Compressor, air conditioning apparatus, and vehicle

Abstract

The application belongs to the technical field of compression equipment, and particularly relates to a compressor, air conditioning equipment and a vehicle. The compressor comprises a shell, a first bearing and a crankshaft arranged in the shell. One end of the crankshaft is in plug-in fit with the first bearing. A pre-tightening piece is arranged on the outer wall of the one end of the crankshaft. A pre-tightening cavity is formed between the pre-tightening piece and the crankshaft. A flow-through channel for the flow of high-pressure medium and in communication with the pre-tightening cavity is formed in the crankshaft. The outer ring of the first bearing is fixed in the shell. Since the pressure of the high-pressure medium can be effectively controlled and adjusted, the pre-tightening force can be effectively controlled and adjusted by means of the high-pressure medium to the pre-tightening piece. Thus, the pre-tightening force can be always in a reasonable and controllable range, so that the service life of the first bearing is considered and the working noise of the compressor is effectively reduced.

Description

Technical Field

[0001] The present application belongs to the technical field of compression equipment, and in particular relates to a compressor, air-conditioning equipment and a vehicle. Background Art

[0002] Existing automobile air conditioning systems are usually equipped with a compressor. The crankshaft in the compressor is generally supported by bearings. However, due to the gap between the rolling elements and the inner and outer rings of the bearings, when the crankshaft rotates at high speed, the bearings will generate large vibrations and noise, thereby increasing the overall operating noise of the compressor and affecting the user experience.

[0003] To reduce this noise, the current common practice is to preload the bearings. This existing preloading method involves adding a compression spring between the crankshaft and the inner ring of the bearing. This compression spring limits the friction between the inner ring and the rolling elements of the bearing. However, using a compression spring for preloading presents the problem of difficulty controlling the preload force applied by the compression spring to the bearing. Excessive preload force can shorten the bearing lifespan, while too little preload can hinder bearing vibration and noise control, hindering compressor noise suppression. Summary of the Invention

[0004] The purpose of the embodiments of the present application is to provide a compressor, air-conditioning equipment and vehicle, aiming to solve the technical problem that the bearings used to support the crankshaft of the existing compressor are difficult to effectively pre-tighten, resulting in the difficulty in suppressing the vibration and noise of the bearings and reducing their lifespan.

[0005] To achieve the above objectives, the technical solution adopted in this application is:

[0006] In a first aspect, a compressor is provided, comprising a housing, a first bearing arranged in the housing, and a crankshaft, one end of the crankshaft being plugged into and fitted with the first bearing, a pre-tightening member being provided on an outer wall of one end of the crankshaft, a pre-tightening chamber being formed between the pre-tightening member and the crankshaft, a flow channel being formed in the crankshaft for circulating a high-pressure medium and communicating with the pre-tightening chamber, and an outer ring of the first bearing being fixed in the housing.

[0007] Optionally, a fixing ring is formed on the inner wall of the shell, and a limiting ring step is provided on the inner wall of the fixing ring. The outer ring of the first bearing is embedded in the fixing ring, and the end face of the outer ring facing away from the preloaded part abuts against the step surface of the limiting ring step.

[0008] Optionally, the compressor further includes a bracket connected to one end of the casing, and a second bearing arranged on the bracket, a bearing cavity is formed in the bracket, the second bearing is arranged in the bearing cavity, and the other end of the crankshaft is plugged into the second bearing; a bearing cavity connected to the circulation channel is formed in the bracket, the second bearing is located in the bearing cavity, and the high-pressure medium can be transported to the circulation channel through the bearing cavity.

[0009] Optionally, the compressor further includes a pressure-limiting valve, which is disposed on the bracket and is used to drain the high-pressure medium in the bearing cavity to outside the bearing cavity when the pressure of the high-pressure medium in the bearing cavity is greater than a preset pressure value.

[0010] Optionally, the preload member includes a main body and an assembly ring portion formed on one side of the main body, the main body sealing sleeve is arranged on the crankshaft, the crankshaft passes through the assembly ring portion, and the crankshaft has a ring platform protruding radially along the position corresponding to the assembly ring portion, the main body, the assembly ring portion and the ring platform together form the preload cavity, and a seal is arranged between the ring platform and the assembly ring portion.

[0011] Optionally, a first annular groove is provided on the outer peripheral surface of one side of the annular platform along the circumferential direction, and a first sealing ring is provided in the first annular groove for abutting against the assembly ring portion to form a seal.

