Compressor, air conditioner and vehicle

Abstract

The utility model discloses a kind of compressor, air conditioner and vehicle, compressor includes: crankshaft, crankshaft includes output shaft section;Cylinder assembly, cylinder assembly includes first bearing, cylinder structure and second bearing, first bearing is equipped with first bearing hole, second bearing is equipped with second bearing hole, output shaft section is rotatably worn in first bearing hole, cylinder structure and second bearing hole, output shaft section is used to reciprocating motion of piston piece in cylinder structure is promoted;Wherein, the inner wall of second bearing hole is at least part is structured as avoidance section, avoidance section and the outer peripheral wall of output shaft section are spaced apart distribution.The compressor of the utility model embodiment, the compression function of compressor can be realized, and second bearing and crankshaft can be effectively avoided in avoidance section contact and produce friction, so as to reduce the friction power consumption of compressor, improve the energy efficiency of compressor, and second bearing can be reduced the abrasion of crankshaft, prolong the service life of crankshaft and second bearing, improve the reliability of compressor work.

Description

Technical Field

[0001] This utility model relates to the field of vehicle manufacturing technology, and in particular to a compressor, an air conditioner having the compressor, and a vehicle having the compressor or the air conditioner. Background Technology

[0002] The pump body of the electric rotor compressor is supported by three points: the bracket, the rolling bearing of the crankshaft small shaft, and the pump body auxiliary bearing. When the compressor compresses gas at high speed, the crankshaft will wobble and deform due to inertia and gas force. Since the clearance between the crankshaft and the bearing is small, this deformation will exceed the clearance between the bearing and the crankshaft, resulting in wear on the crankshaft auxiliary shaft end and the corresponding part of the inner diameter of the auxiliary bearing. There is room for improvement. Utility Model Content

[0003] This utility model aims to solve at least one of the technical problems existing in the prior art. To this end, this utility model proposes a compressor that can realize the compression function of the compressor and can effectively avoid friction between the second bearing and the crankshaft in the avoidance section, thereby reducing the frictional power consumption of the compressor, improving the energy efficiency of the compressor, reducing the wear of the crankshaft and the second bearing, extending the service life of the crankshaft and the second bearing, and improving the reliability of the compressor operation.

[0004] A compressor according to an embodiment of the present invention includes: a crankshaft, the crankshaft including an output shaft section; a cylinder assembly, the cylinder assembly including a first bearing, a cylinder structure and a second bearing, the first bearing having a first bearing hole, the second bearing having a second bearing hole, the output shaft section being rotatably disposed through the first bearing hole, the cylinder structure and the second bearing hole, the output shaft section being used to drive a piston in the cylinder structure to reciprocate; wherein, at least a portion of the inner wall of the second bearing hole is configured as a clearance section, the clearance section being spaced apart from the outer peripheral wall of the output shaft section.

[0005] According to the present invention, the compressor, by passing an output shaft section through a first bearing hole and a second bearing hole, allows the first and second bearings to support the crankshaft, ensuring the reliability of the crankshaft's operation and enabling the crankshaft to rotate relative to the first and second bearings. Simultaneously, by passing the output shaft section through a cylinder structure, the output shaft section can drive a piston to reciprocate, thereby converting the crankshaft's rotational motion into reciprocating motion to achieve the compressor's compression function. Furthermore, at least a portion of the inner wall of the second bearing hole is constructed as a clearance section, which is spaced apart from the outer peripheral wall of the output shaft section. This effectively prevents the second bearing and crankshaft from contacting and rubbing against each other in the clearance section, thereby reducing the compressor's frictional power consumption, improving its energy efficiency, reducing wear on the crankshaft and second bearing, extending their service life, and enhancing the compressor's operational reliability.

[0006] According to some embodiments of the compressor of the present invention, the clearance section is located in the region of the inner wall of the second bearing hole away from the cylinder structure; wherein, the crankshaft further includes an input shaft section connected to the output shaft section, the input shaft section is used to connect to a power source, and the end face of the output shaft section away from the input shaft section is located in the clearance section and spaced apart from the end of the clearance section.

[0007] According to some embodiments of the compressor of the present invention, the inner wall of the second bearing hole further includes a mating section, the outer peripheral wall of the output shaft section is fitted and supported by the mating section, and the clearance section and the mating section are distributed along the axial direction of the second bearing hole.

