioning end surface 721 can, for example, have a clearance fit with the corresponding end surface of the radial bearing.

[0061] like Figure 1 and Figure 5 、 Figure 6 As shown, in some embodiments, the shaft seal mounting hole 67 is a stepped hole, comprising a large-diameter section located at one end near the diffuser structure and a small-diameter section located at one end away from the diffuser structure. The shaft seal disc 71 is installed within the large-diameter section and cooperates with the large-diameter section, while the shaft seal positioning stop 72 is installed within the small-diameter section and cooperates with the small-diameter section. A stepped positioning surface 65 is formed between the large-diameter and small-diameter sections, and the end face 714 of the shaft seal disc 71, which is adjacent to the positioning ring, has a clearance fit with the stepped positioning surface 65. This arrangement facilitates the axial positioning of the bearing assembly 70. Furthermore, because the shaft seal assembly assumes the axial positioning function of the radial bearing, it also facilitates the axial positioning of the radial bearing.

[0062] like Figure 6 As shown, the fluid inlet of the fluid inlet channel 63 is arranged on the end face of the other axial end of the diffuser. This arrangement facilitates the introduction of fluid into the fluid inlet channel 63 from the compressor housing.

[0063] The bearing support member 60 includes a plurality of fluid outflow channels 64. The plurality of fluid outflow channels 64 are evenly distributed along the circumference of the bearing support member 60. The plurality of fluid outflow channels 64 are evenly distributed along the circumference of the bearing support member 60 at intervals of 360° / m+1, where m is the number of the plurality of fluid outflow channels 64. The number m can be 2, 3, 4, 5, 6 or more. Figures 1 to 6 In the illustrated embodiment, m = 5. The number and distribution of the first fluid channels correspond to the number and distribution of the fluid outlet channels 64 provided on the bearing support component 60. Fluid inlet channels 63 are provided in locations on the circumference of the bearing support component 60 where fluid outlet channels 64 are not provided. This arrangement ensures that all fluid channels in the bearing support component 60 are roughly evenly distributed, facilitating fluid channel processing and accurate positioning during assembly of the bearing support component 60.

[0064] like Figure 1 、 Figure 5 and Figure 6 As shown, the fluid outlet of the fluid outflow channel 64 is provided on the end surface of the second axial end of the diffuser and / or the outer peripheral surface of the bearing seat.

[0065] The bearing support component 60 includes a bearing positioning structure at the other axial end for axially positioning the radial bearing. This bearing positioning structure includes an annular groove 66. Annular groove 66 is provided on the sidewall of the bearing chamber 62. A retaining ring 81 is mounted within annular groove 66. The inner diameter of retaining ring 81 is smaller than the diameter of the bearing chamber 62.

[0066] The bearing support component 60 also includes a support locating notch 68 at the other axial end of the diffuser, a diffuser locating hole 69, and a diffuser mounting hole. The support locating notch 68 engages the inner wall of the right end of the motor barrel 11 of the compressor casing 10 to determine the radial and axial position of the bearing support component 60. The bearing support component 60 is circumferentially positioned between the casing 10 and the locating member, which passes through the diffuser locating hole 69. The bearing support component 60 is securely connected to the casing 10 by a threaded connector that passes through the diffuser mounting hole.

[0067] The disclosed embodiment further provides a refrigerant circulation system, comprising the aforementioned compressor.

[0068] The compressor and the refrigerant circulation system according to the embodiment of the present disclosure have the corresponding advantages of the shaft sealing component 70 according to the embodiment of the present disclosure.

[0069] The following is further combined Figures 1 to 6 Some embodiments of the present disclosure are described in more detail.

[0070] like Figure 1 As shown, the compressor mainly includes a housing 10 , a compressor rotor 20 , a motor stator 30 , a bearing assembly, a first-stage diffuser 50 , a bearing support component 60 and a shaft seal component 70 .

