Compressor, air conditioning device, and vehicle

Abstract

This invention discloses a compressor, an air conditioning unit, and a vehicle. The compressor includes: a housing and a mounting bracket. A first bearing hole is formed within the mounting bracket, and a first bearing component is disposed within the first bearing hole. The first bearing component includes an inner ring and an outer ring, and the space between the inner and outer rings is connected to an oil supply circuit. A motor unit, a crankshaft, a moving scroll, and a stationary scroll are also included. The motor unit is poweredly connected to the moving scroll via the crankshaft to drive the moving scroll to rotate eccentrically relative to the stationary scroll, thereby compressing the medium within the compression chamber. A thrust member is mounted within the mounting bracket and is located at one end of the first bearing component to axially limit the inner ring. A mating structure is provided within the first bearing hole, which is fitted to the outer ring and tilts the outer ring relative to the first bearing hole axially to pre-tighten the inner ring towards the thrust member. The compressor of this invention achieves a tight seal between the inner ring of the first bearing component and the thrust member, preventing lubricating oil leakage and improving the reliability of the compressor.

Description

Technical Field

[0001] This invention relates to the field of compressor manufacturing technology, and more particularly to a compressor, an air conditioning unit having the compressor, and a vehicle having the air conditioning unit. Background Technology

[0002] In an electric scroll compressor, components typically include a mounting bracket, crankshaft, moving scroll, and a first bearing assembly. The crankshaft passes through the mounting bracket and the first bearing assembly and connects to the moving scroll to drive its revolution and translation. The mounting bracket has a first bearing bore, in which the first bearing assembly is housed. The first bearing assembly is typically a cylindrical roller bearing. The inner ring of the first bearing assembly is interference-fitted with the crankshaft, and the outer ring is interference-fitted with the first bearing bore. Due to the characteristics of cylindrical roller bearings, the outer ring can only restrict the crankshaft's movement towards the moving scroll, but cannot restrict its movement away from the moving scroll. Therefore, a thrust stop is usually added between the inner ring and the mounting bracket as a limiting element.

[0003] The existing electric scroll compressor structure cannot guarantee that the inner ring of the first bearing component will always press against the thrust member. This causes the pressure on both sides of the mounting bracket to leak through the gap between the thrust member and the inner ring of the first bearing component, resulting in the failure of the oil supply circuit and causing compressor reliability problems. There is still room for improvement. Summary of the Invention

[0004] This invention aims to at least solve one of the technical problems existing in the prior art. To this end, this invention proposes a compressor capable of achieving a tight seal between the inner ring of a first bearing and a thrust member, preventing lubricating oil leakage and improving the reliability of the compressor.

[0005] A compressor according to an embodiment of the present invention includes: a housing and a mounting bracket, the housing and the mounting bracket being fitted together to define a first cavity and a second cavity, the first cavity having a motor portion, the mounting bracket having a first bearing hole, the first bearing hole having a first bearing member, the first bearing member including an inner ring portion, an outer ring portion, and a rolling element located between the inner ring portion and the outer ring portion, the space between the inner ring portion and the outer ring portion communicating with an oil supply circuit; a crankshaft and a compression component, the compression component being located in the second cavity and including a moving scroll and a stationary scroll, the moving scroll and the stationary scroll jointly defining the compression cavity, the crankshaft being interference-fitted through the inner ring portion and interference-fitted with the inner ring portion to allow for... The first bearing is rotatably supported on the mounting bracket. One end of the crankshaft is located in the first cavity. The moving scroll is eccentrically connected to the other end of the crankshaft. The motor is poweredly connected to the moving scroll through the crankshaft to drive the moving scroll to rotate eccentrically relative to the stationary scroll to compress the medium in the compression cavity. A thrust member is installed in the mounting bracket. The thrust member is located at the end of the first bearing away from the moving scroll to limit the inner ring portion axially. A fitting structure is provided in the first bearing hole. The fitting structure is fitted with the outer ring portion and tilts the outer ring portion axially relative to the first bearing hole to pre-tighten the inner ring portion toward the thrust member.

[0006] According to an embodiment of the present invention, the compressor has a fitting structure provided in the first bearing hole. The fitting structure is installed and fitted with the outer ring portion and the outer ring portion is axially inclined relative to the first bearing hole so that the inner ring portion is pre-tightened toward the thrust member. This allows the crankshaft to always generate an axial component force pointing toward the thrust member during operation, so that the inner ring portion of the first bearing member can always press against the thrust member. This achieves a tight seal between the inner ring portion of the first bearing member and the thrust member, prevents lubricating oil leakage, and improves the reliability of the compressor.

[0007] According to some embodiments of the compressor of the present invention, the mounting bracket includes a limiting stop portion located at one end of the first bearing bore away from the moving scroll, the limiting stop portion forming a through hole through which the crankshaft extends into the first bearing bore, and the limiting stop portion forming a limiting mounting groove opening toward the first bearing bore; wherein, the thrust member is located in the limiting mounting groove and is axially opposite to the inner ring portion of the crankshaft, and the limiting stop portion and the outer ring portion are axially opposite to the crankshaft.

[0008] According to some embodiments of the compressor of the present invention, at least a portion of the inner peripheral wall of the first bearing bore is configured as the mating structure, the mating structure being configured such that the inner diameter dimensions are different at at least two positions in the axial direction.

[0009] According to some embodiments of the compressor of the present invention, the inner diameter of the mating structure is configured to decrease axially in a direction away from the thrust member; and / or, the inner peripheral wall surface of the mating structure is configured as an arcuate surface, a straight surface, or an irregular surface; the inner diameter of the mating structure is configured to decrease linearly axially in a direction away from the thrust member.

[0010] According to some embodiments of the compressor of the present invention, the mating structure includes at least two cylindrical sub-hole walls, and the inner diameter of one of two adjacent cylindrical sub-hole walls closer to the thrust member is greater than the inner diameter of the one farther away from the thrust member; and / or, the mating structure includes at least one cylindrical sub-hole wall and at least one tapered sub-hole wall, and the inner diameter of the tapered sub-hole wall gradually decreases in the direction away from the thrust member.

[0011] According to some embodiments of the compressor of the present invention, the inner diameter of the end of the mating structure away from the thrust member is D1, and the inner diameter of the end of the mating structure close to the thrust member is D2, where D1 < D2; and / or, the maximum value of the change in the inner diameter of the mating structure is less than the first bearing clearance of the first bearing member.