[0012] Optionally, a second annular groove is formed on the inner peripheral wall of the main body, and a second sealing ring is provided in the second annular groove for abutting against the outer wall of the crankshaft to form a seal.

[0013] Optionally, the circulation channel includes a main channel and a secondary channel, the main channel is arranged along the axial direction of the crankshaft and is connected to the bearing cavity, the secondary channel is arranged along the radial direction of the crankshaft, and the preload cavity is connected to the main channel through the secondary channel.

[0014] Optionally, the crankshaft includes a main shaft and a secondary shaft, the circulation channel is opened in the main shaft and arranged along the axial direction of the main shaft, the first bearing is sleeved on the secondary shaft, the preloaded member is formed on the secondary shaft, and the preloaded member and the main shaft facing one end of the secondary shaft together form the preloaded cavity, and the end of the main shaft facing away from the preloaded member is plugged into the second bearing.

[0015] Optionally, the preload member includes a main body and a covering ring portion formed on the side of the main body facing the main shaft, the covering ring portion covers the end of the main shaft facing the main body, and is sealed to the outer wall of the main shaft, and the covering ring portion, the main body and the end face of the secondary shaft facing the main shaft together form the preload cavity.

[0016] Optionally, a third ring groove is formed in the main shaft corresponding to the position of the cover ring part, and a third sealing ring for forming a seal by abutting against the cover ring part is arranged in the third ring groove.

[0017] Compared with the prior art, the compressor provided in the embodiments of the present application has at least the following beneficial effects: the compressor provided in the embodiments of the present application is provided with a pre-tightening member on the outer wall of the crankshaft, and a pre-tightening cavity is formed between the pre-tightening member and the crankshaft. Thus, the pre-tightening member can be pushed by high-pressure medium flowing into the pre-tightening cavity through the flow-through channel in the crankshaft, so that the pre-tightening member exerts a pre-tightening force on the inner ring of the first bearing in the axial direction parallel to the crankshaft. At the same time, since the outer ring of the first bearing is fixed to the housing, the inner ring and the outer ring of the first bearing simultaneously exert pre-tightening forces in opposite directions on the rolling elements of the first bearing, thereby significantly reducing the gap between the rolling elements and the inner ring and the outer ring of the first bearing, and further reducing the overall working noise of the compressor. Since the pressure of the high-pressure medium can be effectively controlled and adjusted, the pre-tightening force provided to the pre-tightening member by means of the high-pressure medium can be effectively controlled and adjusted, so that the pre-tightening force is always within a reasonable and controllable range, thereby balancing the service life of the first bearing and effectively reducing the working noise of the compressor.

[0018] The second aspect provides an air conditioning device comprising the compressor.

[0019] Compared with the prior art, the air conditioning device provided in the embodiments of the present application has at least the following beneficial effects: the air conditioning device provided in the embodiments of the present application comprises the compressor described above, and the compressor described above controls the pre-tightening force of the pre-tightening member pre-tightening the crankshaft by introducing high-pressure medium, so that the pre-tightening force between the crankshaft and the first bearing is adjustable, thereby providing a suitable pre-tightening force between the crankshaft and the first bearing, further ensuring the service life of the first bearing, effectively reducing the working noise of the compressor, improving the quality and reliability of the air conditioning device, and reducing the working noise of the air conditioning device.

[0020] The third aspect provides a vehicle comprising the air conditioning device.

[0021] Compared with the prior art, the vehicle provided in the embodiments of the present application has at least the following beneficial effects: the vehicle provided in the embodiments of the present application comprises the air conditioning device described above, and the air conditioning device described above can ensure the quality and reliability thereof while reducing the working noise thereof, thereby helping to control the noise of the vehicle, improving the driving quality of the vehicle, and enhancing the user product experience of the vehicle. BRIEF DESCRIPTION OF DRAWINGS

[0022] In order to more clearly illustrate the technical solutions in the embodiments of the present application, the following briefly introduces the drawings required for use in the embodiments or descriptions of the prior art. Obviously, the drawings described below are only some embodiments of the present application. For ordinary technicians in this field, other drawings can be obtained based on these drawings without any creative work.