[0071] The housing 10 includes a motor barrel 11 and a first-stage volute 12 and a second-stage volute 13 respectively connected to the left and right ends of the motor barrel 11. The left end of the motor barrel 11 has an end wall, and the right end is open.

[0072] The first-stage diffuser 50, the bearing support component 60, and the shaft seal component 70 installed in the shaft seal mounting hole 67 of the bearing support component 60 are respectively arranged at the left and right ends of the motor barrel 11, and divide the internal space of the shell 10 into a motor accommodating chamber 14 located in the middle of the shell 10, a first-stage compression chamber 15 located at the left end of the shell 10, and a second-stage compression chamber 16 located at the right end of the shell 10.

[0073] The compressor rotor 20 mainly includes a main shaft 21 , a first-stage impeller 22 , a second-stage impeller 23 and a thrust plate component 24 .

[0074] The motor stator 30 is fixed to the inner wall of the motor barrel 11 and has a rotor mounting hole. A spiral groove can be provided on the inner wall of the motor barrel 11 for passing a cooling fluid for cooling the motor stator 30.

[0075] The main shaft 21 is disposed within the motor stator 30 and extends through the rotor mounting hole of the motor stator 30. A permanent magnet for generating a magnetic field is located in the middle of the main shaft 21. The left and right ends of the permanent magnet are provided with a first end shaft segment and a second end shaft segment, respectively. Therefore, in this embodiment, the main shaft 21 also serves as the motor rotor of the compressor motor. The motor stator 30 and the main shaft 21 constitute the compressor motor. When the windings of the motor stator 30 are energized, the main shaft 21 rotates, thereby driving the entire compressor rotor.

[0076] The first-stage impeller 22 and the second-stage impeller 23 are fixedly connected to the left and right ends of the main shaft 21. The first-stage impeller 22 and the diffuser structure of the first-stage diffuser 50 are located in the first-stage compression chamber 15. The second-stage impeller 23 and the diffuser structure on the bearing support component 60 are located in the second-stage compression chamber 16.

[0077] The thrust plate assembly 24 is positioned near the primary impeller 22 and comprises a thrust plate and an integral mounting sleeve. The thrust plate assembly 24 is securely mounted on the outer circumference of the first end section of the main shaft 21. The mounting sleeve is positioned between the primary impeller 22 and the thrust plate. The thrust plate assembly 24 can be shrink-fitted onto the first end section of the main shaft 21.

[0078] The bearing assembly includes a thrust bearing assembly 41 , a first radial bearing 42 and a second radial bearing.

[0079] like Figure 1 As shown, the thrust bearing assembly 41 includes a first thrust bearing 411, a second thrust bearing 412 and a thrust bearing locating ring 413. Figures 1 to 6 In the illustrated embodiment, the first thrust bearing 411 , the second thrust bearing 412 , the first radial bearing 42 and the second radial bearing are all hydrostatic gas bearings.

[0080] The left end of the first-stage diffuser 50 includes a diffuser structure, such as a diffuser surface or diffuser blades. A shaft hole is centrally located within the first-stage diffuser 50, within which a shaft seal structure, such as a comb structure, is located. The mounting sleeve of the thrust plate assembly 24 is located within the shaft hole of the first-stage diffuser 50 and engages with the shaft seal structure therein. The radially outer end of the first-stage diffuser 50 is sealingly secured to the end wall of the motor barrel 11, thereby isolating the first-stage compression chamber 15 at the left end of the housing 10 from the motor housing 14 in the center of the housing 10.

[0081] like Figure 1As shown, the right end of the first-stage diffuser 50 has a diffuser positioning spigot, and the left end of the end wall of the motor barrel 11 has a diffuser mounting opening. The diffuser positioning spigot of the first-stage diffuser 50 is installed in the diffuser mounting opening and cooperates with the diffuser mounting opening, thereby achieving axial and radial positioning of the first-stage diffuser 50. The interior of the diffuser positioning spigot of the first-stage diffuser 50 and the bottom wall of the diffuser mounting opening of the motor barrel 11 form a thrust bearing assembly mounting chamber.

