Compressor, air conditioning device and vehicle

Abstract

The compressor comprises a shell and a mounting support, a first bearing hole is formed in the mounting support, a first bearing part is arranged in the first bearing hole, the first bearing part comprises an inner ring part and an outer ring part, the space between the inner ring part and the outer ring part communicates with an oil supply path, and the outer ring part is arranged in the inner ring part; the outer ring part is in interference fit with the first bearing hole; the motor part is in power connection with the orbiting scroll through a crankshaft so as to drive the orbiting scroll to eccentrically rotate relative to the static scroll to compress a medium in the compression cavity; the thrust part is installed in the installation support, the thrust part is located at one end of the first bearing part to limit the inner ring part in the axial direction, a matching structure is arranged outside the crankshaft, and the matching structure is installed and matched with the inner ring part and enables the inner ring part to incline relative to the axial direction of the crankshaft so that the inner ring part can be pre-tightened towards the thrust part. According to the compressor, tight sealing between the inner ring part of the first bearing part and the thrust part can be achieved, lubricating oil leakage is prevented, and the reliability of the compressor is improved.

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 containing a motor portion, the mounting bracket having a first bearing hole, the first bearing hole containing 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, the outer ring portion being interference-fitted with the first bearing hole; 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 passing through the inner ring portion and being fitted together with the motor portion. The inner ring portion is interference-fitted to be rotatably supported on the mounting bracket by the first bearing member. 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 and 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 on the outside of the crankshaft. The fitting structure is fitted with the inner ring portion and tilts the inner ring portion axially relative to the crankshaft to preload the inner ring portion toward the thrust member.

[0006] According to an embodiment of the present invention, the compressor has a mating structure on the outside of the crankshaft. The mating structure is installed and mated with the inner ring portion, and the inner ring portion is inclined axially relative to the crankshaft 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 mounted at the limiting mounting groove and is axially aligned with the inner ring portion of the crankshaft, and the limiting stop portion and the outer ring portion are axially aligned with the crankshaft.

[0008] According to some embodiments of the compressor of the present invention, at least a portion of the outer peripheral wall of the crankshaft is formed as the mating structure, and the mating structure is configured to have different outer diameter dimensions at at least two locations along the axial direction of the crankshaft.

[0009] According to some embodiments of the compressor of the present invention, the outer diameter of the mating structure is configured to decrease axially in a direction away from the thrust member; and / or, the outer peripheral wall surface of the mating structure is configured as an arcuate surface, a straight surface, or an irregular surface; and / or, the outer 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-shaft segments, and the outer diameter of one of two adjacent cylindrical sub-shaft segments closer to the thrust member is greater than the outer diameter of the one farther away from the thrust member; and / or, the mating structure includes at least one cylindrical sub-shaft segment and at least one tapered sub-shaft segment, and the outer diameter of the tapered sub-shaft segment gradually decreases in the direction away from the thrust member.

[0011] According to some embodiments of the compressor of the present invention, the outer diameter of the end of the mating structure away from the thrust member is D1, and the outer diameter of the end of the mating structure near the thrust member is D2, where D1 < D2; and / or, the maximum value of the change in the outer 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 outer peripheral wall of the crankshaft, the mating protrusion pressing against the inner peripheral wall of the inner ring portion.

[0013] According to some embodiments of the compressor of the present invention, the mating protrusion is constructed as an annular protrusion, the outer diameter of the annular protrusion being larger than the outer diameter of the crankshaft; 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 crankshaft.

[0014] According to some embodiments of the compressor of the present invention, the outer 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 crankshaft, and the first mating inclined surface being in contact with and pressing against the inner peripheral wall of the inner ring portion.

[0015] According to some embodiments of the compressor of the present invention, the mating structure is configured as a mating part sleeved outside the crankshaft, wherein the outer diameter of the mating part is larger than the outer diameter of the crankshaft.

[0016] According to some embodiments of the compressor of the present invention, the fitting component is interference-fitted to the outer peripheral wall of the crankshaft; and / or, the outer peripheral wall of the fitting component is formed with a second fitting slope, the second fitting slope being inclined relative to the axial direction of the crankshaft, and the second fitting slope being in contact with and pressing against the inner peripheral wall of the inner 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 4This 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 112, through hole 1121, limiting mounting groove 1122, first bearing hole 111, first bearing component 12, inner ring 121, outer ring 122, rolling element 123, first housing 14, second housing 15, cover plate 16.