[0023] Figure 1 A schematic diagram of the structure of a compressor provided in an embodiment of the present application;

[0024] Figure 2 for Figure 1 A partial enlarged view of point A in the middle;

[0025] Figure 3 A schematic structural diagram of a preload member and a crankshaft of a compressor provided in an embodiment of the present application;

[0026] Figure 4 Another structural schematic diagram of a compressor provided in an embodiment of the present application;

[0027] Figure 5 for Figure 4 A partial enlarged view of point B in the middle;

[0028] Figure 6 Another structural schematic diagram of the preload member and crankshaft of the compressor provided in an embodiment of the present application.

[0029] Among them, the reference numerals in the figures are:

[0030] 11—housing 12—bracket 13—second bearing

[0031] 14—Bearing cavity 15—Pressure limiting valve 16—Fixed ring

[0032] 20—crankshaft 21—preload element 22—preload chamber

[0033] 23 - circulation channel 24 - main body 25 - assembly ring

[0034] 26 - ring platform 27 - main shaft 28 - secondary shaft

[0035] 30 - first bearing 31 - inner ring 32 - outer ring

[0036] 33 - rolling element 111 - air intake hole 112 - static disk component

[0037] 113 - Oil distribution pipe 114 - Oil pool 115 - Throttle assembly

[0038] 211—Main body 212—Covering ring 231—Main channel

[0039] 232 - sub passage 241 - second ring groove 242 - second sealing ring

[0040] 261 - first ring groove 262 - first sealing ring 271 - third ring groove

[0041] 272 - third sealing ring 273 - plug-like portion. DETAILED DESCRIPTION

[0042] Embodiments of the present application are described below in detail, examples of which are shown in the accompanying drawings, wherein the same or similar notations represent the same or similar elements or elements having the same or similar functions throughout. Hereinafter, the embodiments of the present application are described by referring to the accompanying drawings, which help to understand the present application. Figures 1 to 6 The described embodiments are examples and are intended to be illustrative of the present application and are not to be understood as limiting the present application.

[0043] In the description of the present application, it needs to be understood that the terms "length", "width", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer" and the like indicate the orientation or positional relationship based on the orientation or positional relationship shown in the drawings, and are only for the purpose of facilitating the description of the present application and simplifying the description, and therefore cannot be understood as indicating or implying that the device or element 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 addition, the terms "first", "second" are only for descriptive purposes and cannot be understood as indicating or implying relative importance or implicitly indicating the number of the technical features indicated. Therefore, the features defined with "first", "second" can explicitly or implicitly include one or more of the features. In the description of the present application, the meaning of "a plurality of" is two or more, unless otherwise explicitly specified and limited.

[0045] In the present application, unless otherwise explicitly specified and limited, the terms "mounting", "connection", "connection", "fixing" and the like should be understood broadly, for example, it can be fixedly connected, or it can be detachably connected, or it can be integrated; it can be mechanically connected, or it can be electrically connected; it can be directly connected, or it can be indirectly connected through an intermediate medium; it can be the internal communication of two elements or the interaction relationship between 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.

[0046] As Figures 1 to 3 shown, the embodiments of the present application provide a compressor, an air conditioning device and a vehicle, in the present embodiment, the compressor can be a scroll compressor in particular, which can be applied to the above-mentioned air conditioning device, and the above-mentioned air conditioning device can be applied to the vehicle.

[0047] The following is an explanation of the compressor provided by an embodiment of the present application: In this embodiment, the compressor includes a housing 11, a first bearing 30 disposed within the housing 11, and a crankshaft 20. A preload member 21 is disposed on the outer wall of one end of the crankshaft 20, forming a preload chamber 22 between the preload member 21 and the crankshaft 20. A flow channel 23 is formed within the crankshaft 20 for circulating a high-pressure medium and communicating with the preload chamber 22. The preload member 21 is configured to apply a preload force along the axial direction of the first bearing 30 toward the inner ring 31 of the first bearing 30 under the pressure of the high-pressure medium within the preload chamber 22. The outer ring 32 of the first bearing 30 is fixed within the housing 11. This is equivalent to the inner ring 31 and outer ring 32 of the first bearing 30 simultaneously applying preload forces in opposite directions to the rolling elements of the first bearing 30, thereby effectively preloading the first bearing 30.

[0048] The high-pressure medium may be high-pressure lubricating oil or high-pressure gas, which may come from the inside of the compressor or an external oil supply or gas supply device.

