Compressor for vehicle and vehicle

Abstract

A compressor (100) for a vehicle (200) and a vehicle (200). The compressor (100) comprises: a housing (10) having a first accommodating cavity (101); and a compression mechanism (20) comprising a cylinder assembly (30) and two bearings (40). The bearings (40) are mounted on the housing (10), and the cylinder assembly (30) is located in the first accommodating cavity (101) and sandwiched between the two bearings (40). The cylinder assembly (30) has a suction cavity (301) and a discharge cavity (302). Two axial side surfaces of each bearing (40) are a first side (401) facing away from the cylinder assembly (30) and a second side (402) facing toward the cylinder assembly (30), respectively. A sealing ring (50) is abutted between the first side (401) and the housing (10), and the sealing ring (50) divides the first side (401) into a first area (401a) and a second area (401b). The first area (401a) is in communication with the discharge cavity (302), and the second area (401b) is isolated from the discharge cavity (302) of the cylinder assembly (30).

Description

Compressor for vehicle and vehicle

[0001] Cross-reference to related applications

[0002] The present application claims priority to the Chinese patent application No. 202411377692.1 filed on September 29, 2024 by Anqing Wiling Automobile Parts Co., Ltd., Anhui Wiling Automobile Parts Co., Ltd., and Guangdong Wiling Automobile Parts Co., Ltd., the entire contents of which are hereby incorporated by reference into the present application. TECHNICAL FIELD

[0003] The present application relates to the technical field of compressors, and more particularly, to a compressor for vehicle and vehicle. BACKGROUND

[0004] In the working process of the compressor, the bearing of the compression mechanism is prone to large deformation, which leads to a smaller gap between the bearing and the piston and easy contact and wear. In some related technologies, the deformation is resisted by increasing the thickness of the bearing, which results in high cost and heavy weight of the bearing, and still cannot solve the bearing deformation problem for some refrigerants with high exhaust pressure, such as carbon dioxide. In another related technology, the wear problem is solved by reducing the axial height of the piston and the vane, but it will cause increased leakage and reduced compressor efficiency. SUMMARY

[0005] The present application aims to at least solve one of the technical problems existing in the prior art. To this end, one object of the present application is to provide a compressor for vehicle, which effectively improves the bearing deformation problem.

[0006] The present application also provides a vehicle with the above-mentioned compressor.

[0007] The compressor for vehicle according to the embodiments of the present application comprises a housing having a first accommodating cavity; a compression mechanism comprising a cylinder assembly and two bearings, the bearings being mounted to the housing, the cylinder assembly being located in the first accommodating cavity and sandwiched between the two bearings, the cylinder assembly having a suction chamber and a discharge chamber, two side surfaces of the bearing in the axial direction being a first side facing away from the cylinder assembly and a second side facing toward the cylinder assembly, a sealing ring being in abutment between the first side and the housing, the sealing ring dividing the first side into a first region and a second region, the first region being in communication with the discharge chamber, and the second region being blocked from the discharge chamber of the cylinder assembly.

[0008] According to the compressor for a vehicle provided by the embodiments of the present application, by blocking the second area of the first side of the bearing from the exhaust cavity of the cylinder assembly, the area of the first side of the bearing subjected to high exhaust pressure is reduced, and the difference between the suction and exhaust pressures on both sides of the bearing is reduced, thereby effectively improving the concave deformation caused by the difference between the suction and exhaust pressures, improving the reliability of the compressor, meeting the reliability requirements of high pressure difference and heavy load working conditions, and facilitating the reduction of the axial size of the bearing to reduce the cost and weight, and facilitating the reduction of the distance between the bearing and the piston of the cylinder assembly to reduce the leakage and improve the efficiency of the compressor, and the bearing and the piston are not easy to contact and wear.

[0009] In addition, the compressor for a vehicle provided by the embodiments of the present application can further have the following additional technical features.

[0010] According to some embodiments of the present application, the housing has a second accommodating cavity for accommodating the motor, and the second area is in communication with the second accommodating cavity.

[0011] According to some embodiments of the present application, the bearing includes a body and a protrusion, the protrusion is arranged on the side of the body away from the cylinder assembly, a cavity wall of the first accommodating cavity is provided with a through hole, the protrusion is arranged in the through hole, the sealing ring includes a first sealing ring arranged between the protrusion and the inner wall of the through hole, and the side of the protrusion away from the cylinder assembly is the second area.

[0012] According to some embodiments of the present application, the housing has a second accommodating cavity for accommodating the motor, and the partition wall of the first accommodating cavity and the second accommodating cavity is provided with the through hole.

[0013] According to some embodiments of the present application, the bearing includes a body and a protrusion, the protrusion is arranged on the side of the body away from the cylinder assembly, a cavity wall of the first accommodating cavity is provided with a slot, the protrusion is arranged in the slot, the sealing ring includes a second sealing ring arranged between the protrusion and the slot wall, and the part of the protrusion away from the cylinder assembly and located in the area surrounded by the second sealing ring is the second area.

[0014] According to some embodiments of the present application, the housing has a second accommodating cavity for accommodating the motor, and the compressor further includes a crankshaft, the crankshaft is arranged in the first accommodating cavity and the second accommodating cavity, and the crankshaft is provided with a communication channel in communication with the second accommodating cavity and the slot.

[0015] According to some embodiments of the present application, the part of the body away from the cylinder assembly and located outside the first sealing ring or the second sealing ring is the first area.

[0016] According to some embodiments of the present application, an intermediate chamber is defined between the bearing and the housing, the housing is provided with an exhaust passage in communication with the intermediate chamber, the bearing is provided with an exhaust valve in communication with the exhaust chamber and the intermediate chamber, so that the gas in the exhaust chamber enters the intermediate chamber through the exhaust valve and is discharged through the exhaust passage, wherein the sealing ring comprises a third sealing ring, the third sealing ring is arranged around the exhaust valve, and the portion of the first side located in the region surrounded by the third sealing ring is the first region.