[0008] According to some embodiments of the compressor of the present invention, the inner diameter of the mating section is smaller than the inner diameter of the clearance section; and / or, the mating section is further provided with an oil guide groove.

[0009] According to some embodiments of the compressor of the present invention, a transition chamfer is provided between the clearance section and the mating section; or, the clearance section and the mating section are connected axially along the second bearing hole.

[0010] According to some embodiments of the present invention, the inner diameter of the clearance section is fixed in the direction away from the mating section; or, the inner diameter of the clearance section gradually increases in the direction away from the mating section.

[0011] According to some embodiments of the compressor of the present invention, the depth of the clearance section in the radial direction of the second bearing hole is d, and satisfies: 0.5mm≤d≤1.5mm.

[0012] According to some embodiments of the compressor of the present invention, the axial height of the second bearing is H, and the length of the clearance section in the axial direction of the second bearing is L, and satisfies: 5mm≤L≤0.5H.

[0013] According to some embodiments of the present invention, the compressor has a cylinder structure including at least one cylinder, the at least one cylinder being distributed axially between the first bearing and the second bearing along the crankshaft, the second bearing including a second axial portion and a second radial portion connected axially, the second radial portion being connected to one of the cylinders, the second axial portion being connected to the side of the second radial portion away from the cylinder, and a clearance section being formed on the inner peripheral wall of the second axial portion; and / or, it further includes a first muffler, the first muffler being sleeved outside the first bearing and defining a first muffler cavity together with the first bearing.

[0014] This utility model also proposes an air conditioner.

[0015] The air conditioner according to the present invention includes the compressor described in any of the above embodiments.

[0016] This utility model also proposes a vehicle.

[0017] The vehicle according to the present invention includes the compressor described in any of the above embodiments, or includes the air conditioner described in the above embodiments.

[0018] The vehicle, the air conditioner, and the compressor described above all have the same advantages over the prior art, which will not be elaborated here.

[0019] Additional aspects and advantages of this invention will be set forth in part in the description which follows, and in part will be obvious from the description, or may be learned by practice of the invention. Attached Figure Description

[0020] The above and / or additional aspects and advantages of this utility model will become apparent and readily understood from the description of the embodiments taken in conjunction with the following drawings, in which:

[0021] Figure 1 This is a schematic diagram of the compressor structure according to an embodiment of the present utility model. Figure 1 ;

[0022] Figure 2 This is a schematic diagram of the compressor structure according to an embodiment of the present utility model. Figure 2 ;

[0023] Figure 3 This is a schematic diagram of the structure of the second bearing according to an embodiment of the present utility model. Figure 1 ;

[0024] Figure 4 This is a schematic diagram of the structure of the second bearing according to an embodiment of the present utility model. Figure 2 .

[0025] Figure label:

[0026] Compressor 100,

[0027] Crankshaft 1, Output shaft section 11, Input shaft section 12

[0028] Cylinder assembly 2, first bearing 21, first bearing bore 211, cylinder structure 22, piston 221, cylinder 222, partition 223, second bearing 23, second bearing bore 231, clearance section 2311, mating section 2312, transition chamfer 2313, oil guide groove 232, second axial portion 233, second radial portion 234.

[0029] First silencer 3, first silencer cavity 31. Detailed Implementation

[0030] The embodiments of this utility model are described in detail below. Examples of these embodiments are shown in the accompanying drawings, wherein the same or similar reference numerals denote the same or similar elements or elements having the same or similar functions throughout. The embodiments described below with reference to the accompanying drawings are exemplary and are only used to explain this utility model, and should not be construed as limiting this utility model.

[0031] In the description of this utility model, it should be understood that the terms "center," "longitudinal," "transverse," "length," "width," "thickness," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," "outer," "clockwise," "counterclockwise," "axial," "radial," and "circumferential," etc., indicating the orientation or positional relationship shown in the accompanying drawings, are only for the convenience of describing this utility model and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation of this utility model. Furthermore, features defined with "first" or "second" may explicitly or implicitly include one or more of that feature. In the description of this utility model, unless otherwise stated, "a plurality of" means two or more.

[0032] In the description of this utility model, it should be noted that, unless otherwise explicitly specified and limited, the terms "installation," "connection," and "joining" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral connection; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium; and they can refer to the internal connection of two components. Those skilled in the art can understand the specific meaning of the above terms in this utility model based on the specific circumstances.