[0049] The following is a further explanation of the compressor provided by the embodiment of the present application: The compressor provided by the embodiment of the present application, by arranging a preload member 21 on the outer wall of the crankshaft 20, and forming a preload chamber 22 between the preload member 21 and the crankshaft 20, so that when the first bearing 30 needs to be preloaded, the high-pressure medium can be drained into the preload chamber 22 through the circulation channel 23 in the crankshaft 20. In this way, the preload member 21 can apply a preload force to the inner ring 31 of the first bearing 30 in a direction parallel to the axis of the crankshaft 20 under the push of the high-pressure medium in the preload chamber 22. At the same time, since the outer ring 32 of the first bearing 30 is fixed in the housing 11, it is equivalent to the inner ring 31 and the outer ring 32 of the first bearing 30 simultaneously applying preload forces in opposite directions to the rolling elements of the first bearing 30, thereby significantly reducing the gap between the rolling elements of the first bearing 30 and the inner ring 31 and the outer ring 32, thereby reducing the overall operating noise of the compressor. Since the pressure of the high-pressure medium can be effectively controlled and adjusted, the preload force can be effectively controlled and adjusted by providing the preload force to the preload member 21 with the help of the high-pressure medium. In this way, the preload force can always be within a reasonable and controllable range, thereby taking into account the service life of the first bearing 30 and effectively reducing the operating noise of the compressor.

[0050] The air-conditioning equipment provided in the embodiment of the present application includes the above-mentioned compressor, and the above-mentioned compressor controls the preload force of the preload member 21 therein for preloading the crankshaft 20 by introducing a high-pressure medium, thereby achieving adjustable preload force between the crankshaft 20 and the first bearing 30, thereby being able to provide a suitable preload force between the crankshaft 20 and the first bearing 30, thereby effectively reducing the operating noise of the compressor while ensuring the service life of the first bearing 30, thereby improving the quality and reliability of the air-conditioning equipment while also reducing the operating noise of the air-conditioning equipment.

[0051] An embodiment of the present application also provides a vehicle comprising the above-mentioned air-conditioning device.

[0052] The vehicles in the embodiments of the present application may be new energy vehicles that use unconventional automotive fuels as their power source, or they may be new energy vehicles that use conventional automotive fuels but employ novel onboard power units. Specifically, new energy vehicles may include hybrid electric vehicles, pure electric vehicles, or fuel cell electric vehicles, and they may also be vehicles that use high-efficiency energy storage devices such as supercapacitors, flywheel batteries, or flywheel energy storage devices as their power source.

[0053] Optionally, the vehicle in the embodiment of the present application may also be a vehicle that uses conventional vehicle fuel as a power source, such as gasoline, diesel, natural gas, liquefied petroleum gas, ethanol gasoline, methanol, or dimethyl alcohol as a power source.

[0054] The vehicle provided in the embodiment of the present application includes the above-mentioned air-conditioning equipment, and the above-mentioned air-conditioning equipment can reduce its operating noise while ensuring its quality reliability, thereby also contributing to vehicle noise control, improving the vehicle's driving quality, and enhancing the vehicle's user product experience.

[0055] In other embodiments of the present application, Figure 1 and Figure 4 As shown, a fixing ring 16 is formed on the inner wall of the shell, and a limiting ring step is provided on the inner wall of the fixing ring 16. The outer ring 32 of the first bearing 30 is embedded in the fixing ring 16, and the end face of the outer ring 32 facing away from the preload member 21 abuts against the step surface of the limiting ring step.

[0056] Specifically, by providing the fixing ring 16 and embedding the outer ring 32 of the first bearing 30 in the fixing ring 16, the outer ring 32 of the first bearing 30 is effectively fixed. The outer ring 32 of the first bearing 30 may preferably, but is not limited to, have an interference fit with the fixing ring 16.

[0057] Furthermore, by making the end face of the outer ring 32 facing away from the preload member 21 abut against the step surface of the limiting ring step of the fixing ring 16, effective limitation of the outer ring 32 is achieved. In this way, the outer ring 32 and the inner ring 31 of the first bearing 30 are subjected to two relative preload forces along the axial direction of the first bearing 30, so that the outer ring 32 and the inner ring 31 tend to move relative to the rolling element 33 of the first bearing 30, thereby effectively reducing the gap between the outer ring 32 and the inner ring 31 relative to the rolling element 33, thereby reducing the operating noise of the first bearing 30 and the operating noise of the compressor.