[0017] According to some embodiments of the present application, the projection of the exhaust chamber on the first side in the axial direction at least partially coincides with the first region; and the projection of the suction chamber on the first side in the axial direction at least partially coincides with the second region.

[0018] According to some embodiments of the present application, the area of the first region is S1, the area of the second region is S2, the cylinder assembly comprises a cylinder, the cylinder has a cylinder chamber, the cylinder chamber comprises the suction chamber and the exhaust chamber, and the cross-sectional area of the cylinder chamber perpendicular to the axial direction is S3, wherein S1 / S3 is 25%-45%; and / or S2 / S3 is 30%-60%.

[0019] According to some embodiments of the present application, the cylinder assembly comprises a cylinder and a piston, the cylinder has a cylinder chamber, the compression mechanism further comprises a crankshaft penetrating the cylinder chamber, the piston is sleeved on the crankshaft and is adapted to eccentrically rotate in the cylinder chamber, the area of the first region is S1, the maximum cross-sectional area of the exhaust chamber perpendicular to the axial direction is S4, the cross-sectional area of the gap between the crankshaft and the piston perpendicular to the axial direction is S5, and S1 / (S4+S5) is 70%-130%.

[0020] According to some embodiments of the present application, the housing comprises a high-pressure shell, a low-pressure shell and a partition, the high-pressure shell and the low-pressure shell are respectively arranged on the two sides of the partition, the high-pressure shell and the partition cooperatively define the first containing chamber, the low-pressure shell and the partition cooperatively define a second containing chamber, the second containing chamber is used for containing a motor, the two bearings are respectively a main bearing and a secondary bearing, the sealing ring is arranged between the main bearing and the partition, and the sealing ring is arranged between the secondary bearing and the high-pressure shell.

[0021] According to some embodiments of the present application, the refrigerant used by the compressor is carbon dioxide.

[0022] The vehicle according to embodiments of the present application comprises the compressor for vehicle according to embodiments of the present application.

[0023] Additional aspects and advantages of the application will be set forth in part in the description which follows, and in part will become apparent to those skilled in the art upon examination of the following and / or can be learned by practice of the application. BRIEF DESCRIPTION OF DRAWINGS

[0024] The foregoing and / or additional aspects and advantages of the application are achieved by providing what is described below and / or claimed by the application as can be learned by perusal of the following description and / or claims.

[0025] FIG. 1 is a schematic view of a compressor according to some embodiments of the application;

[0026] FIG. 2 is a left view of a cylinder assembly according to some embodiments of the application;

[0027] FIG. 3 is a sectional view of a compressor according to some embodiments of the application;

[0028] FIG. 4 is a sectional view of FIG. 2 according to some embodiments of the application;

[0029] FIG. 5 is a sectional view of FIG. 4 according to some embodiments of the application;

[0030] FIG. 6 is a left view of a cylinder assembly according to some embodiments of the application;

[0031] FIG. 7 is a sectional view of FIG. 6 according to some embodiments of the application;

[0032] FIG. 8 is a schematic view of a vehicle according to some embodiments of the application.

[0033] REFERENCE NUMERALS:

[0034] Vehicle 200; Compressor 100;

[0035] Housing 10; First accommodating cavity 101; Second accommodating cavity 102; Through hole 103; Insert slot 104; First intermediate chamber 105; Second intermediate chamber 106; Oil cavity 107; High-pressure shell 11; First exhaust passage 111; Low-pressure shell 12; Partition 13; Intake hole 131;

[0036] Compression mechanism 20; Intake passage 201; First through passage 202; Second through passage 203;

[0037] Cylinder assembly 30; Suction cavity 301; Exhaust cavity 302; Cylinder 31; Cylinder cavity 311; Piston 32; Slide vane 33; Middle partition 34;

[0038] Bearing 40; First side 401; First region 401a; Second region 401b; Second side 402; Body 41; Convex portion 42; Main bearing 43; Auxiliary bearing 44;

[0039] Sealing ring 50; first sealing ring 51; second sealing ring 52; third sealing ring 53; fourth sealing ring 54; fifth sealing ring 55;

[0040] Crankshaft 60; communication passage 601;

[0041] Exhaust valve 70. Embodiments of the present application

[0042] Embodiments of the present application are described in detail below with reference to the attached drawing figures, wherein the same or like reference numerals and characters designate the same or like components throughout the drawings. The embodiments described below are exemplary, and are merely intended to explain the present application, and are not to be understood as limiting the present application.

[0043] In the description of the present application, it is to be understood that the orientations or positional relationships indicated by the terms "center", "longitudinal", "lateral", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "clockwise", "counterclockwise", "axial", "radial", "circumferential" and the like are based on the orientations or positional relationships shown in the drawings, and are only for the convenience of describing the present application and simplifying the description, and do not indicate or imply that the devices or elements referred to must have a particular orientation, be constructed and operated in a particular orientation, and therefore cannot be understood as limiting the present application.

[0044] In the description of the present application, "first feature" and "second feature" can include one or more of the features, the meaning of "a plurality of" is two or more, and "above" or "below" the first feature with respect to the second feature can include that the first and second features are in direct contact, or can include that the first and second features are not in direct contact but are in contact through another feature therebetween, and "above", "over" and "on" the first feature with respect to the second feature include that the first feature is directly above and obliquely above the second feature, or only indicates that the first feature is higher than the second feature in horizontal height.

[0045] The compression mechanism of the compressor is in a high-pressure cavity with high exhaust pressure. The compression mechanism bears high pressure of the exhaust, especially the inner and outer end faces of the bearing. The outer end face bears high pressure all the time, and the inner end face bears the suction pressure of the suction cavity and the exhaust pressure of the exhaust cavity as the compressor operates. When the cylinder is in the suction state, the pressure difference between the inner and outer cylinders due to the suction and exhaust pressure difference will cause the deformation of the two end faces of the bearing. The bearing is concave to the inner cavity of the cylinder, which causes the gap between the bearing and the piston to become smaller and is prone to contact and wear. In some related technologies, the deformation caused by the pressure difference is resisted by increasing the axial thickness of the bearing, but the problem of greater deformation with greater pressure difference and the need for thicker bearings still exists, especially for refrigerants with higher exhaust pressure such as carbon dioxide. Increasing the thickness of the bearing will increase the cost, weight and compression. In some other related technologies, the wear problem is solved by increasing the gap between the piston and the bearing in the axial direction, but this will cause increased leakage and reduced compressor efficiency.