[0082] The thrust bearing assembly 41 is disposed within the thrust bearing assembly mounting chamber. The left and right end surfaces of the thrust plate of the thrust plate component 24 mate with the first thrust surface of the first thrust bearing 411 and the second thrust surface of the second thrust bearing 412, respectively. Thus, the thrust plate, the first thrust bearing 411, and the second thrust bearing 412 collectively define the axial position of the compressor rotor 21.

[0083] The radially outer end of the first thrust surface of the first thrust bearing 411 is further provided with a first positioning surface, and the radially outer end of the second thrust surface of the second thrust bearing 412 is further provided with a second positioning surface. The left and right end surfaces of the thrust bearing positioning ring 413 are clearance-matched with the first and second positioning surfaces, respectively. Thus, the distance between the left and right end surfaces of the thrust bearing positioning ring 413 defines the distance between the first and second thrust surfaces, and thus defines the sum of the gaps between the thrust disc and the first thrust surface, and the gaps between the thrust disc and the second thrust surface. The thrust bearing positioning ring 413 is fixedly connected to the second thrust bearing 42 and the end wall of the motor barrel 11 via threaded connectors.

[0084] A second fluid passage is provided on the thrust bearing locating ring 413 for connecting the radial inner side and the radial outer side thereof. The second fluid passage helps to ensure the back pressure of the thrust bearing assembly is stable, thereby facilitating the stable operation of the compressor.

[0085] An end wall bearing chamber is provided in the radially central portion of the end wall of the motor barrel 10, and a first radial bearing 42 is disposed within the end wall bearing chamber. The left end of the first radial bearing 42 has a clearance fit with the side of the second thrust bearing 412 that is distal to the second thrust surface. The right end of the first radial bearing 42 has a clearance fit with a retaining ring 82 mounted within a groove in the end wall bearing chamber. As a result, the axial position of the first radial bearing 42 is determined by both the second thrust bearing 412 and the retaining ring 82.

[0086] The bearing support member 60 integrates the diffuser ( Figure 1 In the embodiment shown, the second radial bearing 43 is mounted in the bearing chamber 62 of the bearing support member 60. The second radial bearing 43 is sleeved on the outer periphery of the second end section of the main shaft 21.

[0087] The shaft seal component 70 is fixedly mounted within the shaft seal mounting hole 67 of the bearing support component 60. As previously mentioned, the bearing support component 60 is fixedly mounted to the right end of the motor housing 11. The bearing support component 60 and the motor housing 11 are sealed. After the shaft seal component 70 is installed within the bearing support component 60 and fitted over the main shaft 21, a seal is formed between the shaft seal structure within the shaft hole of the bearing component 70 and the second end section of the main shaft 21. The radial outer end of the bearing component 70 is sealedly connected to the radial inner end of the bearing support component 60. As a result, the shaft seal component 70 and the bearing support component 60 isolate the second compression chamber 16 of the housing 10 from the motor accommodating chamber 14.

[0088] After the bearing carrier 60, shaft seal 70, and second radial bearing 43 are assembled, the bearing positioning end face 721 of the shaft seal 70 forms a clearance fit with the right end face of the second radial bearing 43, while the left end of the second radial bearing 43 forms a clearance fit with the retaining ring 81. As a result, the axial position of the second radial bearing 43 is determined by the shaft seal 70 and the retaining ring 81. Simultaneously, the first fluid passages of the shaft seal 70 communicate with the corresponding fluid outflow passages 64 of the bearing carrier 60.