[0058] Alternatively, the fixing ring 16 may be integrally cast with the housing 11. This reduces the manufacturing costs of the fixing ring 16 and the housing 11 while also ensuring the strength of the connection between the fixing ring 16 and the housing 11. Furthermore, integral casting allows fixing rings 16 having complex configurations to be formed at a lower cost, thereby reducing the overall manufacturing cost of the compressor.

[0059] Optionally, the fixing ring 16 can also be detachably connected to the shell 11 by connecting parts such as bolts, which can improve the convenience of disassembly and assembly of the fixing ring 16. Then, when the fixing ring 16 is damaged and needs to be replaced, it only needs to be removed from the shell 11 and replaced, without having to replace it together with the shell 11, thereby significantly reducing the disassembly and maintenance cost of the compressor.

[0060] In other embodiments of the present application, Figure 1 and Figure 4 As shown, the compressor also includes a bracket 12 connected to one end of the shell 11, and a second bearing 13 arranged on the bracket 12, a bearing cavity 14 is formed in the bracket 12, the second bearing 13 is arranged in the bearing cavity 14, the other end of the crankshaft 20 (that is, the end of the crankshaft 20 facing away from the preloaded member 21) is plugged into the second bearing 13, a bearing cavity 14 connected to the circulation channel 23 is formed in the bracket 12, the second bearing is located in the bearing cavity 14, and the high-pressure medium can be transported to the circulation channel 23 through the bearing cavity.

[0061] Specifically, by providing the bracket 12 and disposing the second bearing 13 in the bearing cavity 14 within the bracket 12, the crankshaft 20 is configured such that the end proximate to the preload element 21 and the end facing the preload element 21 are respectively pluggably engaged with the second bearing 13 and the first bearing 30, thereby achieving rotation within the housing 11. The high-pressure medium within the housing 11 can enter the circulation channel 23 through the bearing cavity 14 and then enter the preload cavity 22 through the circulation channel 23, thereby providing the preload element 21 with a preload force applied to the inner ring 31 of the first bearing 30.

[0062] Optionally, when the high-pressure medium comes from the shell 11, its specific supply method is: when the compressor is working, low-pressure refrigerant gas is sucked in from an external device (such as a refrigeration system) through the intake hole 111 of the shell 11. At this time, the low-pressure refrigerant gas can be compressed by the compression part of the compressor to become high-pressure gas, and discharged to the exhaust area of ​​the static disk component 112 of the shell 11. In this process, the high-pressure gas will be mixed with the lubricating oil of the shell 11, thereby forming an oil-gas mixture. The oil-gas mixture is separated from the oil under the action of the oil distribution pipe 113 of the shell 11, and then the gas therein is discharged from the exhaust area of ​​the shell 11 to the outside of the compressor. The separated high-pressure lubricating oil can fall into the oil pool 114, and the high-pressure lubricating oil in the oil pool 114 passes through the throttling assembly 115 provided on the static disk component 112 and enters the bearing cavity 14, and then enters the circulation channel 23 through the bearing cavity 14, and then enters the pre-tightening cavity 22 through the circulation channel 23, and provides pre-tightening force to the pre-tightening member 21 as a high-pressure medium. In this way, on the one hand, the lubricating oil in the compressor itself is utilized to achieve self-sufficiency of the high-pressure medium, saving the cost of pre-tightening the first bearing 30. On the other hand, the internal space of the crankshaft 20 and the bracket 12 is fully utilized to achieve a hidden layout of the high-pressure medium supply path in the shell 11, providing considerable space for the installation of other components in the shell 11.

[0063] Optionally, the pressure value when the low-pressure refrigerant gas enters the housing 11 is set to P0, and the pressure value when the high-pressure lubricating oil enters the bearing cavity 14 and the circulation channel 23 is set to P1. In this case, P1 is the pressure value of the high-pressure lubricating oil in the preload cavity 22, the circulation channel 23, and the bearing cavity 14, and is also the pressure value acting on the preload member 21. At the same time, the preload force on the first bearing 30 is set to F, then F satisfies the following relationship:

[0064] F = S1*P1-S0*P0;

[0065] S1 is the wall area of ​​the preload cavity 22 facing the preload member 21 , also known as the effective pressure-bearing area, and S0 is the end surface area of ​​the crankshaft 20 close to the preload member 21 .

[0066] The above formula indicates that the pressure obtained by subtracting the pressure in the opposite direction of the pressure exerted by the low-pressure refrigerant gas toward the high-pressure medium on the crankshaft 20 itself from the pressure borne by the preload 21 from the high-pressure medium is the preload force applied by the preload 21 to the inner ring 31 of the first bearing 30.