[0046] To this end, the application provides a compressor 100 for a vehicle 200. By blocking the first area 401a of the first side 401 of the bearing 40 from the exhaust cavity 302 of the cylinder assembly 30, the area of the first side 401 of the bearing 40 subjected to high exhaust pressure is reduced, and the suction and exhaust pressure difference on both sides of the bearing 40 is reduced, effectively improving the concave deformation caused by the suction and exhaust pressure difference, improving the reliability of the compressor 100, and meeting the reliability requirements of high pressure difference and heavy load working conditions.

[0047] The compressor 100 for a vehicle 200 according to the embodiments of the application will be described below with reference to the accompanying drawings. In the embodiments of the application, the compressor 100 can be a horizontal compressor or a vertical compressor, and can be a single-cylinder single-exhaust compressor, a single-cylinder double-exhaust compressor, a double-cylinder compressor, etc. For example, the compressor 100 can be a rotary compressor.

[0048] Referring to FIGS. 1-3, the compressor 100 for a vehicle 200 according to the embodiments of the application can include a housing 10 and a compression mechanism 20.

[0049] Specifically, the housing 10 has a first accommodating cavity 101, the compression mechanism 20 includes a cylinder assembly 30 and two bearings 40, the bearings 40 are installed in the housing 10, the cylinder assembly 30 is located in the first accommodating cavity 101 and is clamped between the two bearings 40, and the cylinder assembly 30 has a suction cavity 301 and an exhaust cavity 302.

[0050] The bearing 40 can provide support and limit for the installation of the cylinder assembly 30, and the operation of the cylinder assembly 30 can realize the compression of the refrigerant. For example, the cylinder assembly 30 can include a cylinder 31 having a cylinder cavity 311 in which an eccentric rotating piston 32 is arranged and a vane 33 slot in which a reciprocating vane 33 is arranged, and one end of the vane 33 abuts against the outer peripheral wall of the piston 32. The vane 33 is movably arranged in the vane 33 slot, and the tip of the vane 33 (the end of the vane 33 closest to the center of the cylinder 31) abuts against the outer peripheral wall of the piston 32. The piston 32 is rollable along the inner wall of the corresponding cylinder cavity 311, and under the action of spring force or gas force, the tip of the vane 33 can always abut against the outer peripheral wall of the piston 32. When the piston 32 rotates in the cylinder cavity 311, the vane 33 moves in the vane 33 slot, so that the piston 32 and the vane 33 cooperate to divide the cylinder cavity 311 into a suction cavity 301 and a discharge cavity 302. The cylinder 31 has an intake port communicating with the suction cavity 301 and a discharge port communicating with the discharge cavity 302. In the compressor 100, the piston 32 can be sleeved on the eccentric portion of the crankshaft 60 of the compressor 100. The motor drives the crankshaft 60 to rotate, and the piston 32 is driven by the crankshaft 60 to abut against and roll along the inner wall of the cylinder cavity 311 to compress the refrigerant, so that the refrigerant enters the suction cavity 301 through the intake port. The piston 32 rolls along the inner wall of the cylinder cavity 311 to compress the refrigerant, the refrigerant is continuously heated and pressurized, and then enters the discharge cavity 302, and then is discharged from the cylinder cavity 311 through the discharge port.

[0051] In addition, as shown in FIGS. 1-3, the two side surfaces of the bearing 40 in the axial direction are a first side 401 and a second side 402, respectively. The first side 401 faces away from the cylinder assembly 30, and the second side 402 faces toward the cylinder assembly 30. The first side 401 abuts against the sealing ring 50 between the housing 10, and the sealing ring 50 can divide the first side 401 into a first region 401a and a second region 401b. The first region 401a communicates with the discharge cavity 302, and the second region 401b is blocked from the discharge cavity 302 of the cylinder assembly 30, that is, the high-pressure gas discharged from the discharge cavity 302 cannot flow to the second region 401b.

[0052] In the above embodiment, at least part of the second side 402 can bear the pressure of the suction cavity 301 and the discharge cavity 302 of the cylinder assembly 30. When the cylinder assembly 30 is in a suction state, the overall second side 402 bears less pressure. The first region 401a bears the discharge pressure of the cylinder assembly 30, and the second region 401b does not bear the discharge pressure of the cylinder assembly 30. The gas pressure borne by the second region 401b can be less than the gas pressure of the discharge cavity 302, so that part of the area of the first side 401 of the bearing 40 is changed from bearing the discharge pressure in the related art to bearing the suction pressure or the intermediate pressure.

[0053] Therefore, the area of the first side 401 of the bearing 40 subjected to high pressure is reduced, the pressure difference between the suction and discharge sides of the bearing 40 is reduced, the inward deformation of the bearing 40 caused by the pressure difference between the suction and discharge sides is reduced, the reliability of the compressor 100 is improved, especially the reliability of the compressor 100 under high pressure difference and heavy load conditions, and the reliability requirements of the compressor 100 using carbon dioxide and other high-pressure fluid as refrigerant can be met. Moreover, under the condition of certain pressure-bearing capacity requirement, the axial thickness of the bearing 40 can be relatively reduced to reduce the cost and weight, and the gap between the bearing 40 and the piston 32 and the gap between the bearing 40 and the vane 33 can be reduced to reduce the leakage and improve the efficiency of the compressor 100.

[0054] It is worth noting that the sum of the areas of the first region 401a and the second region 401b can be equal to the area of the first side 401, or can be less than the area of the first side 401. In the description of the present application, the areas of the first region 401a, the second region 401b, the first side 401 and the second side 402 are the areas of the projections in the axial direction of the compression mechanism 20.