[0089] like Figure 1 As shown, the motor housing 11 is provided with a first gas inlet channel 17 for supplying suspended gas to the first radial bearing 42 and the second radial bearing 43. The fluid inlet channel 63 of the bearing support component 60 communicates with the first gas inlet channel 17 via a fluid inlet provided on the diffuser end face thereof. This allows the suspended gas to enter the bearing chamber of the bearing support component 60, pass through the porous medium of the second radial bearing 43, and enter the gap between the second radial bearing 43 and the second end section of the main shaft 21. The suspended gas then enters the inner cavity of the retaining ring 72 of the shaft seal component 70. The suspended gas then enters the fluid outlet channel 64 of the corresponding bearing support component 60 through each first fluid channel, enters the motor accommodating chamber 14, and finally flows out of the housing 10 through an outlet (not shown) provided on the motor housing 11.

[0090] In this embodiment, the housing 10 is also provided with a second gas inlet channel for supplying suspended gas to the thrust bearing assembly 41. This second gas inlet channel is independent of the first gas inlet channel. Suspended gas in the second gas inlet channel is supplied to the interiors of the first thrust bearing 411 and the second thrust bearing 412, respectively. Suspended gas passes through the porous media of the first thrust bearing 411 and the porous media of the second thrust bearing 412, respectively, into the gaps between the first thrust surface and the thrust disc, and between the second thrust surface and the thrust disc. The gas then flows through the second fluid channel on the thrust bearing locating ring 413 to the motor accommodating chamber 14. This second fluid channel on the thrust bearing locating ring 413 facilitates the timely removal of suspended gas, ensuring stable back pressure within the thrust bearing assembly 41.

[0091] In some embodiments not shown, the second gas inlet channel may be connected to the first gas inlet channel, so that suspension gas may be supplied to each branch channel and each gas bearing corresponding to the branch channel through the same housing air inlet and the same main channel.

[0092] like Figure 5 As shown in the figure, the arrows indicate the flow path of the suspended gas supplied to the second radial bearing 43. The suspended gas enters the fluid inlet channel 63 and bearing chamber 62 of the bearing support structure 60 from the first gas inlet channel 17 at the bottom of the motor housing 11, and is then supplied to the second radial bearing 43. The suspended gas enters the interior of the second radial bearing 43, passes through the porous medium throttling of the second radial bearing 43, and enters the gap between the second radial bearing 43 and the main shaft 21. The suspended gas forms an air film within the gap between the second radial bearing 43 and the main shaft 21, causing the main shaft 21 to float. The suspended gas is then discharged from both ends of the gap. Suspended gas discharged from the left end enters the motor accommodating cavity 14 and is then discharged from the housing 10 along with the cooling gas used to cool the motor. Suspended gas discharged from the right end passes through the first fluid channels of the shaft seal 70 and enters the fluid outlet channels 64 of the bearing support structure 60. The suspended gas then enters the motor accommodating cavity 14 and is discharged from the housing 10 along with the cooling gas used to cool the motor.

[0093] Static gas bearings require very high precision, with bearing clearances typically below 10μm. The sealing clearance of the shaft seal component 70 should also be as small as possible while ensuring relative rotation. For example, the sealing clearance can be as low as 0.02mm. Such a small sealing clearance places high demands on the coaxiality between the shaft seal structure and the main shaft 21. The shaft seal locating stop 72 allows the shaft seal component 70 to be positioned relative to compressor components, such as the bearing support component 70 and the housing 10, ensuring coaxiality between the shaft seal structure and the main shaft 21.

[0094] The shaft seal structure is set as a comb tooth structure, which cooperates with the main shaft 21 to prevent the exhaust gas of the compressor's secondary impeller 23 from entering the bearing chamber 62 of the bearing support component 60, which is beneficial to reducing the leakage loss of the compressor and improving the energy efficiency of the compressor. It is also beneficial to prevent the back pressure of the bearing chamber 62 from increasing due to excessive leakage.