[0033] The following is for reference. Figures 1-4 The compressor 100 according to an embodiment of the present invention describes how the output shaft section 11 is inserted into the cylinder structure 22, allowing the output shaft section 11 to drive the piston 221 to reciprocate, thereby converting the rotational motion of the crankshaft 1 into reciprocating motion to achieve the compression function of the compressor 100. Furthermore, at least a portion of the inner wall of the second bearing hole 231 is constructed as a clearance section 2311, which is spaced apart from the outer peripheral wall of the output shaft section 11. This effectively prevents the second bearing 23 from contacting the crankshaft 1 and causing friction in the clearance section 2311, thereby reducing the frictional power consumption of the compressor 100, improving the energy efficiency of the compressor 100, reducing wear on the crankshaft 1 and the second bearing 23, extending the service life of the crankshaft 1 and the second bearing 23, and improving the reliability of the compressor 100.

[0034] like Figure 1As shown, a compressor 100 according to an embodiment of the present invention includes: a crankshaft 1 and a cylinder assembly 2.

[0035] The crankshaft 1 includes an output shaft section 11; the cylinder assembly 2 includes a first bearing 21, a cylinder structure 22, and a second bearing 23. The first bearing 21 has a first bearing hole 211, and the second bearing 23 has a second bearing hole 231. The output shaft section 11 is rotatably disposed through the first bearing hole 211, the cylinder structure 22, and the second bearing hole 231. The output shaft section 11 is used to drive the piston 221 in the cylinder structure 22 to reciprocate. At least a portion of the inner wall of the second bearing hole 231 is constructed as a clearance section 2311, which is spaced apart from the outer peripheral wall of the output shaft section 11.

[0036] Specifically, the compressor 100 is used to compress the volume of gas to increase the gas pressure. The compressor 100 includes a crankshaft 1 and a cylinder assembly 2. The crankshaft 1 is used to convert rotary motion into reciprocating motion, and the cylinder assembly 2 is used to compress the gas. The crankshaft 1 includes an output shaft section 11, and the cylinder assembly 2 includes a first bearing 21, a cylinder structure 22, and a second bearing 23. The first bearing 21 has a first bearing hole 211, and the second bearing 23 has a second bearing hole 231. The output shaft section 11 is rotatably inserted into the first bearing hole 211 and the second bearing hole 231, so that the output shaft section 11 can be engaged with the first bearing 21 and the second bearing 23, allowing the output shaft section 11 to rotate relative to the first bearing 21 and the second bearing 23. The outer peripheral wall of the output shaft section 11 can simultaneously engage with the inner wall of the first bearing hole 211 and the inner wall of the second bearing hole 231, so that the first bearing 21 and the second bearing 23 can simultaneously support the crankshaft 1, ensuring the reliability of the crankshaft 1's operation.

[0037] Meanwhile, the output shaft section 11 is rotatably inserted into the cylinder structure 22, so that the output shaft section 11 can cooperate with the piston 221 in the cylinder structure 22, so that while rotating, it can drive the piston 221 to reciprocate. That is, the output shaft section 11 can convert its own rotational motion into the reciprocating motion of the piston 221, so that the piston 221 can compress the gas while reciprocating, thereby realizing the compression function of the compressor 100.

[0038] Furthermore, at least a portion of the inner wall of the second bearing bore 231 is constructed as a clearance section 2311. The clearance section 2311 is used to avoid at least a portion of the output shaft section 11, preventing the crankshaft 1 and the second bearing 23 from contacting and rubbing at the clearance section 2311. This reduces the frictional power consumption of the compressor 100, improves the energy efficiency of the compressor 100, reduces the wear of the crankshaft 1 and the second bearing 23, extends the service life of the crankshaft 1 and the second bearing 23, improves the reliability of the compressor 100, and allows a portion of the second bearing bore 231 to... Alternatively, all sections 2311 can be designated as clearance sections to increase their length and improve their operational reliability. This can effectively enhance the energy efficiency and operational reliability of the compressor 100. Furthermore, by distributing clearance sections 2311 and the outer peripheral wall of the output shaft section 11 separately, a certain distance can be maintained between them. This ensures that the crankshaft 1 and the second bearing 23 will not come into contact and rub against each other at the clearance section 2311, thereby further improving the operational reliability of the clearance section 2311.

[0039] It should be noted that, due to the relatively long length of the crankshaft 1, it will undergo wobbling deformation under the action of inertial force while rotating relative to the first bearing 21 and the second bearing 23, which will increase the friction between it and the second bearing 23. An avoidance section 2311 is provided in the second bearing hole 231 so that the avoidance section 2311 can avoid the wobbling part of the crankshaft 1, thereby preventing the wobbling part of the crankshaft 1 from rubbing against the second bearing 23 at the avoidance section 2311.