[0055] The first side 401 and the housing 10 can be provided with one sealing ring 50 or a plurality of sealing rings 50; the first side 401 can include one first region 401a or a plurality of first regions 401a, and can include one second region 401b or a plurality of second regions 401b.

[0056] According to the compressor 100 for the vehicle 200 provided by the embodiments of the present application, by blocking the second region 401b of the first side 401 of the bearing 40 away from the cylinder assembly 30 from the discharge cavity 302 of the cylinder assembly 30, the area of the first side 401 of the bearing 40 subjected to high discharge pressure is reduced, and the pressure difference between the suction and discharge sides of the bearing 40 is reduced, the inward deformation caused by the pressure difference between the suction and discharge sides is effectively improved, the reliability of the compressor 100 is improved, the reliability requirements under high pressure difference and heavy load conditions can be met, and the axial size of the bearing 40 is reduced to reduce the cost and weight, the distance between the bearing 40 and the piston 32 of the cylinder assembly 30 is reduced to reduce the leakage and improve the efficiency of the compressor 100, and the bearing 40 and the piston 32 are not easy to contact and wear.

[0057] According to some embodiments of the present application, as shown in FIG. 1, the shell 10 has a second accommodating cavity 102 for accommodating the motor. The second accommodating cavity 102 is formed as a low-pressure cavity with a gas pressure lower than that of the exhaust cavity 302. The second accommodating cavity 102 can provide a layout space for the motor, so as to isolate the high-temperature and high-pressure gas in the second accommodating cavity 102 from the thermal influence on the motor, reduce the risk of performance degradation or even damage of the motor due to overheating, thereby facilitating the reduction of the working temperature of the motor, the reduction of the heat dissipation burden, the prolongation of the service life of the motor, the improvement of the working stability and reliability of the compressor 100, and the reduction of the risk of shutdown of the compressor 100 due to motor failure.

[0058] The second region 401b can be in communication with the second accommodating cavity 102 or be blocked from the second accommodating cavity 102. For example, the second region 401b can be in communication with the normal-pressure space, so that the gas pressure of the second region 401b is between the gas pressures of the low-pressure cavity and the exhaust cavity 302, which can reduce the deformation of the bearing 40. In the embodiment in which the second region 401b is in communication with the second accommodating cavity 102, the gas pressure borne by the second region 401b is closer to the gas pressure of the suction cavity 301, so that the pressure difference between the first side 401 and the second side 402 of the bearing 40 is lower, and the effect of reducing the deformation of the bearing 40 is better.

[0059] According to some embodiments of the present application, as shown in FIG. 1, the shell 10 includes a high-pressure shell 11, a low-pressure shell 12, and a partition 13. The high-pressure shell 11 and the low-pressure shell 12 are respectively arranged on the two sides of the partition 13, such as the left and right sides shown in FIG. 1. The high-pressure shell 11 cooperates with the partition 13 to define the first accommodating cavity 101, and the low-pressure shell 12 cooperates with the partition 13 to define the second accommodating cavity 102 for accommodating the motor. The motor can drive the compression mechanism 20 to operate to compress the refrigerant. The partition 13 can isolate the high-temperature and high-pressure gas in the second accommodating cavity 102 from the thermal influence on the motor.

[0060] In addition, continuing to refer to FIG. 1, the two bearings 40 are respectively a main bearing 43 and a secondary bearing 44. The main bearing 43 is provided with a sealing ring 50 between the main bearing 43 and the partition 13, and the secondary bearing 44 is provided with a sealing ring 50 between the secondary bearing 44 and the high-pressure shell 11. In other words, the suction-exhaust pressure difference on the two axial sides of the main bearing 43 can be reduced, and the suction-exhaust pressure difference on the two axial sides of the secondary bearing 44 can also be reduced. The main bearing 43 and the secondary bearing 44 are less likely to be deformed, and the effect of improving the reliability of the compressor 100 is better, especially the reliability under high-pressure difference and heavy load conditions.

[0061] It is worth noting that the stress conditions of the main bearing 43 and the secondary bearing 44 can be the same or different according to actual conditions. When the stress conditions of the main bearing 43 and the secondary bearing 44 are the same, the overall stress of the compressor 100 is more balanced, which is conducive to improving the overall reliability of the compressor 100.

[0062] In some embodiments of the present application, as shown in FIGS. 1-5, the bearing 40 comprises a body 41 and a protrusion 42, the protrusion 42 is arranged on the side of the body 41 away from the cylinder assembly 30. The cavity wall of the first accommodating cavity 101 is provided with a through hole 103, the protrusion 42 is arranged in the through hole 103, the sealing ring 50 comprises a first sealing ring 51 arranged between the protrusion 42 and the inner wall of the through hole 103, and the side of the protrusion 42 away from the cylinder assembly 30 is the second area 401b.

[0063] By arranging the protrusion 42 on the side of the body 41 away from the cylinder assembly 30, the surface of the body 41 away from the cylinder assembly 30 and the surface of the protrusion 42 away from the cylinder assembly 30 together form the first side 401. The protrusion 42 is arranged in the through hole 103 and sealed between the protrusion 42 and the inner wall of the through hole 103 by the first sealing ring 51, so that the space in the first accommodating cavity 101 is not communicated with the side of the protrusion 42 away from the cylinder assembly 30, and the high-pressure gas discharged from the exhaust cavity 302 cannot flow to the surface of the protrusion 42 away from the cylinder assembly 30. Therefore, the side of the protrusion 42 away from the cylinder assembly 30 does not need to bear the high pressure of the exhaust, effectively reducing the area of the first side 401 of the bearing 40 that bears the high pressure, and effectively reducing the pressure difference between the two sides of the bearing 40 in the axial direction.

[0064] In addition, the cooperation of the protrusion 42 and the through hole 103 can realize reliable limiting and installation of the bearing 40 on the shell 10, and the protrusion 42 also improves the local thickness of the bearing 40 to some extent, which is also conducive to reducing the deformation of the bearing 40.