[0095] The back pressure in bearing chamber 62 affects the distribution of air film pressure between the second radial bearing 43 and the main shaft 21, thereby affecting bearing stiffness and damping. These factors, in turn, influence rotor dynamic stability. Furthermore, fluctuations in bearing back pressure can also cause bearing vortex motion. Therefore, maintaining stable back pressure during use of a static gas bearing is crucial for ensuring the stability of the bearing-rotor system. The first fluid passageway of the shaft seal 70 and the fluid outflow passageway 64 of the bearing support structure 60 prevent gas exhausted from the left end from being retained within the shaft seal 70 and the bearing support structure 60, effectively preventing unstable back pressure in the second radial bearing 43.

[0096] The bearing positioning end face 721 of the shaft seal component 70 is loosely matched with the right end face of the second radial bearing 43 , and together with the snap ring 81 limits the axial position of the second radial bearing 43 , thereby preventing the second radial bearing 43 from moving left and right and causing bearing instability.

[0097] It can be seen that the shaft seal component 70 of the embodiment of the present disclosure is beneficial to reducing leakage losses while ensuring the stability of the working back pressure of the radial bearing adjacent to the shaft seal component 70, thereby improving the energy efficiency of the compressor and the stability of the bearing rotor system.

[0098] The bearing support component 60 of the embodiment of the present disclosure designs the diffuser and the bearing seat into one part, and provides a shaft seal mounting hole, integrating the functions of the diffuser, the bearing seat and the shaft seal mounting seat, which helps to reduce the number of parts and improve assembly efficiency. At the same time, it can also reduce the length of the compressor rotor and improve the stability of the bearing rotor system.

[0099] Since the bearing support component 60 has a fluid inflow channel 63 and a fluid outflow channel 64, it is beneficial to ensure the normal operation of the second radial bearing 43 and the stability of the working back pressure, which is beneficial to improving the stability of the bearing rotor system. At the same time, it also serves as a diffuser, reduces the number of parts, reduces the length of the compressor rotor, and improves the stability of the bearing rotor system.

[0100] The bearing support component 60 is dually positioned using a support component positioning stop 68 and a diffuser positioning hole 69 in conjunction with a positioning pin. The support component positioning stop 68, along with the right end surface and inner wall of the motor barrel 11, ensures the coaxiality of the bearing support component 60 and its bearing chamber 62 with the main shaft 21, thereby ensuring the coaxiality of the second radial bearing 43 with the main shaft 21 after assembly. The pin, in conjunction with the diffuser positioning hole 69, precisely positions the bearing support component 60 in the circumferential direction. Consequently, this bearing support component 60 improves assembly efficiency and accuracy.

[0101] Since the bearing clearance of hydrostatic gas bearings is generally a few microns to tens of microns, rotating machinery supported by hydrostatic gas bearings places extremely high demands on the coaxiality of the two radial bearings. If the coaxiality is poor, the bearing performance will be reduced, and in severe cases, the rotor will not be able to float. Therefore, the bearing support structure 60 of the embodiment of the present disclosure and the bearing component 70 matched therewith are both suitable for compressors supported by hydrostatic gas bearings. Of course, although the shaft seal component 70 of the embodiment of the present disclosure is suitable for compressors using gas bearings, such as centrifugal compressors, it does not exclude the use of the shaft seal component 70 of the embodiment of the present disclosure in other rotating systems.

[0102] Finally, it should be noted that the above embodiments are only used to illustrate the technical solutions of the present disclosure and are not intended to limit them. Although the present disclosure has been described in detail with reference to preferred embodiments, ordinary technicians in the relevant field should understand that the specific implementation methods of the present disclosure can still be modified or some technical features can be replaced by equivalents, which should all be included in the scope of the technical solutions claimed for protection in the present disclosure.