[0040] According to the compressor 100 of this utility model embodiment, by passing the output shaft section 11 through the first bearing hole 211 and the second bearing hole 231, the first bearing 21 and the second bearing 23 can support the crankshaft 1, ensuring the reliability of the crankshaft 1's operation and allowing the crankshaft 1 to rotate relative to the first bearing 21 and the second bearing 23. Simultaneously, by passing the output shaft section 11 through the cylinder structure 22, the output shaft section 11 can drive the piston 221 to reciprocate, thereby converting the rotational motion of the crankshaft 1 into reciprocating motion to achieve the desired compressor operation. The compressor 100 has a compression function, and at least a portion of the inner wall of the second bearing hole 231 is constructed as a clearance section 2311, so that the clearance section 2311 can be spaced apart from the outer peripheral wall of the output shaft section 11, effectively preventing the second bearing 23 from contacting the crankshaft 1 in the clearance section 2311 and generating friction, thereby reducing the frictional power consumption of the compressor 100, improving the energy efficiency of the compressor 100, reducing the wear of the crankshaft 1 and the second bearing 23, extending the service life of the crankshaft 1 and the second bearing 23, and improving the reliability of the compressor 100.

[0041] In some embodiments, the clearance section 2311 is located in the region of the inner wall of the second bearing hole 231 away from the cylinder structure 22; wherein, the crankshaft 1 further includes an input shaft section 12 connected to the output shaft section 11, the input shaft section 12 being used to connect to a power source, and the end face of the output shaft section 11 away from the input shaft section 12 being located within the clearance section 2311 and spaced apart from the end of the clearance section 2311.

[0042] Specifically, the clearance section 2311 is used to avoid at least a portion of the output shaft section 11. By setting the clearance section 2311 in the area of ​​the inner wall of the second bearing hole 231 away from the cylinder structure 22, the clearance section 2311 can be positioned opposite to the end of the output shaft section 11 to avoid the part of the output shaft section 11 that is wobbling. This allows the clearance section 2311 to be spaced a distance from the part of the output shaft section 11 that is wobbling, effectively preventing the part of the output shaft section 11 that is wobbling from contacting the second bearing 23 at the clearance section 2311 and causing friction, thereby improving the efficiency and reliability of the compressor 100.

[0043] Furthermore, the crankshaft 1 includes an input shaft section 12 and an output shaft section 11. The input shaft section 12 is used for power input, and the output shaft section 11 is used for power output. Connecting the input shaft section 12 and the output shaft section 11 makes the crankshaft 1 a whole, which can improve the overall structural strength of the crankshaft 1. At the same time, connecting the input shaft section 12 to a power source allows the power source to provide power to the input shaft section 12. Thus, the input shaft section 12 can drive the output shaft section 11 to rotate relative to the first bearing 21 and the second bearing 23 under the drive of the power source. During the rotation, the output shaft section 11 can push the piston 221 to reciprocate, thereby realizing the compression function of the compressor 100. The power source can be an electric motor.

[0044] Furthermore, when the input shaft segment 12 drives the output shaft segment 11 to rotate under the drive of the power source, the end of the output shaft segment 11 away from the input shaft segment 12 will wobble. By setting the end face of the output shaft segment 11 away from the input shaft segment 12 in the clearance segment 2311 and spaced apart from the end of the clearance segment 2311, the part of the output shaft segment 11 away from the input shaft segment 12 can be set in the clearance segment 2311, so that the clearance segment 2311 can be spaced a distance from the wobble part of the output shaft segment 11, thereby avoiding the second bearing 23 from contacting the wobble part of the crankshaft 1 and causing friction, thus improving the energy efficiency and operational reliability of the compressor 100.

[0045] In some embodiments, the inner wall of the second bearing hole 231 further includes a mating section 2312, the outer peripheral wall of the output shaft section 11 is fitted and supported by the mating section 2312, and the clearance section 2311 and the mating section 2312 are distributed along the axial direction of the second bearing hole 231.