[0065] In some embodiments of the shell 10 having the second accommodating cavity 102, as shown in FIG. 1, the partition wall between the first accommodating cavity 101 and the second accommodating cavity 102 is provided with a through hole 103, for example, in the embodiment comprising the partition piece 13, the partition piece 13 can be provided with a through hole 103. The protrusion 42 is arranged in the through hole 103, so that the side of the protrusion 42 away from the cylinder assembly 30 is communicated with the second accommodating cavity 102, and the side of the protrusion 42 away from the cylinder assembly 30 bears the suction pressure, which is more effective in reducing the deformation of the bearing 40.

[0066] In some embodiments of the present application, as shown in FIGS. 1-5, the bearing 40 comprises a body 41 and a protrusion 42, the protrusion 42 is arranged on the side of the body 41 away from the cylinder assembly 30. The cavity wall of the first accommodating cavity 101 is provided with a slot 104, the protrusion 42 is arranged in the slot 104, the sealing ring 50 comprises a second sealing ring 52 arranged between the protrusion 42 and the slot wall of the slot 104, and the part of the protrusion 42 away from the cylinder assembly 30 and located in the area surrounded by the second sealing ring 52 is the second area 401b.

[0067] The gap between the convex portion 42 and the slot wall of the insertion slot 104 is sealed by the second sealing ring 52, so that the side of the convex portion 42 away from the cylinder assembly 30 is not communicated with the first accommodating cavity 101, and the high-pressure gas discharged from the exhaust cavity 302 cannot flow to the surface of the side of the convex portion 42 away from the cylinder assembly 30. Thus, the side of the convex portion 42 away from the cylinder assembly 30 does not need to bear the high pressure of the exhaust gas, effectively reducing the area of the first side 401 of the bearing 40 that bears the high pressure, and effectively reducing the pressure difference between the two axial sides of the bearing 40. In addition, the insertion slot 104 can play a good limiting and mounting role on the bearing 40.

[0068] It should be noted that in the embodiments of the present application, the two bearings 40 can be matched with the through hole 103, or matched with the insertion slot 104, or one bearing 40 is matched with the through hole 103 and the other bearing 40 is matched with the insertion slot 104. For example, in the example shown in FIG. 1, the main bearing 43 is matched with the through hole 103 of the partition 13, and the auxiliary bearing 44 is matched with the insertion slot 104 of the high-pressure shell 11, so that the space in the high-pressure shell 11 is not communicated with the space outside the shell 10, reducing the risk of leakage.

[0069] In some embodiments, as shown in FIGS. 1 and 4, the shell 10 has a second accommodating cavity 102 for accommodating the motor, and the compression mechanism 20 further includes a crankshaft 60, the crankshaft 60 is arranged in the first accommodating cavity 101 and the second accommodating cavity 102, and the crankshaft 60 is provided with a communication passage 601 communicating the second accommodating cavity 102 and the insertion slot 104. By arranging the communication passage 601, the space in the insertion slot 104 can be communicated with the second accommodating cavity 102, so that the side of the convex portion 42 away from the cylinder assembly 30 bears the suction pressure, and the effect of reducing the deformation of the bearing 40 is better.

[0070] According to some embodiments of the present application, as shown in FIGS. 1-5, the part of the body 41 away from the cylinder assembly 30 and outside the first sealing ring 51 or the second sealing ring 52 is the first area 401a. In other words, the sealing ring 50 only includes at least one of the first sealing ring 51 and the second sealing ring 52, and the area of the first side 401 that is not in the area surrounded by the sealing ring 50 is communicated with the exhaust cavity 302 and bears the high pressure of the exhaust gas. Under the premise of meeting the small deformation of the bearing 40, the sealing structure between the bearing 40 and the shell 10 is simpler, which is beneficial to simplify the structure.

[0071] According to some embodiments of the present application, as shown in FIGS. 1-7, an intermediate chamber is defined between the bearing 40 and the housing 10, the housing 10 is provided with an exhaust passage (e.g., first exhaust passage 111 and second exhaust passage) communicating with the intermediate chamber (e.g., first intermediate chamber 105 and second intermediate chamber 106), and the bearing 40 is provided with an exhaust valve 70 communicating the exhaust chamber 302 and the intermediate chamber, so that the high-pressure gas in the exhaust chamber 302 can enter the intermediate chamber through the exhaust valve 70 and then be discharged through the exhaust passage.

[0072] For example, in some embodiments, as shown in FIGS. 1-5, the housing 10 includes a low-pressure shell 12, a high-pressure shell 11, and a partition 13 disposed between the low-pressure shell 12 and the high-pressure shell 11, the low-pressure shell 12 and the partition 13 define a second accommodating chamber 102 for accommodating the motor, and the high-pressure shell 11 and the partition 13 define a first accommodating chamber 101, and the partition 13 is provided with an air inlet hole 131 communicating with the second accommodating chamber 102. The compression mechanism 20 divides the first accommodating chamber 101 into a first intermediate chamber 105, a second intermediate chamber 106, and an oil chamber 107, and the intermediate chamber includes the first intermediate chamber 105 and the second intermediate chamber 106. Specifically, the two bearings 40 are a main bearing 43 and a sub-bearing 44, the main bearing 43 is sealingly fitted with the partition 13 by a fourth sealing ring 54 to define the first intermediate chamber 105, and the sub-bearing 44 is sealingly fitted with the high-pressure shell 11 by a fifth sealing ring 55 to define the second intermediate chamber 106. The outer periphery of the compression mechanism 20 and the high-pressure shell 11 define the oil chamber 107 for storing lubricating oil. The main bearing 43 is provided with an air inlet passage 201 axially opposite the air inlet hole 131 to communicate the air inlet hole 131 and the cylinder chamber 311, and the main bearing 43 is further provided with an exhaust valve 70 axially opposite and communicating with the first intermediate chamber 105. The compression mechanism 20 is provided with a first through passage 202 formed in the main bearing 43, the cylinder 31, the partition 34, and the sub-bearing 44, and the first through passage 202 communicates the first intermediate chamber 105 and the second intermediate chamber 106. The high-pressure shell 11 is provided with a first exhaust passage 111 communicating with the second intermediate chamber 106, and the first exhaust passage 111 can be provided on the right end wall of the high-pressure shell 11 or on the peripheral wall of the high-pressure shell 11.