[0012] According to some embodiments of the compressor of the present invention, the mating structure is configured as a mating protrusion protruding from the inner peripheral wall of the first bearing hole, the mating protrusion pressing against the outer peripheral wall of the outer ring portion.

[0013] According to some embodiments of the compressor of the present invention, the mating protrusion is constructed as an annular protrusion, the inner diameter of the annular protrusion being smaller than the inner diameter of the first bearing hole; and / or, the mating protrusion is constructed as a mating protrusion, there are multiple mating protrusions, and the multiple mating protrusions are spaced apart in the circumferential direction of the first bearing hole.

[0014] According to some embodiments of the compressor of the present invention, the inner peripheral wall of the annular protrusion is formed with a first mating inclined surface, the first mating inclined surface being inclined relative to the axial direction of the first bearing hole, and the first mating inclined surface being in contact with and pressing against the outer peripheral wall of the outer ring portion.

[0015] According to some embodiments of the compressor of the present invention, the mating structure is configured as a mating part installed in the first bearing hole, wherein the inner diameter of the mating part is smaller than the inner diameter of the first bearing hole.

[0016] According to some embodiments of the compressor of the present invention, the mating component is interference-fitted to the inner peripheral wall of the first bearing hole; and / or, the inner peripheral wall of the mating component is formed with a second mating slope, the second mating slope being inclined relative to the axial direction of the first bearing hole, and the second mating slope being in contact with and pressing against the outer peripheral wall of the outer ring portion.

[0017] According to some embodiments of the compressor of the present invention, the compressor further includes an eccentric pin and an eccentric sleeve, the other end of the crankshaft is provided with a first eccentric hole, the eccentric sleeve is provided with a second eccentric hole, one end of the eccentric pin is connected to the first eccentric hole, the other end of the eccentric pin is connected to the second eccentric hole, and the moving scroll is sleeved outside the eccentric sleeve; the axis of the first eccentric hole is offset from the axis of the crankshaft, the axis of the second eccentric hole is offset from the axis of the eccentric sleeve, and the axis of the crankshaft is offset from the axis of the eccentric sleeve.

[0018] According to some embodiments of the compressor of the present invention, the moving scroll is formed with a second bearing hole that opens toward the first bearing hole, a second bearing member is provided in the second bearing hole, and the eccentric sleeve is installed in the second bearing member to be rotatably supported on the moving scroll by the second bearing member.

[0019] According to some embodiments of the compressor of the present invention, the housing includes a first housing and a second housing, the first housing and the second housing being respectively connected to both sides of the mounting bracket, the first housing and the mounting bracket defining a first cavity, and the second housing and the mounting bracket defining a second cavity.

[0020] The present invention also proposes an air conditioning device, which is equipped with a compressor as described in any one of the claims.

[0021] The present invention also proposes a vehicle equipped with any of the air conditioning devices described in the present invention.

[0022] The advantages of the air conditioning unit, the vehicle, and the compressor mentioned above compared to the prior art are the same, and will not be repeated here.

[0023] Additional aspects and advantages of the 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

[0024] The above and / or additional aspects and advantages of the present invention will become apparent and readily understood from the description of the embodiments taken in conjunction with the following drawings, in which:

[0025] Figure 1 This is a cross-sectional view of a compressor according to an embodiment of the present invention;

[0026] Figure 2 yes Figure 1 A partial structural diagram;

[0027] Figure 3 This is a schematic diagram of the mating structure according to an embodiment of the present invention. Figure 1 ;

[0028] Figure 4 This is a schematic diagram of the mating structure according to an embodiment of the present invention. Figure 2 ;

[0029] Figure 5 This is a schematic diagram of the mating structure according to an embodiment of the present invention. Figure 3 ;

[0030] Figure 6 The calculation of the tilting tension of the crankshaft according to an embodiment of the present invention. Figure 1 ;

[0031] Figure 7 The calculation of the tilting tension of the crankshaft according to an embodiment of the present invention. Figure 2 ;

[0032] Figure 8 The crankshaft tension according to an embodiment of the present invention Figure 1 ;

[0033] Figure 9 The crankshaft tension according to an embodiment of the present invention Figure 2 .

[0034] Figure label:

[0035] Compressor 100,

[0036] Housing 1, mounting bracket 11, first cavity 101, second cavity 102, limiting stop 12, through hole 121, limiting mounting groove 122, first bearing hole 112, mating structure 1121, cylindrical sub-hole wall 1122, tapered sub-hole wall 1123, first bearing component 13, inner ring portion 131, outer ring portion 132, rolling element 133, first housing 14, second housing 15, cover plate 16.

[0037] 2. Crankshaft, 3. Thrust wrench, 4. Eccentric sleeve, 51. Electrical control unit, 52. Motor unit, 7. Stationary scroll, 8. Moving scroll, 81. Compression chamber, 9. Eccentric pin. Detailed Implementation

[0038] Embodiments of the present invention 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 the present invention, and should not be construed as limiting the present invention.

[0039] In the description of this invention, it should be understood that the terms "center," "longitudinal," "lateral," "length," "width," "thickness," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," "outer," "clockwise," "counterclockwise," "axial," "radial," and "circumferential," etc., indicating orientation or positional relationships, are based on the orientation or positional relationships shown in the accompanying drawings and are only for the convenience of describing the invention 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 the invention. Furthermore, features defined with "first" or "second" may explicitly or implicitly include one or more of that feature. In the description of this invention, unless otherwise stated, "a plurality of" means two or more.

[0040] In the description of this invention, it should be noted that, unless otherwise explicitly specified and limited, the terms "installation," "connection," and "linking" 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 invention based on the specific circumstances.

[0041] The following is for reference. Figures 1-9 A compressor 100 according to an embodiment of the present invention is described, which can achieve a tight seal between the inner ring portion 131 of the first bearing member 13 and the thrust member 3, prevent lubricating oil leakage, and improve the reliability of the compressor 100.

[0042] like Figures 1-9 As shown, the compressor 100 according to an embodiment of the present invention includes: a housing 1, a mounting bracket 11, a crankshaft 2, a thrust member 3, and a compression component. The housing is used to install and protect the internal components. The housing 1 is fitted with the mounting bracket 11 to define a first cavity 101 and a second cavity 102. The first cavity 101 is provided with a motor part 52. The compression component is located in the second cavity 102 and includes a moving scroll 8 and a stationary scroll 7. The mounting bracket 11 is used to install a first bearing member 13 and a thrust member 3. One end of the crankshaft 2 can be inserted into the mounting bracket 11 to be rotatably supported on the first bearing member 13.