[0037] Thrust component 2, crankshaft 3, mating structure 31, cylindrical sub-shaft section 311, tapered sub-shaft section 312, eccentric sleeve 4, electrical control unit 51, motor unit 52, stationary scroll 7, moving scroll 8, compression chamber 81, eccentric pin 9. 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 121 of the first bearing member 12 and the thrust member 2, 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 thrust member 2, a crankshaft 3, and a compression component.

[0043] The housing 1 is used to install and protect the internal components. The housing 1 is installed and fitted with the mounting bracket 11 to define the first cavity 101 and the second cavity 102. The first cavity 101 is provided with the motor part 52, and the compression component is located in the second cavity 102. The compression component includes a moving scroll 8 and a stationary scroll 7. The mounting bracket 11 is used to install the first bearing 12 and the thrust member 2. One end of the crankshaft 3 can be inserted into the mounting bracket 11 and is rotatably supported in the mounting bracket 11 by the first bearing 12.

[0044] The mounting bracket 11 has a first bearing hole 111, and a first bearing component 12 is provided in the first bearing hole 111. The first bearing component 12 includes an inner ring portion 121, an outer ring portion 122, and a rolling element 123 located between the inner ring portion 121 and the outer ring portion 122. The space between the inner ring portion 121 and the outer ring portion 122 is connected to the oil supply circuit, and the outer ring portion 122 is interference-fitted with the first bearing hole 111. In other words, the mounting bracket 11 has a first bearing hole 111 extending axially. The first bearing member 12 is installed in the first bearing hole 111. The outer ring portion 122 of the first bearing member 12 is in abutting contact with the inner peripheral wall of the first bearing hole 111. The inner ring portion 121 is coaxially installed in the outer ring portion 122. The rolling element 123 is disposed between the inner ring portion 121 and the outer ring portion 122, meaning that the inner ring portion 121 can rotate relative to the outer ring portion 122 through the rolling element 123. The outer peripheral wall of the outer ring portion 122 is interference-fitted with the first bearing hole 111, which can achieve a tight connection between the first bearing member 12 and the mounting bracket 11, preventing axial movement of the first bearing member 12. The space between the inner ring portion 121 and the outer ring portion 122 is connected to the oil supply circuit, allowing lubricating oil in the oil supply circuit to enter the space between the inner ring portion 121 and the outer ring portion 122, thereby lubricating the first bearing member 12. The rolling element 123 can be constructed as a cylindrical roller.

[0045] The crankshaft 3 passes through the inner ring portion 121 and is interference-fitted with the inner ring portion 121 to be rotatably supported on the mounting bracket 11 via the first bearing member 12. That is, the crankshaft 3 can pass through the inner ring portion 121, meaning that the outer peripheral wall of the crankshaft 3 can press against the inner ring portion 121 of the first bearing member 12. This allows the crankshaft 3 to be rotatably supported in the mounting bracket 11 via the first bearing member 12. When the crankshaft 3 rotates, the rotation of the first bearing member 12 reduces the friction between the crankshaft 3 and the mounting bracket 11. Furthermore, the interference fit between the crankshaft 3 and the inner ring portion 121 of the first bearing member 12 ensures a tight connection between the first bearing member 12 and the crankshaft 3, preventing axial movement of the crankshaft 3 and thus achieving precise power transmission. At the same time, the end face of the first bearing hole 111 can limit the outer ring portion 122 of the first bearing member 12, preventing axial movement of the first bearing member 12.

[0046] The motor unit 52 drives the crankshaft 3 to rotate, that is, the motor unit 52 provides power to the crankshaft 3 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 3 is located in the first chamber 101, and the moving scroll 8 is eccentrically connected to the other end of the crankshaft 3. The motor unit 52 is connected to the crankshaft 3 via the crankshaft 3 and the moving scroll 8. The moving scroll 8 is powered to drive its eccentric rotation relative to the stationary scroll 7, thereby compressing the medium within the compression chamber 81. Specifically, in actual operation, the end of the crankshaft 3 closest to the motor unit 52 is powered to the motor unit 52 within the first chamber 101, while the end of the crankshaft 3 furthest from the motor unit 52 is powered to the moving scroll 8 within the second chamber 102. The motor unit 52 drives the crankshaft 3 to rotate within the mounting bracket 11. This rotation of the crankshaft 3, in turn, causes the moving scroll 8 to rotate eccentrically relative to the stationary scroll 7, thus transmitting power from the motor unit 52 to the moving scroll 8. At this time, the stationary scroll 7 is stationary relative to the moving scroll 8, and the movement of the moving 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.