[0046] Specifically, the output shaft section 11 passes through the second bearing 23, which supports the output shaft section 11. The outer peripheral wall of the output shaft section 11 is fitted and supported against the mating section 2312, allowing the outer peripheral wall of the output shaft section 11 to fit against the mating section 2312. This mating section 2312 enables the connection between the output shaft section 11 and the second bearing 23, allowing the second bearing 23 to support the output shaft section 11, ensuring the reliability of the crankshaft 1's operation. Furthermore, the clearance section 2311... The mating section 2312 is distributed along the axial direction of the second bearing hole 231, so that the clearance section 2311 and the mating section 2312 are coaxially arranged. When the output shaft section 11 is inserted into the second bearing hole 231, the output shaft section 11 can be inserted into the clearance section 2311 and the mating section 2312 in sequence, thereby realizing the mating between the output shaft section 11, the clearance section 2311 and the mating section 2312. The clearance section 2311 is used to make way for the output shaft section 11, and the mating section 2312 is used to support the output shaft section 11.

[0047] In some embodiments, the inner diameter of the mating section 2312 is smaller than the inner diameter of the clearance section 2311; and / or, the mating section 2312 is further provided with an oil guide groove 232.

[0048] Specifically, the mating section 2312 is used to fit against the outer peripheral wall of the output shaft section 11 to support the output shaft section 11, so that the inner diameter of the mating section 2312 is equal to the outer diameter of the output shaft section 11. The clearance section 2311 is used to clearance the output shaft section 11, and the clearance section 2311 is spaced apart from the outer peripheral wall of the output shaft section 11, so that the inner diameter of the clearance section 2311 is greater than the outer diameter of the output shaft section 11. Consequently, the inner diameter of the mating section 2312 is smaller than the inner diameter of the clearance section 2311, so as to ensure that the mating section 2312 can support the output shaft section 11 and the clearance section 2311 can clearance the output shaft section 11.

[0049] Furthermore, the mating section 2312 fits against the outer peripheral wall of the output shaft section 11 to support the output shaft section 11. An oil guide groove 232 is provided in the mating section 2312 to guide the flow of lubricating oil so that the lubricating oil can flow to the critical lubrication area of ​​the second bearing 23, ensuring that the surface of the second bearing 23 can be adequately lubricated, reducing the friction between the second bearing 23 and the output shaft section 11, thereby reducing the frictional power consumption of the compressor 100, improving the energy efficiency of the compressor 100, and reducing the wear of the crankshaft 1 and the second bearing 23, extending the service life of the crankshaft 1 and the second bearing 23, and improving the reliability of the compressor 100.

[0050] In some embodiments, a transition chamfer 2313 connects the avoidance section 2311 and the mating section 2312.

[0051] Specifically, the second bearing hole 231 includes a clearance section 2311 and a mating section 2312. The clearance section 2311 is used to allow clearance for the output shaft section 11, and the mating section 2312 is used to support the output shaft section 11. The inner diameters of the clearance section 2311 and the mating section 2312 can be constructed differently to improve the reliability of the clearance section 2311 in allowing clearance for the output shaft section 11 and the reliability of the mating section 2312 in supporting the output shaft section 11. Simultaneously, a transition chamfer 2313 can be connected between the clearance section 2311 and the mating section 2312 to achieve this. The transition chamfer 2313 connects the clearance section 2311 and the mating section 2312. In other words, the clearance section 2311 and the mating section 2312 with different inner diameters can be connected by the transition chamfer 2313 to form a smooth transition at the connection between the clearance section 2311 and the mating section 2312. This facilitates the sequential insertion of the output shaft section 11 through the clearance section 2311 and the mating section 2312, and avoids interference at the connection between the output shaft section 11 and the clearance section 2311 and the mating section 2312, which could prevent the crankshaft 1 from being installed or cause wear between the crankshaft 1 and the second bearing 23.

[0052] Alternatively, the clearance section 2311 and the mating section 2312 are connected along the axial direction of the second bearing hole 231.

[0053] Specifically, the second bearing hole 231 includes a clearance section 2311 and a mating section 2312, and the clearance section 2311 and the mating section 2312 are distributed along the axial direction of the second bearing hole 231, so that the clearance section 2311 and the mating section 2312 are coaxially arranged. At the same time, the clearance section 2311 and the mating section 2312 can be connected along the axial direction of the second bearing hole 231, so that when the output shaft section 11 is inserted into the second bearing hole 231, the output shaft section 11 can be inserted sequentially through the clearance section 2311 and the mating section 2312, so that the clearance section 2311 can make way for the output shaft section 11, and the mating section 2312 can support the output shaft section 11.