[0043] A first bearing hole 112 is formed within the mounting bracket 11, and a first bearing element 13 is disposed within the first bearing hole 112. The first bearing element 13 includes an inner ring portion 131, an outer ring portion 132, and a rolling element 133 located between the inner ring portion 131 and the outer ring portion 132. The space between the inner ring portion 131 and the outer ring portion 132 is connected to an oil supply passage. The crankshaft 2 is interference-fitted through the inner ring portion 131 and is rotatably supported on the mounting bracket 11 by the first bearing element 13. The rolling element 133 may be constructed as a cylindrical roller or other structural components.

[0044] In other words, the mounting bracket 11 has a first bearing hole 112 that extends axially. The first bearing member 13 is installed in the first bearing hole 112. The outer ring portion 132 of the first bearing member 13 is in abutting contact with the inner peripheral wall of the first bearing hole 112. The inner ring portion 131 is coaxially installed inside the outer ring portion 132. The rolling element 133 is disposed between the inner ring portion 131 and the outer ring portion 132. That is, the inner ring portion 131 can rotate relative to the outer ring portion 132 through the rolling element 133. With this configuration, when one end of the crankshaft 2 extends into the first bearing hole 112, the crankshaft 2 can pass through the inner ring portion 131. That is, the outer peripheral wall of the crankshaft 2 can be in abutting contact with the inner ring portion 131 of the first bearing member 13, thereby allowing the crankshaft 2 to pass through the first bearing member 131. Rotatably supported within the mounting bracket 11, the crankshaft 2 rotates, and the rotation of the first bearing component 13 reduces friction between it and the mounting bracket 11. Furthermore, the inner ring 131 of the crankshaft 2 and the first bearing component 13 is an interference fit, ensuring a tight connection between the first bearing component 13 and the crankshaft 2, preventing axial movement of the crankshaft 2, and thus achieving precise power transmission. Simultaneously, the inner end face of the first bearing hole 112 can limit the outer ring 132 of the first bearing component 13, preventing axial movement of the first bearing component 13. The space between the inner ring 131 and the outer ring 132 is connected to the oil supply circuit, allowing lubricating oil in the oil supply circuit to enter the space between the inner ring 131 and the outer ring 132, thus lubricating the first bearing component 13.

[0045] The motor unit 52 drives the crankshaft 2 to rotate, that is, the motor unit 52 provides power to the crankshaft 2 to make it rotate, thereby driving other components to rotate and realizing power transmission. The stationary scroll 7 is provided with a scroll cavity to install the moving scroll 8, that is, the moving scroll 8 is installed in the stationary scroll 7, and the moving scroll 8 and the stationary scroll 7 together define the compression chamber 81 to compress the gas in the compression chamber 81 to achieve the compression effect. The motor unit 52 is installed in the first chamber 101, and the moving scroll 8 and the stationary scroll 7 are both installed in the second chamber 102, so that the motor unit 52 and the stationary scroll 7 are respectively installed on both sides of the mounting bracket 11. One end of the crankshaft 2 is located in the first chamber 101, and the moving scroll 8 is eccentrically connected to the other end of the crankshaft 2. The motor unit 52 is connected to the moving scroll 8 through the crankshaft 2. The power connection of the rotating scroll 8 relative to the stationary scroll 7 compresses the medium within the compression chamber 81. Specifically, in actual operation, the end of the crankshaft 2 closest to the motor unit 52 is powered by the motor unit 52 within the first chamber 101, while the end furthest from the motor unit 52 is powered by the rotating scroll 8 within the second chamber 102. The motor unit 52 drives the crankshaft 2 to rotate within the mounting bracket 11. This rotation, in turn, causes the rotating scroll 8 to rotate eccentrically relative to the stationary scroll 7 within the stationary scroll 7, thus transmitting power from the motor unit 52 to the rotating scroll 8. At this time, the stationary scroll 7 is stationary relative to the rotating scroll 8, and the rotating scroll 8 forms a continuously changing compression chamber 81. The compression of the gas is achieved through the change in the volume of the compression chamber 81. The medium within the compression chamber 81 can be a refrigerant.

[0046] In addition, the inner ring portion 131 and the outer ring portion 132 of the first bearing component 13 are separable, that is, the inner ring portion 131 and the outer ring portion 132 can be disassembled relative to each other, which is flexible and convenient.

[0047] Furthermore, the thrust member 3 is installed inside the mounting bracket 11. The thrust member 3 is located at the end of the first bearing member 13 away from the moving scroll 8 to limit the inner ring portion 131 axially. That is, the thrust member 3 can be constructed as a ring, installed between the mounting bracket 11 and the end of the first bearing member 13 away from the moving scroll 8, and sleeved on the outer periphery of the crankshaft 2. The end of the thrust member 3 facing the first bearing member 13 is pressed against the inner ring portion 131 of the first bearing member 13, and the end away from the first bearing member 13 is pressed against the inner wall of the mounting bracket 11. Thus, the thrust member 3 axially presses against the first bearing member 13 and the mounting bracket 11, which can limit the first bearing member 13 and prevent the first bearing member 13 from moving axially.

[0048] The first bearing hole 112 is provided with a mating structure 1121, which is installed and mated with the outer ring portion 132 and makes the outer ring portion 132 axially inclined relative to the first bearing hole 112 so that the inner ring portion 131 is pre-tightened toward the thrust member 3.

[0049] Specifically, the fitting structure 1121 in the first bearing hole 112 can be interference-fitted with the outer ring portion 132. The interference fit allows the outer ring portion 132 to be tightly connected with the fitting structure 1121, thereby achieving a tight connection between the first bearing component 13 and the mounting bracket 11, further preventing axial movement of the first bearing component 13, and facilitating the positioning of the crankshaft 2 to prevent its movement. The inner peripheral wall of the mating structure 1121 can be configured to have a certain inclination or irregular shape relative to the axial direction, so that after the mating structure 1121 and the outer ring portion 132 are interference-fitted, the inner peripheral wall of the mating structure 1121 can exert a certain compressive force on the outer peripheral wall of the outer ring portion 132, causing the outer ring portion 132 to tilt a certain direction relative to the axial direction of the first bearing hole 112, thereby causing the inner ring portion 131 to tilt a certain direction relative to the axial direction of the first bearing hole 112, that is, a certain angle can be formed relative to the axial direction, so that the inner ring portion 131 is pre-tightened towards the thrust member 3. In other words, the inner ring portion 131 moves closer to the thrust member 3, reducing the gap between the thrust member 3 and the inner ring portion 131, so that the two are tightly pressed together, thereby achieving a seal between the inner ring portion 131 and the thrust member 3.