[0067] In other embodiments of the present application, Figure 1 and Figure 4As shown, the housing 11 further includes a pressure limiting valve 15 , which is disposed on the bracket 12 and is used to drain the high-pressure medium in the bearing cavity 14 to the outside of the bearing cavity 14 when the pressure of the high-pressure medium in the bearing cavity 14 is greater than a preset pressure value.

[0068] Specifically, by arranging a pressure-limiting valve 15 on the bracket 12, when the pressure of the high-pressure medium is greater than a preset pressure value, the pressure-limiting valve 15 can start to discharge the pressure, and drain the excess high-pressure medium to other cavities such as the shell 11, thereby reducing the pressure value input to the preload member 21. In this way, the preload force applied by the preload member 21 to the inner ring 31 of the first bearing 30 is always maintained at a reasonable level, thereby achieving effective protection of the first bearing 30.

[0069] In other embodiments of the present application, Figures 1 to 3 As shown, as a form of pre-tightening of the crankshaft 20 and the first bearing 30, the pre-tightening member 21 includes a main body 24 and an assembly ring portion 25 formed on one side of the main body 24. The main body 24 is sealed and sleeved on the crankshaft 20. The crankshaft 20 passes through the assembly ring portion 25, and a ring platform 26 is formed at a position of the crankshaft 20 corresponding to the assembly ring portion 25 along its radial direction. The main body 24, the assembly ring portion 25 and the ring platform 26 together form a pre-tightening cavity 22, and a seal is set between the ring platform 26 and the assembly ring portion 25.

[0070] Specifically, as a first specific arrangement of the preload member 21 and the crankshaft 20, its main body 24 is sleeved on the crankshaft 20 to facilitate axial sliding along the crankshaft 20, thereby abutting against the inner ring 31 of the first bearing 30. The assembly ring 25, together with the main body 24 and the annular platform 26 provided on the outer wall of the crankshaft 20, forms a preload cavity 22. By abutting against the first sealing ring 262, the preload cavity 22 is effectively sealed. This not only forms an effective preload structure for the first bearing 30, but also enables a detachable connection of the preload member 21 with respect to the crankshaft 20, thereby improving the convenience and cost-effectiveness of the removal, replacement, and maintenance of the preload member 21.

[0071] In other embodiments of the present application, Figures 1 to 3 As shown, a first annular groove 261 is formed on the outer peripheral surface of one side of the annular platform 26 along the circumferential direction, and a first sealing ring 262 for contacting with the assembly ring portion 25 to form a seal is provided in the first annular groove 261 .

[0072] Specifically, by opening a first annular groove 261 on the outer peripheral surface of one side of the annular platform 26 and arranging a first sealing ring 262 in the first annular groove 261, the first sealing ring 262 can achieve sealing between the annular platform 26 and the assembly ring portion 25, thereby ensuring the sealing performance of the preload chamber 22, preventing the high-pressure medium in the preload chamber 22 from overflowing from the preload chamber 22, and further ensuring the stability of the pressure provided by the high-pressure medium to the preload force.

[0073] In other embodiments of the present application, Figure 3 As shown, a second annular groove 241 is formed on the inner peripheral wall of the main body 24 (i.e., the wall surface of the main body 24 facing the crankshaft 20 ), and a second sealing ring 242 for contacting the outer wall of the crankshaft 20 is provided in the second annular groove 241 .

[0074] Specifically, by opening a second annular groove 241 on the main body 24 and arranging a second sealing ring 242 in the second annular groove 241, the second sealing ring 242 and the wall surface of the crankshaft 20 are abutted against each other, thereby realizing the sealing of the main body 24 relative to the crankshaft 20, thereby further improving the sealing performance of the preload chamber 22, further avoiding the high-pressure medium in the preload chamber 22 from overflowing from the preload chamber 22, and thus enabling the high-pressure medium to provide pressure to the preload force more stably.

[0075] In other embodiments of the present application, Figure 2 and Figure 3 As shown, the circulation channel 23 includes a main channel 231 and a secondary channel 232. The main channel 231 is arranged along the axial direction of the crankshaft 20 and is connected to the bearing cavity 14. The secondary channel 232 is arranged along the radial direction of the crankshaft 20, and the preload cavity 22 is connected to the main channel 231 through the secondary channel 232.