[0054] In some embodiments, the inner diameter of the clearance section 2311 is configured to remain unchanged in the direction away from the mating section 2312.

[0055] Specifically, the clearance section 2311 is sleeved on the outside of the output shaft section 11 to allow clearance from the output shaft section 11. The inner diameter of the clearance section 2311 can be constructed to be larger than the outer diameter of the output shaft section 11, so that the clearance section 2311 can be spaced a distance from the outer peripheral wall of the output shaft section 11, ensuring that the clearance section 2311 can allow clearance from the output shaft section 11. Meanwhile, if... Figure 2 and Figure 4As shown, the inner diameter of each part of the avoidance section 2311 can also be made equal, so that each part of the avoidance section 2311 can be spaced a distance from the outer peripheral wall of the output shaft section 11, further ensuring that the avoidance section 2311 can avoid the output shaft section 11, improving the reliability of the avoidance section 2311 in avoiding the output shaft section 11, and reducing the machining difficulty.

[0056] Alternatively, the inner diameter of the avoidance section 2311 may be constructed to gradually increase in the direction away from the mating section 2312.

[0057] Specifically, the clearance section 2311 is sleeved on the outside of the output shaft section 11 to allow clearance from the output shaft section 11. The clearance section 2311 and the mating section 2312 are connected axially along the second bearing hole 231, and the mating section 2312 fits against the outer peripheral wall of the output shaft section 11. Meanwhile, if... Figure 1 and Figure 3 As shown, the inner diameter of the clearance section 2311 is designed to gradually increase in the direction away from the mating section 2312. This makes the inner diameter of the clearance section 2311 at the connection with the mating section 2312 the smallest, and gradually increases from the connection with the mating section 2312 away from the mating section 2312. This ensures that the clearance section 2311 can be spaced a distance from the outer peripheral wall of the output shaft section 11 at all points, ensuring that the clearance section 2311 can avoid the output shaft section 11 and effectively improving the reliability of the clearance section 2311 in avoiding the output shaft section 11.

[0058] In some embodiments, the depth of the clearance section 2311 in the radial direction of the second bearing hole 231 is d, and satisfies: 0.5mm≤d≤1.5mm.

[0059] Specifically, the clearance section 2311 is spaced apart from the outer peripheral wall of the output shaft section 11, allowing the clearance section 2311 to have a certain distance between it and the outer peripheral wall of the output shaft section 11, thus avoiding the output shaft section 11. The radial depth of the clearance section 2311 in the second bearing hole 231 can be set as d. d should not be too large or too small. When d is too large, it will result in an excessively large inner diameter of the second bearing hole 231, which will lead to an excessively large radial dimension of the second bearing 23, which is not conducive to the setting of the compressor 100. When d is too small, it will result in a small gap between the clearance section 2311 and the outer peripheral wall of the output shaft section 11, which is not conducive to the clearance section 2311 clearing the output shaft section 11. d can be between 0.5mm and 1.5mm, such as 0.5mm, 1mm, or 1.5mm, which can avoid the second bearing 23 from being too large while meeting the clearance space for the output shaft section 11.

[0060] In some embodiments, the axial height of the second bearing 23 is H, and the length of the clearance section 2311 in the axial direction of the second bearing 23 is L, and satisfies: 5mm≤L≤0.5H.

[0061] Specifically, the second bearing 23 is provided with a second bearing hole 231. The axial height of the second bearing 23 is H, that is, the axial length of the second bearing hole 231 is H. At least part of the second bearing hole 231 is constructed as a clearance section 2311, and the second bearing hole 231 includes a clearance section 2311 and a mating section 2312. The length of the clearance section 2311 in the axial direction of the second bearing 23 is L. L cannot be too large or too small. When L is too large, it will cause the length of the mating section 2312 in the axial direction of the second bearing 23 to be too small, resulting in a weakening of the support effect of the second bearing 23 on the crankshaft 1. When L is too small, that is, the setting length of the clearance section 2311 is too small, resulting in a too small clearance length for the output shaft section 11.

[0062] Meanwhile, the relationship between L and H satisfies: 5mm≤L≤0.5H, which means that L is between 5mm and half of the axial height of the second bearing 23. This ensures that the length of the clearance section 2311 in the axial direction of the second bearing 23 is neither too large nor too small. Under the premise that the mating section 2312 supports the output shaft section 11, the length of the clearance section 2311 can be guaranteed, thereby ensuring the effect of reducing friction between the crankshaft 1 and the second bearing 23.