[0073] During the operation of the compressor 100, the refrigerant in the second accommodating cavity 106 flows into the cylinder cavity 311 through the intake hole 131 and the intake passage 201 as indicated by arrow a; the compressed refrigerant in the cylinder cavity 311 can flow into the first intermediate chamber 105 through the left end exhaust valve 70 as indicated by arrow b, and then flow to the second intermediate chamber 106 through the first through passage 202 as indicated by arrow c; the compressed refrigerant can also flow into the second intermediate chamber 106 through the right end exhaust valve 70 as indicated by arrow b'; the refrigerant in the second intermediate chamber 106 can be discharged from the shell 10 through the first exhaust passage 111 as indicated by arrow d.

[0074] Of course, the flow path arrangement of the compressor 100 is not limited to this, for example, in other embodiments, the high-pressure shell 11 is provided with the first exhaust passage 111, and the first exhaust passage 111 of the high-pressure shell 11 communicates with the second intermediate chamber 106; the partition 13 is provided with the second exhaust passage, and the second exhaust passage of the partition 13 communicates with the first intermediate chamber 105. The refrigerant in the first intermediate chamber 105 can be discharged through the second exhaust passage of the partition 13, and the refrigerant in the second intermediate chamber 106 can be discharged through the first exhaust passage 111 of the high-pressure shell 11.

[0075] In some embodiments, as shown in FIGS. 6 and 7, the sealing ring 50 includes a third sealing ring 53, and the third sealing ring 53 is arranged around the exhaust valve 70. The portion of the first side 401 located in the area surrounded by the third sealing ring 53 is the first area 401a. That is, the third sealing ring 53 seals the gap between the bearing 40 and the shell 10, and makes the high-pressure gas flow in the area surrounded by the third sealing ring 53.

[0076] Therefore, the high-pressure gas discharged by the exhaust valve 70 can flow to the first area 401a surrounded by the third sealing ring 53, and the first area 401a bears the exhaust high pressure. The area of the first side 401 which is not surrounded by the third sealing ring 53 can not be affected by the exhaust high pressure. By arranging the third sealing ring 53, the area of the first side 401 which bears the high pressure can be more flexible, for example, the area of the first area 401a can be smaller, so as to further improve the deformation problem of the bearing 40 caused by the suction and exhaust pressure difference.

[0077] It is worth noting that the sealing ring 50 can only include the third sealing ring 53, at this time the part located in the area surrounded by the third sealing ring 53 is the first area 401a, and the part located outside the third sealing ring 53 is the second area 401b; or the sealing ring 50 can include at least one of the first sealing ring 51 and the second sealing ring 52 and the third sealing ring 53, taking the case of including the first sealing ring 51 and the third sealing ring 53 as an example, the part located in the area surrounded by the third sealing ring 53 is the first area 401a, the part located in the area surrounded by the first sealing ring 51 is the second area 401b which communicates with the second containing cavity 102, and the part located outside the first sealing ring 51 and outside the third sealing ring 53 is the second area 401b which communicates with the normal pressure space.

[0078] In the embodiment including the third sealing ring 53, a second exhaust passage can be provided in the partition 13, and the second exhaust passage communicates with the area surrounded by the third sealing ring 53 corresponding to the main bearing 43, so that the gas discharged by the exhaust valve 70 corresponding to the main bearing 43 is discharged through the second exhaust passage of the partition 13, and the gas discharged by the exhaust valve 70 corresponding to the auxiliary bearing 44 is discharged through the first exhaust passage 111 of the high-pressure shell 11; or as shown in FIGS. 6 and 7, an axially penetrating second penetrating passage 203 can be provided in the compression mechanism 20, and the second penetrating passage 203 communicates the area surrounded by the third sealing ring 53 corresponding to the main bearing 43 and the area surrounded by the third sealing ring 53 corresponding to the auxiliary bearing 44, so that the gas discharged by the exhaust valve 70 corresponding to the main bearing 43 can flow to the area surrounded by the third sealing ring 53 corresponding to the auxiliary bearing 44 through the second penetrating passage 203, and then be discharged through the first exhaust passage 111 of the high-pressure shell 11.

[0079] According to some embodiments of the present application, the projection of the exhaust cavity 302 on the first side 401 at least partially coincides with the first area 401a in the axial direction; and the projection of the suction cavity 301 on the first side 401 at least partially coincides with the second area 401b in the axial direction.

[0080] The high-pressure gas in the exhaust cavity 302 acts on the second side 402 to form a high-pressure area; the projection of the exhaust cavity 302 and the first area 401a at least partially coincide, so that the high-pressure area of the second side 402 and the first area 401a are at least partially opposite in the axial direction; the low-pressure gas in the suction cavity 301 acts on the second side 402 to form a low-pressure area; the projection of the suction cavity 301 and the second area 401b at least partially coincide, so that the low-pressure area of the second side 402 and the second area 401b are at least partially opposite in the axial direction. In this way, the positions of the high-pressure and low-pressure areas on the two sides of the bearing 40 in the axial direction are the same or similar, so that the stress on different positions of the bearing 40 is more uniform, and the deformation is smaller.

[0081] According to some embodiments of the present application, the area of the first region 401a is S1, and the area of the second region 401b is S2. The cylinder assembly 30 includes a cylinder 31 having a cylinder cavity 311 including the intake cavity 301 and the exhaust cavity 302, and the cross-sectional area of the cylinder cavity 311 perpendicular to the axial direction is S3. For example, the cross-sectional area of the cylinder cavity 311 perpendicular to the axial direction is equal to the sum of the cross-sectional area of the intake cavity 301, the cross-sectional area of the exhaust cavity 302, the cross-sectional area of the piston 32, the cross-sectional area of the crankshaft 60, and the cross-sectional area of the gap between the piston 32 and the crankshaft 60 perpendicular to the axial direction. In embodiments in which the cylinder assembly 30 includes a plurality of cylinders 31, two adjacent cylinders 31 can be separated by a partition 34.