[0076] Specifically, as a form of communication between the circulation channel 23 and the preload chamber 22, the circulation channel 23 includes a main channel 231 and a secondary channel 232. This allows the high-pressure medium to flow from the bearing cavity 14 into the main channel 231, then reach the position corresponding to the preload chamber 22 through the main channel 231, and then enter the preload chamber 22 through the secondary channel 232 opened along the radial direction of the crankshaft 20. This achieves smooth transportation of the high-pressure medium within the crankshaft 20 and conceals the transportation path, avoiding the need for additional dedicated high-pressure medium drainage pipelines.

[0077] Optionally, as another form of connection between the circulation channel 23 and the pre-tightening chamber 22, a dedicated high-pressure medium drainage pipeline is also arranged on the wall of the crankshaft 20, so that it replaces the secondary channel 232 and the main channel 231 arranged in the crankshaft 20, and is directly connected to the pre-tightening chamber 22 and the bearing chamber 14, thereby effectively reducing the processing cost of the crankshaft 20.

[0078] In other embodiments of the present application, Figures 4-6As shown, the crankshaft 20 includes a main shaft 27 and a secondary shaft 28, the circulation channel 23 is opened in the main shaft 27 and arranged along the axial direction of the main shaft 27, the first bearing 30 is sleeved on the secondary shaft 28, the preload member 21 is formed on the secondary shaft 28, and the preload member 21 and the end of the main shaft 27 facing the secondary shaft 28 are combined to form a preload cavity 22, and the end of the main shaft 27 facing away from the preload member 21 is plugged into the second bearing 13.

[0079] Specifically, as a second specific setting form of the preload member 21 and the crankshaft 20, the crankshaft 20 can be divided into a main shaft 27 and a secondary shaft 28 that are set at intervals, wherein the preload member 21 is formed on the secondary shaft 28, specifically formed on the end of the secondary shaft 28 close to the main shaft 27, so that the preload member 21 and the end of the main shaft 27 close to the secondary shaft 28 can be combined to form a preload chamber 22. On the one hand, the circulation channel 23 can be directly connected to the preload chamber 22, and there is no need to divide it into a main channel 231 and a secondary channel 232, thereby reducing the cost of opening the circulation channel 23. On the other hand, the preload member 21 can be directly integrally formed on the secondary shaft 28, thereby also reducing the processing and manufacturing cost of the preload member 21.

[0080] In other embodiments of the present application, Figure 5 and Figure 6 As shown, the preload member 21 includes a main body 211 and a covering ring portion 212 formed on the side of the main body 211 facing the main shaft 27. The covering ring portion 212 covers the end of the main shaft 27 facing the main body 211 and is in sealing contact with the outer wall of the main shaft 27. The covering ring portion 212, the main body 211, and the end surface of the secondary shaft 28 facing the main shaft 27 together form a preload cavity 22. Specifically, by ensuring that the covering ring portion 212 is in sealing contact with the outer wall of the main shaft 27, the sealing performance of the preload cavity 22 formed by the main body, the covering ring portion 212, the secondary shaft 28, and the main shaft 27 is also ensured.

[0081] In other embodiments of the present application, Figure 6 As shown, a third annular groove 271 is formed on the outer wall of the main shaft 27 at a position corresponding to the covering ring portion 212 , and a third sealing ring 272 is provided in the third annular groove 271 for contacting with the covering ring portion 212 to form a seal.

[0082] Specifically, by providing a third annular groove 271 on the main shaft 27 and allowing the third sealing ring 272 in the third annular groove 271 to abut against the cover ring portion 212, the preload chamber 22 is sealed. Furthermore, by providing the third annular groove 271 on the outer wall of the main shaft 27, rather than on the side wall of the cover ring portion 212 facing the main shaft 27, the cover ring portion 212 has sufficient structural strength, thereby ensuring the overall structural strength of the preload member 21.

[0083] Optionally, a plug-shaped portion 273 is formed at a position on the main shaft 27 corresponding to the cover ring portion 212, and the third annular groove 271 is formed on the plug-shaped portion 273. By providing the plug-shaped portion 273, the plug-shaped portion 273 can be partially or completely inserted into the cover ring portion 212, thereby achieving the connection between the main shaft 27 and the cover ring portion 212, and further improving the sealing between the main shaft 27 and the preload member 21.