[0050] With this configuration, the tilt of the inner ring 131 allows the crankshaft 2 to rotate. The movement of the rolling elements 133 inside the first bearing 13 ensures that the crankshaft 2 always generates an axial force pointing towards the thrust member 3 during its movement. This allows the inner ring 131 of the first bearing 13 to always press against the thrust member 3, thereby achieving a tight seal between the inner ring 131 of the first bearing 13 and the thrust member 3. Since there is lubricating oil inside the first bearing 13, it also prevents the pressure on both sides of the mounting bracket 11 from leaking through the gap between the thrust member 3 and the inner ring 131 of the first bearing 13, thus preventing the failure of the oil supply circuit inside the first bearing 13 and improving the reliability of the compressor 100.

[0051] It should be noted that the compressor 100 in this embodiment can be an electric scroll compressor. The electric scroll compressor can be used in the air conditioning system of an automobile. The electric scroll compressor also includes components such as an eccentric sleeve 4. The eccentric sleeve 4 is disposed in the moving scroll 8 and is connected to the crankshaft 2 through an eccentric pin 9. That is, the rotation of the crankshaft 2 can drive the moving scroll 8 to move through the eccentric sleeve 4. It also includes an electronic control unit, which controls the movement of the motor unit 52 through the electronic control unit 51.

[0052] According to an embodiment of the present invention, the compressor 100 provides a mating structure 1121 in the first bearing hole 112. The mating structure 1121 is installed and mated with the outer ring portion 132, and the outer ring portion 132 is axially inclined relative to the first bearing hole 112 so that the inner ring portion 131 is pre-tightened toward the thrust member 3. This allows the crankshaft 2 to always generate an axial component force pointing toward the thrust member 3 during operation, so that the inner ring portion 131 of the first bearing member 13 can always press against the thrust member 3. This achieves a tight seal between the inner ring portion 131 of the first bearing member 13 and the thrust member 3, prevents lubricating oil leakage, and improves the reliability of the compressor 100.

[0053] In some embodiments, the mounting bracket 11 includes a limiting stop portion 12, which is located at one end of the first bearing hole 112 away from the moving scroll 8. The limiting stop portion 12 has a through hole 121 through which the crankshaft 2 extends into the first bearing hole 112. The limiting stop portion 12 has a limiting mounting groove 122 that opens toward the first bearing hole 112.

[0054] The thrust member 3 is located in the limiting mounting groove 122 and is directly opposite the inner ring portion 131 in the axial direction of the crankshaft 2, while the limiting stop portion 12 and the outer ring portion 132 are directly opposite each other in the axial direction of the crankshaft 2.

[0055] Specifically, such as Figure 1 and Figure 2 As shown, the mounting bracket 11 is provided with a limiting stop 12. The limiting stop 12 is used to install and limit the first bearing member 13 and the thrust member 3. The limiting stop 12 is located at one end of the first bearing hole 112 away from the moving scroll 8, and a through hole 121 is formed on the side of the limiting stop 12 near the first cavity 101. The through hole 121 communicates with the first bearing hole 112 so that the crankshaft 2 can extend into the first bearing hole 112 through the through hole 121 and connect with the first bearing member 13. Furthermore, the inner peripheral wall of the limiting stop portion 12 is formed with a limiting mounting groove 122 that opens toward the first bearing hole 112. The limiting mounting groove 122 is used to install the thrust member 3. Thus, the inner ring portion 131 of the first bearing member 13 can be axially pressed and connected with the thrust member 3 to limit the inner ring portion 131 axially. The outer ring portion 132 of the first bearing member 13 is pressed and connected with the inner peripheral wall of the limiting stop portion 12 to limit the outer ring portion 132 axially. In this way, the space between the inner ring portion 131 and the outer ring portion 132 can be sealed by the thrust member 3.

[0056] In some embodiments, at least a portion of the inner peripheral wall of the first bearing hole 112 is configured as a mating structure 1121. The mating structure 1121 is configured to have different inner diameters at at least two positions in the axial direction. That is, a portion of the inner peripheral wall of the first bearing hole 112 can be configured as a mating structure 1121 for mounting the first bearing member 13. The inner diameters of the inner peripheral wall of the first bearing hole 112 can be set to be different at two, three, or even more positions in the axial direction. In other words, the inner peripheral wall of the first bearing hole 112 can form a certain angle with the axial direction, or the inner peripheral wall of the first bearing hole 112 can be parallel to the axial direction, but the inner diameters are different at multiple positions, changing, for example, the inner diameter decreases.

[0057] By setting the inner diameter of the inner circumferential wall of the first bearing hole 112 to be different at multiple locations, after the first bearing component 13 is installed in the first bearing hole 112, the outer ring portion 132 of the first bearing component 13 can be tilted relative to the axial direction of the first bearing hole 112, forming a certain angle with the axial direction. This causes the outer ring portion 132 to be squeezed by the inner circumferential wall of the mounting bracket 11, generating a certain force. This causes the inner ring portion 131 to also form a certain angle with the axial direction, thereby causing the inner ring portion 131 to be pre-tightened toward the thrust member 3. That is, the inner ring portion 131 and the thrust member 3 are tightly pressed together. This allows the crankshaft 2 to always generate an axial component force pointing toward the thrust member 3 during the movement, so that the inner ring portion 131 of the first bearing component 13 can always press against the thrust member 3. This achieves a tight seal between the inner ring portion 131 of the first bearing component 13 and the thrust member 3, improving the reliability of the compressor 100.

[0058] In some embodiments, the inner diameter of the mating structure 1121 is configured to decrease axially in the direction away from the thrust member 3. The decreasing method can be step-down, linear, irregular, etc. It is only necessary to satisfy that the inner diameter of the mating structure 1121 gradually decreases axially in the direction away from the thrust member 3, so that the inner ring portion 131 of the first bearing member 13 forms a certain angle with the axial direction after installation.