[0063] In some embodiments, the cylinder structure 22 includes at least one cylinder 222, which is distributed along the axial direction of the crankshaft 1 between the first bearing 21 and the second bearing 23. The second bearing 23 includes a second axial portion 233 and a second radial portion 234 connected along the axial direction. The second radial portion 234 is used to connect with one of the cylinders 222. The second axial portion 233 is connected to the side of the second radial portion 234 away from the cylinder 222. A clearance section 2311 is formed on the inner peripheral wall of the second axial portion 233.

[0064] Specifically, cylinder 222 provides a sealed space where gas can be compressed. Cylinder structure 22 includes at least one cylinder 222, meaning the number of cylinders 222 can be one, two, three, or more. This allows gas to be compressed simultaneously within at least one cylinder 222, thereby improving the efficiency of compressor 100. Distributing at least one cylinder 222 along the axial direction of crankshaft 1 between first bearing 21 and second bearing 23 allows crankshaft 1 to simultaneously drive piston 221 within at least one cylinder 222 to reciprocate, compressing gas simultaneously within at least one cylinder 222. This effectively improves the efficiency of compressor 100 and reduces the number of power sources required, thus lowering installation costs.

[0065] In such Figure 1 and Figure 2In the embodiment shown, the cylinder structure 22 includes two cylinders 222, which are sequentially arranged between the first bearing 21 and the second bearing 23. The first bearing 21 and the second bearing 23 are respectively connected to the cylinder 222 that is closer to them. A partition 223 is provided between the two cylinders 222 to ensure that the two cylinders 222 can work independently, effectively improving the efficiency of the compressor 100. The number of cylinders 222 is not limited to that described in this embodiment and can be flexibly set according to specific needs and space.

[0066] Furthermore, the second axial portion 233 and the second radial portion 234 are distributed axially, and connecting the second axial portion 233 and the second radial portion 234 allows the second bearing 23 to be integrated as a whole, thereby improving the overall structural strength of the second bearing 23. Simultaneously, connecting the second radial portion 234 to one of the cylinders 222 allows the second radial portion 234 to be connected to a cylinder 222 closest to itself. Connecting the second axial portion 233 to the side of the second radial portion 234 away from the cylinder 222 allows the second axial portion 233 and the cylinder 222 to be respectively connected to the second bearing 233. The two ends of the radial portion 234 are designed to prevent interference between the second axial portion 233 and the cylinder 222, which would prevent the second bearing 23 from being connected to the cylinder 222. Furthermore, the second axial portion 233 extends axially and the second radial portion 234 extends radially, which increases the contact area between the second radial portion 234 and the cylinder 222. This improves the connection strength between the second bearing 23 and the corresponding cylinder 222, and also increases the contact area between the second axial portion 233 and the crankshaft 1, thereby improving the reliability of the second bearing 23 in supporting the crankshaft 1.

[0067] Furthermore, the avoidance section 2311 is formed on the inner peripheral wall of the second axial portion 233, which allows the avoidance section 2311 to extend axially, thereby increasing the setting length of the avoidance section 2311 and ensuring that the avoidance section 2311 can avoid the output shaft section 11. This effectively prevents the second bearing 23 from contacting the crankshaft 1 in the avoidance section 2311 and causing friction, thereby improving the energy efficiency and operational reliability of the compressor 100.

[0068] And / or, the compressor 100 also includes a first silencer 3, which is sleeved outside the first bearing 21 and together with the first bearing 21 defines a first silencer cavity 31.

[0069] Specifically, the first silencer 3 is used to reduce noise propagation. The first silencer 3 is sleeved on the outside of the first bearing 21 to realize the installation of the first silencer 3. The first silencer 3 can be connected to the first bearing 21 to provide additional structural stability and ensure the stability and reliability of the compressor 100 during operation. Moreover, the first silencer 3 and the first bearing 21 together define the first silencing cavity 31, which can be used to absorb, isolate and reflect noise to suppress the propagation of noise and reduce the impact of noise on the surrounding environment and human health.

[0070] This utility model also proposes an air conditioner.