Claims

1. A compressor, characterized in that: include: A compressor rotor (20), including a main shaft (21); a radial bearing for carrying the main shaft (21), wherein the radial bearing is a gas bearing; and A shaft sealing component (70) comprises a shaft sealing disc body (71) and a shaft sealing positioning stop (72), wherein the shaft sealing disc body (71) has an axial hole at its center, a shaft sealing structure is provided on the hole wall of the axial hole, the shaft sealing positioning stop (72) is coaxially and integrally arranged at one axial end of the shaft sealing disc body (71), the shaft sealing positioning stop (72) is provided with a first fluid channel communicating with the radial inner side and the radial outer side of the shaft sealing positioning stop (72), the main shaft (21) is passed through the axial hole of the shaft sealing component (70), the shaft sealing structure of the shaft sealing component (70) cooperates with the main shaft (21), and the first fluid channel of the shaft sealing component (70) is communicated with the gap between the radial bearing and the main shaft (21) for discharging suspended gas to prevent the radial bearing from retaining suspended gas.

2. The compressor according to claim 1, characterized in that The shaft sealing structure includes a comb tooth structure (711).

3. The compressor according to claim 1, characterized in that One end of the shaft seal positioning stop (72) away from the shaft seal disc body (71) has a bearing positioning end surface (721) for axially positioning the radial bearing.

4. The compressor according to claim 1, characterized in that The first fluid channel comprises: At least one through hole provided on the side wall of the shaft seal positioning stop (72); and / or A groove (722) is recessed from an end of the shaft seal positioning stop (72) away from the shaft seal disc body (71) to an end close to the shaft seal disc body (71).

5. The compressor according to claim 1, characterized in that The shaft seal component (70) comprises a plurality of the first fluid channels, and the plurality of the first fluid channels are evenly arranged along the circumference of the shaft seal positioning stop (72).

6. The compressor according to claim 5, characterized in that The plurality of first fluid channels are evenly arranged along the circumference of the shaft seal positioning stop (72) at an angular interval of 360° / (n+1), wherein n is the number of the plurality of first fluid channels.

7. The compressor according to claim 1, characterized in that The shaft seal component (70) comprises a shaft seal connection hole (712) and / or a shaft seal positioning hole (713) provided on the shaft seal disc body (71).

8. The compressor according to claim 1, characterized in that The diameter of the inner circumference of the shaft seal positioning stop (72) is larger than the diameter of the shaft hole.

9. The compressor according to any one of claims 1 to 8, characterized in that The compressor further comprises a bearing bearing component (60), wherein the bearing bearing component (60) comprises: A diffuser having a shaft seal mounting hole (67), a diffuser structure being provided at one axial end of the diffuser, and the shaft seal component (70) being provided in the shaft seal mounting hole (67); A bearing seat is integrally arranged at the other axial end of the diffuser, and the bearing seat is provided with a bearing chamber (62) coaxial with and in communication with the shaft seal mounting hole (67), and the radial bearing is arranged in the bearing chamber (62).

10. The compressor according to claim 9, characterized in that The bearing support component (60) comprises a fluid inlet channel (63), wherein the fluid inlet channel (63) communicates with the bearing chamber (62) and the outside of the bearing support component (60).

11. The compressor according to claim 9, characterized in that The bearing supporting component (60) includes a fluid outflow channel (64), the fluid outflow channel (64) is connected to the shaft seal mounting hole (67) and the outside of the bearing supporting component (60), and the first fluid channel is connected to the fluid outflow channel (64).

12. The compressor according to claim 9, characterized in that One end of the shaft seal positioning stop (72) away from the shaft seal disc body (71) has a bearing positioning end surface (721) for axially positioning the radial bearing.

13. The compressor according to claim 9, characterized in that The shaft seal mounting hole (67) is a stepped hole, comprising a large diameter section located at one end close to the pressure diffuser structure and a small diameter section at one end away from the pressure diffuser structure, a stepped positioning surface (65) is formed between the large diameter section and the small diameter section, the shaft seal disc body (71) is located in the large diameter section, the shaft seal positioning stop (72) is located in the small diameter section, and an end surface (714) of the shaft seal disc body (71) close to the shaft seal positioning stop (72) abuts against the stepped positioning surface (65).

14. A refrigerant circulation system, characterized in that: A compressor comprising the compressor according to any one of claims 1 to 13.

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