[0059] Therefore, the inner diameter of the mating structure 1121 on the side closer to the thrust member 3 is larger than the inner diameter of the mating structure 1121 on the side farther from the thrust member 3. This allows the inner ring portion 131 of the first bearing member 13 to form a certain angle relative to the axial direction, thereby enabling the crankshaft 2 to generate axial tension during operation, or to improve the axial tension generated by the tilting of the crankshaft 2. Since the inner diameter of the mating structure 1121 decreases in the direction away from the thrust member 3, the axial tension can always be directed towards the thrust member 3, causing the thrust member 3 to press tightly between the inner ring portion 131 of the first bearing member 13 and the inner peripheral wall of the mounting bracket 11. This achieves a seal between the inner ring portion 131 of the first bearing member 13 and the thrust member 3, preventing pressure on both sides of the mounting bracket 11 from leaking through the gap between the thrust member 3 and the inner ring portion 131 of the first bearing member 13. This prevents lubricating oil leakage in the first bearing member 13, which could lead to failure of the oil supply circuit and improve the reliability of the compressor 100.

[0060] like Figures 2-5 As shown, the middle section of the inner peripheral wall of the first bearing hole 112 is constructed as a mating structure 1121. The first bearing component 13 is installed in the mating structure 1121. The inner diameter of the mating structure 1121 decreases axially in the direction away from the thrust member 3, as shown in the vertical direction in the figure. The inner diameter of the mating structure 1121 decreases from bottom to top.

[0061] In addition, such as Figures 6-9 As shown, through simulation calculations, it is verified that when the inner diameter of the mating structure 1121 decreases axially in the direction away from the thrust member 3, the crankshaft 2 can generate axial tension or improve the axial tension generated by the tilt of the crankshaft 2, and the direction of the tension is towards the side closer to the thrust member 3. If the inner diameter of the mating structure 1121 decreases axially in the direction closer to the thrust member 3, that is, when the decreasing direction is set to the opposite, the direction of the axial tension generated by the crankshaft 2 is in the opposite direction, pointing away from the thrust member 3, which will lead to the deterioration of the axial tension, that is, it is impossible for the inner ring portion 131 of the first bearing member 13 to press the thrust member 3 and achieve the seal between the thrust member 3 and the inner ring portion 131.

[0062] And / or, the inner peripheral wall surface of the mating structure 1121 is constructed as an arc-shaped surface, a straight surface, or an irregular surface.

[0063] In other words, the inner peripheral wall of the mating structure 1121 can be arc-shaped, linear, or irregularly decreasing. For example, the arc-shaped surface can be a circular arc, an elliptical arc, or any other arbitrary arc-shaped surface, as long as it decreases in the direction away from the thrust member 3. The specific decreasing method of the inner peripheral wall of the mating structure 1121 can be flexibly adjusted according to actual needs and is not limited to what is described in this embodiment.

[0064] And / or, the inner diameter of the mating structure 1121 is configured to decrease linearly in the axial direction away from the thrust member 3.

[0065] Specifically, such as Figure 3 As shown, the inner diameter of the mating structure 1121 decreases linearly in the axial direction away from the thrust member 3, that is, the inner diameter of the mating structure 1121 gradually decreases in a straight line in the cross section. As a result, the inner peripheral wall of the mating structure 1121 can form a certain taper in the axial direction (as shown by angle θ in the figure), so that the inner ring portion 131 of the first bearing member 13 forms a certain taper in the axial direction, which in turn can cause the crankshaft 2 to generate an axial pulling force pointing towards the thrust member 3, so that the inner ring portion 131 of the first bearing member 13 can press tightly against the thrust member 3.

[0066] In some embodiments, the mating structure 1121 includes at least two cylindrical sub-hole walls 1122, that is, the mating structure 1121 may include two, three, four or even more cylindrical sub-hole walls 1122, and the inner diameter of the one of two adjacent cylindrical sub-hole walls 1122 closer to the thrust member 3 is larger than the inner diameter of the one farther away from the thrust member 3. Thus, the inner diameter of the mating structure 1121 can be stepped down in the axial direction, thereby allowing the outer ring portion 132 of the first bearing member 13 to drive the inner ring portion 131 to be pre-tightened in the direction closer to the thrust member 3. The crankshaft 2 can generate an axial pulling force pointing towards the thrust member 3, thereby achieving a tight seal between the thrust member 3 and the inner ring portion 131 of the first bearing member 13.

[0067] Specifically, such as Figure 4 As shown, the mating structure 1121 includes two connected cylindrical sub-hole walls 1122, as... Figure 4 As shown in the vertical direction, the lower cylindrical sub-hole wall 1122, which is the cylindrical sub-hole wall 1122 close to the thrust member 3, has a larger inner diameter than the upper cylindrical sub-hole wall 1122, which is the cylindrical sub-hole wall 1122 away from the thrust member 3. Thus, the inner diameter of the mating structure 1121 decreases axially in the direction away from the thrust member 3, and further allows the inner ring portion 131 of the first bearing member 13 to form a certain angle with the axial direction.

[0068] It should be noted that the number of cylindrical sub-hole walls 1122 is not limited to that shown in this embodiment, and can be flexibly adjusted according to actual needs, as long as the inner diameter of the cylindrical sub-hole walls 1122 decreases in the direction away from the thrust member 3.

[0069] And / or, the mating structure 1121 includes at least one cylindrical sub-hole wall 1122 and at least one tapered sub-hole wall 1123. That is, the mating structure 1121 may include one, two, three or more cylindrical sub-hole walls 1122 and one, two, three or more tapered sub-hole walls 1123. The inner diameter of the tapered sub-hole wall 1123 gradually decreases in the direction away from the thrust member 3, and the inner diameter of the cylindrical sub-hole wall 1122 also gradually decreases in the direction away from the thrust member 3. Thus, the inner diameter of the mating structure 1121 can be reduced axially, thereby allowing the outer ring portion 132 of the first bearing member 13 to drive the inner ring portion 131 to be pre-tightened in the direction closer to the thrust member 3. The crankshaft 2 can generate an axial pulling force pointing towards the thrust member 3, thereby achieving a tight seal between the thrust member 3 and the inner ring portion 131 of the first bearing member 13.

[0070] Specifically, such as Figure 5 As shown, the mating structure 1121 includes a cylindrical sub-hole wall 1122 and a conical sub-hole wall 1123 connected together, as... Figure 5 As shown in the vertical direction, the lower section of the mating structure 1121 is a cylindrical sub-hole wall 1122, and the upper section of the mating structure 1121 is a tapered sub-hole wall 1123. The inner diameter of the tapered sub-hole wall 1123 gradually decreases upwards, that is, it gradually decreases in the direction away from the thrust member 3. The inner diameter of the cylindrical sub-hole wall 1122 is greater than the maximum inner diameter of the tapered sub-hole wall 1123. Thus, the inner diameter of the mating structure 1121 decreases in the axial direction away from the thrust member 3, which further allows the inner ring portion 131 of the first bearing member 13 to form a certain angle with the axial direction.