[0071] The air conditioner according to the embodiments of the present invention includes a compressor according to any of the above embodiments. By constructing at least a portion of the inner wall of the second bearing hole 231 as a clearance section 2311, the clearance section 2311 can be spaced apart from the outer peripheral wall of the output shaft section 11, effectively preventing the second bearing 23 from contacting the crankshaft 1 and causing friction in the clearance section 2311. This reduces the frictional power consumption of the compressor 100, improves the energy efficiency of the compressor 100, and thus improves the energy efficiency of the air conditioner. It also reduces the wear of the crankshaft 1 and the second bearing 23, extends the service life of the crankshaft 1 and the second bearing 23, improves the reliability of the compressor 100, and thus improves the reliability of the air conditioner.

[0072] This utility model also proposes a vehicle.

[0073] The vehicle according to the embodiments of the present invention includes the compressor 100 of any of the above embodiments, or includes the air conditioner of the above embodiments. By providing the compressor 100 or the air conditioner, the energy efficiency of the compressor 100 and the air conditioner can be improved, thereby improving the overall vehicle energy efficiency and extending the driving range.

[0074] In the description of this specification, the references to terms such as "one embodiment," "some embodiments," "illustrative embodiment," "example," "specific example," or "some examples," etc., indicate that a specific feature, structure, material, or characteristic described in connection with that embodiment or example is included in at least one embodiment or example of the present invention. In this specification, the illustrative expressions of the above terms do not necessarily refer to the same embodiment or example. Furthermore, the specific features, structures, materials, or characteristics described may be combined in any suitable manner in one or more embodiments or examples.

[0075] Although embodiments of the present invention have been shown and described, those skilled in the art will understand that various changes, modifications, substitutions and alterations can be made to these embodiments without departing from the principles and spirit of the present invention, the scope of which is defined by the claims and their equivalents.

Claims

1. A compressor, characterized in that, include: Crankshaft, the crankshaft including an output shaft section; A cylinder assembly, comprising a first bearing, a cylinder structure, and a second bearing, wherein the first bearing has a first bearing hole, the second bearing has a second bearing hole, and an output shaft section is rotatably disposed through the first bearing hole, the cylinder structure, and the second bearing hole, and the output shaft section is used to drive a piston in the cylinder structure to reciprocate. Wherein, at least a portion of the inner wall of the second bearing hole is constructed as a clearance section, which is spaced apart from the outer peripheral wall of the output shaft section.

2. The compressor according to claim 1, characterized in that, The clearance section is located on the inner wall of the second bearing hole in a region away from the cylinder structure; The crankshaft further includes an input shaft segment connected to the output shaft segment. The input shaft segment is used to connect to a power source. The end face of the output shaft segment away from the input shaft segment is located within the clearance section and is spaced apart from the end of the clearance section.

3. The compressor according to claim 2, characterized in that, The inner wall of the second bearing hole also includes a mating section, the outer peripheral wall of the output shaft section is fitted and supported by the mating section, and the clearance section and the mating section are distributed along the axial direction of the second bearing hole.

4. The compressor according to claim 3, characterized in that, The inner diameter of the mating section is smaller than the inner diameter of the clearance section; And / or, the mating section is also provided with an oil guide groove.

5. The compressor according to claim 4, characterized in that, A transition chamfer connects the avoidance section and the mating section; Alternatively, the clearance section and the mating section are connected axially along the second bearing hole.

6. The compressor according to claim 5, characterized in that, The inner diameter of the clearance section remains unchanged in the direction away from the mating section; Alternatively, the inner diameter of the clearance section may be configured to gradually increase in the direction away from the mating section.

7. The compressor according to claim 6, characterized in that, The depth of the clearance section in the radial direction of the second bearing hole is d, and satisfies: 0.5mm≤d≤1.5mm.

8. The compressor according to any one of claims 1-7, characterized in that, The axial height of the second bearing is H, and the length of the clearance section in the axial direction of the second bearing is L, satisfying: 5mm≤L≤0.5H.

9. The compressor according to any one of claims 1-7, characterized in that, The cylinder structure includes at least one cylinder, which is distributed along the axial direction of the crankshaft between the first bearing and the second bearing. The second bearing includes a second axial portion and a second radial portion connected along the axial direction. The second radial portion is used to connect with one of the cylinders. The second axial portion is connected to the side of the second radial portion away from the cylinder. The clearance section is formed on the inner peripheral wall of the second axial portion. And / or, it also includes a first muffler, which is sleeved outside the first bearing and together with the first bearing defines a first muffler cavity.

10. An air conditioner, characterized in that, The compressor includes any one of claims 1-9.

11. A vehicle, characterized in that, It includes the compressor according to any one of claims 1-9, or the air conditioner according to claim 10.

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