[0082] In some embodiments, S1 / S3 is 25% to 45%. Within the above range, the area of the first region 401a is closer to the projected area of the exhaust cavity 302 on the second side 402, so that the high-pressure areas on both sides of the bearing 40 are the same or similar, and the effect of reducing the deformation of the bearing 40 is better. For example, in some specific embodiments, S1 / S3 can be 25%, 30%, 35%, 40%, 45%, etc.

[0083] In some embodiments, S2 / S3 is 30% to 60%. Within the above range, the area of the second region 401b is closer to the projected area of the intake cavity 301 on the second side 402, so that the low-pressure areas on both sides of the bearing 40 are the same or similar, and the effect of reducing the deformation of the bearing 40 is better. For example, in some specific embodiments, S2 / S3 can be 30%, 35%, 40%, 45%, 50%, 55%, 60%, etc.

[0084] According to some embodiments of the present application, as shown in FIGS. 4 and 5, the cylinder assembly 30 includes a cylinder 31 having a cylinder cavity 311, and the compression mechanism 20 further includes a crankshaft 60 penetrating the cylinder cavity 311, and a piston 32 sleeved on the crankshaft 60 and capable of eccentric rotation in the cylinder cavity 311. The area of the first region 401a is S1, the maximum cross-sectional area of the exhaust cavity 302 perpendicular to the axial direction is S4, the cross-sectional area of the gap between the crankshaft 60 and the piston 32 perpendicular to the axial direction is S5, and S1 / (S4+S5) is 70% to 130%.

[0085] During the operation of the compressor 100, the gap between the crankshaft 60 and the piston 32 can circulate lubricating medium, and the high pressure of the lubricating medium can cause the gap to act on the second side 402 to form high pressure. Within the above range, the area of the first region 401a is closer to the high pressure area of the second region 401b, and the projection area of the exhaust cavity 302 on the second side 402 changes during the entire operation cycle of the compressor 100. Within the above range, the area of the first region 401a can adapt to the area change of the exhaust cavity 302, so that the deformation of the bearing 40 during the entire operation cycle is effectively reduced.

[0086] For example, in some embodiments, S1 / (S4+S5) can be 70%, 80%, 90%, 100%, 110%, 120%, and 130%, etc.

[0087] In some embodiments, the compressor 100 adopts carbon dioxide as the refrigerant, and the compressor 100 can be a carbon dioxide compressor 100. For example, when carbon dioxide is used as the refrigerant, the suction and discharge pressures are relatively high, and carbon dioxide has good thermodynamic properties. Therefore, when the same refrigeration capacity is required, the volume of the compression chamber of the compressor 100 does not need to be too large when carbon dioxide is used as the refrigerant. The volume of the compression chamber can be reduced, thereby reducing the volume and weight of the entire compressor 100. In addition, the compressor 100 using carbon dioxide can operate in a wide pressure range, whether it is preliminary compression in a low-pressure environment or deep compression in a high-pressure environment, and can exhibit stable performance. Therefore, the compressor 100 of the embodiment of the present application can obtain an optimized compression ratio, has high cooling performance when used in a refrigeration system, can reduce energy consumption, and improve energy utilization.

[0088] When the carbon dioxide compressor 100 is used to obtain a large compression ratio, the exhaust pressure is high, the pressure difference between the two sides of the bearing 40 is higher, and the refrigeration capacity is stronger. Therefore, the matching structure of the bearing 40 is improved to improve the influence of the high pressure difference on the force bearing of the bearing 40 when a high compression ratio is obtained by using carbon dioxide as the refrigerant medium.

[0089] The vehicle 200 according to the embodiments of the present application comprises the compressor 100 for the vehicle 200 according to the embodiments of the present application. Since the compressor 100 for the vehicle 200 according to the embodiments of the present application has the beneficial technical effects described above, the vehicle 200 according to the embodiments of the present application, by blocking the second area 401b of the first side 401 of the bearing 40 facing away from the cylinder assembly 30 from the exhaust cavity 302 of the cylinder assembly 30, reduces the area of the first side 401 of the bearing 40 subjected to high exhaust pressure, and in turn reduces the suction and exhaust pressure difference on both sides of the bearing 40 in the axial direction, effectively improves the concave deformation caused by the suction and exhaust pressure difference, improves the reliability of the compressor 100, can meet the reliability requirements of high pressure difference and heavy load working conditions, and is beneficial to reducing the axial size of the bearing 40 to reduce the cost and weight, and is beneficial to reducing the distance between the bearing 40 and the piston 32 of the cylinder assembly 30 to reduce leakage, improve the efficiency of the compressor 100, and the bearing 40 and the piston 32 are not easy to contact and wear.

[0090] It should be noted that the specific type of the vehicle 200 referred to in the present application is not limited, for example, the vehicle 200 can be a fuel automobile, a gas automobile or a new energy automobile, the new energy automobile can be a pure electric automobile, a hybrid electric automobile, a fuel cell electric automobile, a range extended automobile, a solar electric automobile, a gas fuel automobile (for example, a hydrogen engine automobile) or a biofuel automobile (for example, an automobile using ethanol, biodiesel or the like as a power source) and the like.

[0091] The other configurations and operations of the compressor 100 and the vehicle 200 according to the embodiments of the present application are known to those skilled in the art, and will not be described in detail here.

[0092] In the description of the present application, it should be noted that unless otherwise explicitly specified and limited, the terms "mounting", "connecting", "connection" should be understood broadly, for example, it can be fixed connection, or detachable connection, or integrally connected; it can be mechanical connection, or electrical connection; it can be directly connected, or indirectly connected through an intermediate medium, or the communication inside two elements. For those skilled in the art, the specific meaning of the above terms in the present application can be understood according to the specific circumstances.