[0071] It should be noted that the number of cylindrical sub-hole walls 1122 and conical sub-hole walls 1123 is not limited to that shown in this embodiment, and can be flexibly adjusted according to actual needs, as long as the inner diameter of the cylindrical sub-hole wall 1122 and the inner diameter of the conical sub-hole wall 1123 decrease in the direction away from the thrust member 3.

[0072] In some embodiments, the inner diameter of the end of the mating structure 1121 away from the thrust member 3 is D1, and the inner diameter of the end of the mating structure 1121 close to the thrust member 3 is D2, where D1 < D2.

[0073] Specifically, such as Figures 2-5 As shown, D1 is the inner diameter of the end of the mating structure 1121 furthest from the thrust member 3, i.e., the inner diameter of the end furthest from the thrust member 3. D2 is the inner diameter of the end of the mating structure 1121 closest to the thrust member 3, i.e., the inner diameter of the end closest to the thrust member 3. D1 < D2, meaning that the inner diameter of the end of the mating structure 1121 furthest from the thrust member 3 is smaller than the inner diameter of the inner circumferential wall of the first bearing hole 112 at the end closest to the thrust member 3. Thus, the inner diameter of the mating structure 1121 is reduced.

[0074] It is understandable that the greater the difference between the values ​​of D1 and D2, the greater the change in the inner diameter of the mating structure 1121 along the axial direction, i.e., the greater the decrease. The smaller the difference between the values ​​of D1 and D2, the smaller the change in the inner diameter of the mating structure 1121 along the axial direction, i.e., the smaller the decrease. Consequently, the angle between the inner ring portion 131 of the first bearing member 13 and the axial direction is larger or smaller. Therefore, by setting D1 to be less than D2, axial pre-tightening of the inner ring portion 131 toward the thrust member 3 can be achieved.

[0075] And / or, the maximum value of the change in the inner diameter of the mating structure 1121 is less than the clearance of the first bearing member 13.

[0076] In other words, the difference between the inner diameter D1 of the end of the fitting structure 1121 away from the thrust member 3 and the inner diameter D2 of the inner circumferential wall of the first bearing hole 112 near the thrust member 3 needs to be less than the first bearing clearance of the first bearing member 13. Being less than the first bearing clearance can prevent the first bearing member 13 from being excessively squeezed, which would result in excessive rotational resistance, and ensure that the first bearing member 13 can play a smooth rotational bearing role.

[0077] Therefore, while achieving a tight seal between the thrust member 3 and the inner ring 131 of the first bearing member 13, the first bearing member 13 can be prevented from being too tight, thereby ensuring the normal operation of the first bearing member 13, ensuring the flexibility and stability of the first bearing member 13 during operation, and thus improving the reliability of the compressor 100.

[0078] In some embodiments, the mating structure 1121 is configured as a mating protrusion (not shown) protruding from the inner peripheral wall of the first bearing hole 112, the mating protrusion pressing against the outer peripheral wall of the outer ring portion 132.

[0079] That is, a mating protrusion protruding inward a certain distance can be provided on the inner peripheral wall of the first bearing hole 112. The mating protrusion presses against the outer peripheral wall of the outer ring portion 132 and is in an interference fit with the outer ring portion 132. The shape of the mating protrusion can be annular, irregular protrusion, etc., as long as the outer ring portion 132 can be tilted relative to the axial direction of the first bearing hole 112 so that the inner ring portion 131 is pre-tightened toward the thrust member 3.

[0080] In some embodiments, the mating protrusion is configured as an annular protrusion, and the inner diameter of the annular protrusion is smaller than the inner diameter of the first bearing hole 112.

[0081] That is, the inner peripheral wall of the first bearing hole 112 can protrude radially inward by a certain distance to form an annular protrusion, so that the inner diameter of the annular protrusion is smaller than the inner diameter of the first bearing hole 112, and the inner peripheral wall of the annular protrusion is pressed against the outer peripheral wall of the outer ring portion 132.

[0082] And / or, the mating protrusion is constructed as a mating protrusion, there are multiple mating protrusions, and the multiple mating protrusions are spaced apart in the circumferential direction of the first bearing hole 112.

[0083] Multiple mating protrusions can be formed by spaced out radially inward along the circumferential direction of the inner peripheral wall of the first bearing hole 112. The number of mating protrusions can be set to two, three or even more, and they can be evenly spaced out along the circumferential direction of the first bearing hole 112. The inner peripheral wall of the mating protrusion is pressed against the outer peripheral wall of the outer ring portion 132. The surface of the inner peripheral wall of the mating protrusion can be a plane, a slope, an irregular surface, etc.

[0084] In some embodiments, the inner peripheral wall of the annular protrusion is formed with a first mating slope (not shown in the figure), the first mating slope is inclined relative to the axial direction of the first bearing hole 112, and the first mating slope is in contact with and presses against the outer peripheral wall of the outer ring portion 132.

[0085] That is, the inner diameter of the annular protrusion changes along the axial direction to form the first mating inclined surface. For example, the inner diameter of the annular protrusion gradually decreases along the axial direction, so that the first mating inclined surface can be tilted relative to the axial direction of the first bearing hole 112, forming a certain angle with the axial direction. Thus, after the inner peripheral wall of the first mating inclined surface is tightly pressed and connected with the outer peripheral wall of the outer ring 132, the inner ring 131 can be tilted relative to the axial direction of the first bearing hole 112, forming a certain angle with the axial direction. Then, the inner ring 131 is pre-tightened in the direction of the thrust member 3, realizing the seal between the inner ring 131 and the thrust member 3.

[0086] In some embodiments, the mating structure 1121 is configured as a mating part (not shown) installed in the first bearing hole 112, wherein the inner diameter of the mating part is smaller than the inner diameter of the first bearing hole 112.

[0087] The mating structure 1121 is configured as a mating part installed in the first bearing hole 112. That is, the outer peripheral wall of the mating part is pressed and connected to the inner peripheral wall of the first bearing hole 112, and the inner peripheral wall of the mating part is pressed and connected to the outer ring portion 132. The mating part can be separated and disassembled relative to the first bearing part 13, which is flexible and convenient.

[0088] The mating structure 1121 can be constructed as a mating component independent of the first bearing hole 112. When assembling the crankshaft 2 and the first bearing component 13, the mating component can be installed in the first bearing hole 112 first to fix the two into a whole, so that the actual assembly inner diameter in the first bearing hole 112 changes. Then, they are assembled together with the crankshaft 2 to achieve tilted installation. The structure is simple and easy to install. It does not require significant modification to the structure of the first bearing hole 112, thus reducing the setup cost.