[0084] The above are only preferred embodiments of the present application and are not intended to limit the present application. Any modifications, equivalent replacements, and improvements made within the spirit and principles of the present application should be included in the scope of protection of the present application.

Claims

1. A compressor comprising a housing, a first bearing disposed in the housing, and a crankshaft, wherein one end of the crankshaft is plug-fitted to the first bearing, and wherein: A preload member is provided on the outer wall of one end of the crankshaft, a preload chamber is formed between the preload member and the crankshaft, a circulation channel for high-pressure medium to circulate and communicate with the preload chamber is formed in the crankshaft, and the outer ring of the first bearing is fixed in the housing; the compressor also includes a bracket connected to one end of the housing, and a second bearing provided on the bracket, and the other end of the crankshaft is plugged into and fitted with the second bearing; a bearing chamber connected to the circulation channel is formed in the bracket, the second bearing is located in the bearing chamber, and the high-pressure medium can be transported to the circulation channel through the bearing chamber; the high-pressure lubricating oil in the oil pool enters the bearing chamber through the throttling assembly provided on the stator disc component, then enters the circulation channel through the bearing chamber, and then enters the preload chamber through the circulation channel, and provides a preload force to the preload member as the high-pressure medium, which pushes the preload member so that the preload member applies a preload force to the inner ring of the first bearing along the axial direction parallel to the crankshaft, and the outer ring of the first bearing is fixed to the housing.

2. The compressor according to claim 1, characterized in that: A fixing ring is formed on the inner wall of the shell, and a limiting ring step is provided on the inner wall of the fixing ring. The outer ring of the first bearing is embedded in the fixing ring, and the end face of the outer ring facing away from the preloaded member abuts against the step surface of the limiting ring step.

3. The compressor according to claim 1, characterized in that: The compressor further includes a pressure-limiting valve, which is disposed on the bracket and is used to drain the high-pressure medium in the bearing cavity to outside the bearing cavity when the pressure of the high-pressure medium in the bearing cavity is greater than a preset pressure value.

4. The compressor according to any one of claims 1 to 3, characterized in that: The preload member includes a main body and an assembly ring portion formed on one side of the main body. The main body sealing sleeve is arranged on the crankshaft. The crankshaft passes through the assembly ring portion, and the crankshaft has a ring platform protruding along its radial direction at a position corresponding to the assembly ring portion. The main body, the assembly ring portion and the ring platform together form the preload cavity, and a seal is arranged between the ring platform and the assembly ring portion.

5. The compressor according to claim 4, characterized in that: A first annular groove is provided on the outer peripheral surface of one side of the annular platform along the circumferential direction, and a first sealing ring is provided in the first annular groove for contacting with the assembly ring portion to form a seal.

6. The compressor according to claim 4, characterized in that: A second annular groove is formed on the inner peripheral wall of the main body, and a second sealing ring is provided in the second annular groove for contacting with the outer wall of the crankshaft to form a seal.

7. The compressor according to claim 4, characterized in that: The circulation channel includes a main channel and a secondary channel. The main channel is arranged along the axial direction of the crankshaft and is connected to the bearing cavity. The secondary channel is arranged along the radial direction of the crankshaft, and the preload cavity is connected to the main channel through the secondary channel.

8. The compressor according to any one of claims 1 or 3, characterized in that: The crankshaft includes a main shaft and a secondary shaft, the circulation channel is opened in the main shaft and arranged along the axial direction of the main shaft, the first bearing is sleeved on the secondary shaft, the preloaded piece is formed on the secondary shaft, and the preloaded piece and the main shaft facing one end of the secondary shaft together form the preloaded cavity, and the end of the main shaft facing away from the preloaded piece is plugged into the second bearing.

9. The compressor according to claim 8, characterized in that: The preload member includes a main body and a covering ring portion formed on the side of the main body facing the main shaft. The covering ring portion covers the end of the main shaft facing the main body and is sealed with the outer wall of the main shaft. The covering ring portion, the main body and the end face of the secondary shaft facing the main shaft together form the preload cavity.

10. The compressor according to claim 9, characterized in that: A third annular groove is formed on the main shaft at a position corresponding to the covering annular portion. A third sealing ring is provided in the third annular groove for contacting with the covering annular portion to form a seal.

11. An air conditioning device, characterized in that: Including the compressor according to any one of claims 1 to 10.

12. A vehicle, characterized in that: Including the air conditioning equipment according to claim 11.

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