[0093] In the description of the present application, the description referring to the terms "embodiment", "specific embodiment", "example" and the like means that the specific features, structures, materials or characteristics described in conjunction with the embodiment or example are included in at least one embodiment or example of the present application. In the present specification, the illustrative description of the above terms does not necessarily refer to the same embodiment or example. Moreover, the specific features, structures, materials or characteristics described can be combined in any one or more embodiments or examples in a suitable manner.

[0094] While the embodiments of the application have been shown and described, it is to be understood that the embodiments can be varied, modified, substituted and changed by those skilled in the art without departing from the principles and spirit of the application, the scope of which is defined by the claims and their equivalents.

Claims

1. A compressor for a vehicle, wherein, The application relates to a compressor, comprising: a housing having a first accommodating cavity; a compression mechanism comprising a cylinder assembly and two bearings, the bearings being mounted on the housing, the cylinder assembly being located in the first accommodating cavity and clamped between the two bearings, the cylinder assembly having a suction cavity and a discharge cavity, two side faces of the bearings in the axial direction are respectively a first side face facing away from the cylinder assembly and a second side face facing the cylinder assembly, a sealing ring is in abutment between the first side face and the housing, the sealing ring divides the first side face into a first region and a second region, the first region is in communication with the discharge cavity, and the second region is blocked from the discharge cavity of the cylinder assembly.

2. The compressor for a vehicle according to claim 1, wherein The housing has a second accommodating cavity for accommodating an electric motor, and the second region is in communication with the second accommodating cavity.

3. The compressor for a vehicle according to any one of claims 1-2, wherein, The bearing comprises a body and a protrusion, the protrusion being arranged on a side of the body facing away from the cylinder assembly, a through hole is arranged on a cavity wall of the first accommodating cavity, the protrusion is arranged in the through hole, the sealing ring comprises a first sealing ring arranged between the protrusion and an inner wall of the through hole, and the side of the protrusion facing away from the cylinder assembly is the second region.

4. The compressor for a vehicle according to claim 3, wherein The housing has a second accommodating cavity for accommodating an electric motor, and a partition wall between the first accommodating cavity and the second accommodating cavity is provided with the through hole.

5. The compressor for a vehicle according to any one of claims 1-4, wherein, The bearing comprises a body and a protrusion, the protrusion being arranged on a side of the body facing away from the cylinder assembly, a slot is arranged on a cavity wall of the first accommodating cavity, the protrusion is arranged in the slot, the sealing ring comprises a second sealing ring arranged between the protrusion and a slot wall of the slot, and the part of the side of the protrusion facing away from the cylinder assembly and located in the region surrounded by the second sealing ring is the second region.

6. The compressor for a vehicle according to claim 5, wherein The housing has a second accommodating cavity for accommodating an electric motor, and the compression mechanism further comprises a crankshaft, the crankshaft is arranged in the first accommodating cavity and the second accommodating cavity, and the crankshaft is provided with a communication channel in communication with the second accommodating cavity and the slot.

7. The compressor for a vehicle according to claim 3 or 5, wherein The part of the side of the body facing away from the cylinder assembly and located outside the first sealing ring or the second sealing ring is the first region.

8. The compressor for a vehicle according to any one of claims 1-6, wherein, An intermediate cavity is defined between the bearing and the housing, the housing is provided with an exhaust passage in communication with the intermediate cavity, the bearing is provided with an exhaust valve in communication with the discharge cavity and the intermediate cavity, so that the gas in the discharge cavity enters the intermediate cavity through the exhaust valve and is discharged through the exhaust passage, and wherein The sealing ring comprises a third sealing ring, the third sealing ring is arranged around the exhaust valve, and the part of the first side located in the region surrounded by the third sealing ring is the first region.

9. The compressor for a vehicle according to any one of claims 1-8, wherein, The projection of the discharge cavity on the first side in the axial direction at least partially coincides with the first region, and the projection of the suction cavity on the first side in the axial direction at least partially coincides with the second region.

10. The compressor for a vehicle according to any one of claims 1-9, wherein, The area of the first region is S1, the area of the second region is S2, the cylinder assembly comprises a cylinder, the cylinder has a cylinder cavity, the cylinder cavity comprises the suction cavity and the discharge cavity, and the cross-sectional area of the cylinder cavity perpendicular to the axial direction is S3, wherein S1 / S3 is 25% to 45%; and / or, S2 / S3 is 30% to 60%.

11. The compressor for a vehicle according to any one of claims 1-10, wherein, The cylinder assembly comprises a cylinder having a cylinder cavity and a piston, and the compression mechanism further comprises a crankshaft penetrating the cylinder cavity, the piston being sleeved on the crankshaft and being adapted to eccentrically rotate in the cylinder cavity, The first area is S1, the maximum cross-sectional area of the exhaust cavity perpendicular to the axial direction is S4, the cross-sectional area of the gap between the crankshaft and the piston perpendicular to the axial direction is S5, and S1 / (S4+S5) is 70% to 130%.

12. The compressor for a vehicle according to any one of claims 1-11, wherein, The shell comprises a high-pressure shell, a low-pressure shell and a partition, the high-pressure shell and the low-pressure shell are respectively arranged on two sides of the partition, the high-pressure shell and the partition cooperatively define the first accommodating cavity, the low-pressure shell and the partition cooperatively define a second accommodating cavity, and the second accommodating cavity is used for accommodating an electric motor, The two bearings are respectively a main bearing and a secondary bearing, the sealing ring is arranged between the main bearing and the partition, and the sealing ring is arranged between the secondary bearing and the high-pressure shell.

13. The compressor for a vehicle according to any one of claims 1-12, wherein, The refrigerant used by the compressor is carbon dioxide.

14. A vehicle, wherein, A compressor for a vehicle according to any one of claims 1-13. A compressor for a vehicle according to any one of claims 1-13.

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