[0089] In some embodiments, the mating component is press-fitted into the inner peripheral wall of the first bearing hole 112 to achieve a tight connection between the mating component and the inner peripheral wall of the first bearing hole 112, thereby facilitating the pre-tightening of the inner ring 131 toward the thrust member 3 after the mating component is installed and fitted with the outer ring portion 132.

[0090] And / or, the inner peripheral wall of the mating part is formed with a second mating slope, the second mating slope is inclined relative to the axial direction of the first bearing hole 112, and the second mating slope is in contact with and presses against the outer peripheral wall of the outer ring portion 132.

[0091] The inner diameter of the inner circumferential wall of the mating part can be gradually reduced or gradually increased to form a second mating inclined surface. This allows the second mating inclined surface to be inclined relative to the axial direction of the first bearing hole 112, forming a certain angle with the axial direction. As a result, after the inner circumferential wall of the second mating inclined surface is tightly pressed and connected to the outer circumferential wall of the outer ring 132, the inner ring 131 can be inclined relative to the axial direction of the first bearing hole 112, forming a certain angle with the axial direction. Consequently, the inner ring 131 is pre-tightened towards the thrust member 3, achieving a seal between the inner ring 131 and the thrust member 3.

[0092] In some embodiments, the compressor 100 further includes an eccentric pin 9 and an eccentric sleeve 4. The other end of the crankshaft 2 is provided with a first eccentric hole, and the eccentric sleeve 4 is provided with a second eccentric hole. One end of the eccentric pin 9 is connected to the first eccentric hole, and the other end of the eccentric pin 9 is connected to the second eccentric hole. The moving scroll 8 is sleeved on the outside of the eccentric sleeve 4.

[0093] like Figure 1 As shown, the crankshaft 2 has a first eccentric hole at one end near the moving scroll 8, and the eccentric sleeve 4 has a second eccentric hole corresponding to the first eccentric hole. By connecting one end of the eccentric pin 9 to the first eccentric hole and the other end of the eccentric pin 9 to the second eccentric hole, the crankshaft 2 and the eccentric sleeve 4 are connected. The moving scroll 8 is sleeved outside the eccentric sleeve 4, that is, the eccentric sleeve 4 is set inside the moving scroll 8. The moving scroll 8 can move together with the eccentric sleeve 4. Thus, when the crankshaft 2 moves, the eccentric pin 9 can drive the eccentric sleeve 4 and the moving scroll 8 to move inside the stationary scroll 7.

[0094] The axis of the first eccentric hole is offset from the axis of the crankshaft 2, the axis of the second eccentric hole is offset from the axis of the eccentric sleeve 4, and the axis of the crankshaft 2 is offset from the axis of the eccentric sleeve 4.

[0095] Thus, the crankshaft 2 can drive the eccentric sleeve 4 and the moving scroll 8 to rotate eccentrically relative to the stationary scroll 7, which is beneficial for compressing the gas in the compression chamber 81.

[0096] In some embodiments, the moving scroll 8 is formed with a second bearing hole that opens toward the first bearing hole 112. A second bearing member is provided in the second bearing hole, and an eccentric sleeve 4 is installed in the second bearing member to be rotatably supported on the moving scroll 8 by the second bearing member.

[0097] Specifically, such as Figure 1 As shown, the moving scroll 8 has a second bearing hole that is open to the first bearing hole 112 or to the mounting bracket 11. The second bearing component is installed in the second bearing hole, and the eccentric sleeve 4 is installed in the second bearing component and press-fitted with the second bearing component. Thus, the eccentric sleeve 4 is rotatably supported in the moving scroll 8 through the second bearing component, reducing the friction between the eccentric sleeve 4 and the moving scroll 8.

[0098] In some embodiments, the housing 1 includes a first housing 14 and a second housing 15, which are respectively connected to the two sides of the mounting bracket 11. The first housing 14 and the mounting bracket 11 define a first cavity 101, and the second housing 15 and the mounting bracket 11 define a second cavity 102.

[0099] Specifically, as shown in Figure 1, the housing 1 also includes a first housing 14 and a second housing 15. The first housing 14 is the housing on the left side, and the first housing 14 is installed and cooperates with the mounting bracket 11 to define the first cavity 101. The second housing 15 is the housing on the right side, and the second housing 15 is installed and cooperates with the mounting bracket 11 to define the second cavity 102. The moving scroll 8 and the stationary scroll 77 are both installed in the second cavity 102 of the second housing 15 to protect the moving scroll 8 and the stationary scroll 7. Thus, the first housing 14 and the second housing 15 are respectively connected to both sides of the mounting bracket 11 to protect their internal components. In actual design, the first housing 14 can be a low-pressure housing, and the second housing 15 can be a high-pressure housing.

[0100] The housing 1 also includes a cover plate 16, which covers the first housing 14. The motor part 52 is located inside the first housing 14 to prevent damage to the motor part 52. The second housing 15 and the first housing 14 can also ensure the sealing of the compressor 100, prevent gas leakage, and ensure the normal operation of the compressor 100.

[0101] In some embodiments, the high-pressure housing is suitable for electric compressors using R134a, R744, R290, and R1234yf refrigerants to ensure that the compressor 100 can withstand certain pressures and temperatures, thus ensuring the reliability of the compressor 100.

[0102] The present invention also proposes an air conditioning device.

[0103] According to an embodiment of the present invention, an air conditioning device is provided with a compressor 100 as described above. The air conditioning device comprises a compressor 100, a condenser, an expansion valve, and an evaporator. In the compressor 100, a mating structure 1121 is provided within a first bearing hole 112. This mating structure 1121 is installed and fitted with an outer ring portion 132, and the outer ring portion 132 is axially inclined relative to the first bearing hole 112 so that the inner ring portion 131 is pre-tightened towards the thrust member 3. This ensures that the crankshaft 2 can consistently generate an axial component force pointing towards the thrust member 3 during operation, allowing the inner ring portion 131 of the first bearing member 13 to consistently press against the thrust member 3. This achieves a tight seal between the inner ring portion 131 of the first bearing member 13 and the thrust member 3, preventing lubricant leakage, improving the reliability of the compressor 100, and consequently improving the reliability and service life of the air conditioning device.

[0104] The present invention also proposes a vehicle.

[0105] According to an embodiment of the present invention, the vehicle is equipped with the above-mentioned air conditioning device, wherein the air conditioning device can regulate the temperature inside the vehicle and adjust and control the temperature, humidity, air cleanliness and air flow inside the vehicle to an optimal state, so as to provide a comfortable riding environment for the occupants.

[0106] According to embodiments of the present invention, by using the air conditioning device described above, the reliability of the vehicle can be improved and a better driving experience can be obtained.

[0107] 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 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.

[0108] Although embodiments of the 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 invention, the scope of which is defined by the claims and their equivalents.

Claims

1. A compressor, characterized in that, include: The housing and the mounting bracket are fitted together to define a first cavity and a second cavity. The first cavity contains a motor part. The mounting bracket has a first bearing hole. The first bearing hole contains a first bearing element. The first bearing element includes an inner ring portion, an outer ring portion, and a rolling element located between the inner ring portion and the outer ring portion. The space between the inner ring portion and the outer ring portion is connected to an oil supply circuit. A crankshaft and a compression component are provided. The compression component is located in the second cavity and includes a moving scroll and a stationary scroll, which together define the compression cavity. The crankshaft is interference-fitted through the inner ring portion and is rotatably supported on the mounting bracket by the first bearing. One end of the crankshaft is located in the first cavity, and the moving scroll is eccentrically connected to the other end of the crankshaft. The motor is poweredly connected to the moving scroll through the crankshaft to drive the moving scroll to rotate eccentrically relative to the stationary scroll to compress the medium in the compression cavity. A thrust member is installed in the mounting bracket. The thrust member is located at the end of the first bearing member away from the moving scroll to limit the inner ring portion axially. A fitting structure is provided in the first bearing hole. The fitting structure is fitted with the outer ring portion and tilts the outer ring portion axially relative to the first bearing hole to pre-tighten the inner ring portion toward the thrust member.

2. The compressor according to claim 1, characterized in that, The mounting bracket includes a limiting stop portion located at the end of the first bearing hole away from the moving scroll plate. The limiting stop portion has a through hole through which the crankshaft extends into the first bearing hole. The limiting stop portion also has a limiting mounting groove that opens toward the first bearing hole. The thrust stop is located within the limiting mounting groove and is directly opposite the inner ring portion in the axial direction of the crankshaft, while the limiting stop portion is directly opposite the outer ring portion in the axial direction of the crankshaft.

3. The compressor according to claim 1 or 2, characterized in that, At least a portion of the inner peripheral wall of the first bearing hole is configured as the mating structure, wherein the mating structure is configured such that the inner diameter dimensions are different at at least two positions in the axial direction.

4. The compressor according to claim 3, characterized in that, The inner diameter of the mating structure is configured to decrease axially in a direction away from the thrust member; And / or, the inner peripheral wall surface of the mating structure is constructed as an arc-shaped surface, a straight surface, or an irregular surface; And / or, the inner diameter of the mating structure is configured to decrease linearly in the axial direction away from the thrust member.

5. The compressor according to claim 3, characterized in that, The mating structure includes at least two cylindrical sub-hole walls, and the inner diameter of the one of the two adjacent cylindrical sub-hole walls closer to the thrust member is larger than the inner diameter of the one farther away from the thrust member; And / or, the mating structure includes at least one cylindrical sub-hole wall and at least one tapered sub-hole wall, and the inner diameter of the tapered sub-hole wall gradually decreases in the direction away from the thrust member.

6. The compressor according to claim 3, characterized in that, The inner diameter of the end of the mating structure away from the thrust member is D1, and the inner diameter of the end of the mating structure close to the thrust member is D2, where D1 < D2. And / or, the maximum value of the change in the inner diameter of the mating structure is less than the clearance of the first bearing component.

7. The compressor according to claim 1 or 2, characterized in that, The mating structure is configured as a mating protrusion protruding from the inner peripheral wall of the first bearing hole, which abuts against the outer peripheral wall of the outer ring portion.

8. The compressor according to claim 7, characterized in that, The mating protrusion is constructed as an annular protrusion, and the inner diameter of the annular protrusion is smaller than the inner diameter of the first bearing hole. And / or, the mating protrusion is constructed as a mating protrusion, there are multiple mating protrusions, and the multiple mating protrusions are spaced apart in the circumferential direction of the first bearing hole.

9. The compressor according to claim 8, characterized in that, The inner peripheral wall of the annular protrusion is formed with a first mating inclined surface. The first mating inclined surface is inclined relative to the axial direction of the first bearing hole, and the first mating inclined surface is in contact with and presses against the outer peripheral wall of the outer ring portion.

10. The compressor according to claim 1 or 2, characterized in that, The mating structure is configured as a mating part installed in the first bearing hole, and the inner diameter of the mating part is smaller than the inner diameter of the first bearing hole.

11. The compressor according to claim 10, characterized in that, The fitting is press-fitted into the inner circumferential wall of the first bearing hole; And / or, the inner peripheral wall of the mating part is formed with a second mating slope, the second mating slope being inclined relative to the axial direction of the first bearing hole, and the second mating slope being in contact with and pressing against the outer peripheral wall of the outer ring portion.

12. The compressor according to claim 1 or 2, characterized in that, It also includes an eccentric pin and an eccentric sleeve. The other end of the crankshaft is provided with a first eccentric hole, the eccentric sleeve is provided with a second eccentric hole, one end of the eccentric pin is connected to the first eccentric hole, the other end of the eccentric pin is connected to the second eccentric hole, and the moving scroll is sleeved on the outside of the eccentric sleeve. The axis of the first eccentric hole is offset from the axis of the crankshaft, the axis of the second eccentric hole is offset from the axis of the eccentric sleeve, and the axis of the crankshaft is offset from the axis of the eccentric sleeve.

13. The compressor according to claim 12, characterized in that, The moving scroll has a second bearing hole that opens toward the first bearing hole. A second bearing component is provided in the second bearing hole. The eccentric sleeve is installed in the second bearing component to support the moving scroll through the rotation of the second bearing component.

14. The compressor according to claim 1, characterized in that, The housing includes a first housing and a second housing, which are respectively connected to both sides of the mounting bracket. The first housing and the mounting bracket define the first cavity, and the second housing and the mounting bracket define the second cavity.

15. An air conditioning device, characterized in that, The compressor is provided as described in any one of claims 1-14.

16. A vehicle, characterized in that, The device is equipped with a compressor as described in any one of claims 1-14 or an air conditioning unit as described in claim 15.

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