[0047] In addition, the inner ring portion 121 and the outer ring portion 122 of the first bearing component 12 are separable, that is, the inner ring portion 121 and the outer ring portion 122 can be disassembled relative to each other, which is flexible and convenient.

[0048] Furthermore, the thrust member 2 is installed inside the mounting bracket 11. The thrust member 2 is located at the end of the first bearing member 12 away from the moving scroll to limit the inner ring portion 121 axially. That is, the thrust member 2 can be constructed as a ring, installed between the mounting bracket 11 and the first bearing member 12, and sleeved on the outer periphery of the crankshaft 3. The end of the thrust member 2 facing the first bearing member 12 is pressed against the inner ring portion 121 of the first bearing member 12, and the end away from the first bearing member 12 is pressed against the inner wall of the mounting bracket 11. Thus, the thrust member 2 axially presses against the first bearing member 12 and the mounting bracket 11, which can limit the first bearing member 12 and prevent the first bearing member 12 from moving axially.

[0049] The crankshaft 3 is provided with a mating structure 31, which is installed and mated with the inner ring 121 and tilts the inner ring 121 relative to the axial direction of the crankshaft 3 so that the inner ring 121 is pre-tightened toward the thrust member 2.

[0050] Specifically, a mating structure 31 can be provided on the outer peripheral wall of the crankshaft 3. The mating structure 31 can be configured to have a certain inclination relative to the axial direction or an irregular shape, so that after the mating structure 31 and the inner ring 121 are interference-fitted, the outer peripheral wall of the mating structure 31 can generate a certain extrusion force on the inner peripheral wall of the inner ring 121, causing the inner ring 121 to be inclined relative to the axial direction of the crankshaft 3, that is, to form a certain angle relative to the axial direction, so that the inner ring 121 is pre-tightened toward the thrust member 2. In other words, the inner ring 121 is pre-tightened toward the thrust member 2, reducing the gap between the thrust member 2 and the inner ring 121, so that the two are tightly pressed together, thereby achieving a seal between the inner ring 121 and the thrust member 2.

[0051] Therefore, after the first bearing component 12 is installed into the first bearing hole 111 and one end of the crankshaft 3 is inserted into the inner ring portion 121, due to the mating structure 31, the inner ring portion 121 of the first bearing component 12 is compressed by the outer peripheral wall of the crankshaft 3, forming a slope that is not parallel to the axial direction, that is, forming a certain angle with the axial direction. This allows the inner ring portion 121 to be pre-tightened towards the thrust member 2 when it mates with the outer ring portion 122, achieving tight pressing between the inner ring portion 121 and the thrust member 2. Consequently, the crankshaft 3 can rotate... The first bearing 12 can always generate an axial force pointing towards the thrust member 2. The inner ring 121 of the first bearing 12 can always press against the thrust member 2, thereby achieving a tight seal between the inner ring 121 of the first bearing 12 and the thrust member 2. Since there is lubricating oil inside the first bearing 12, it can prevent the pressure on both sides of the mounting bracket 11 from leaking through the gap between the thrust member 2 and the inner ring 121 of the first bearing 12, thereby preventing the failure of the oil supply circuit inside the first bearing 12 and improving the reliability of the compressor 100.

[0052] 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 connected to the crankshaft. That is, the crankshaft 3 can rotate through the eccentric sleeve 4 within the moving scroll 8. It also includes an electronic control unit 51, which controls the movement of the motor unit 52.

[0053] According to an embodiment of the present invention, the compressor 100 has a mating structure 31 on the outside of the crankshaft 3. The mating structure 31 is installed and mated with the inner ring portion 121 and the inner ring portion 121 is tilted relative to the axial direction of the crankshaft 3 so that the inner ring portion 121 is pre-tightened toward the thrust member 2. This allows the crankshaft 3 to always generate an axial component force pointing toward the thrust member 2 during the movement, so that the inner ring portion 121 of the first bearing member 12 can always press against the thrust member 2. This achieves a tight seal between the inner ring portion 121 of the first bearing member 12 and the thrust member 2, prevents lubricating oil leakage, and improves the reliability of the compressor 100.

[0054] In some embodiments, the mounting bracket 11 includes a limiting stop portion 112, which is located at one end of the first bearing hole 111 away from the moving scroll 8. The limiting stop portion 112 has a through hole 1121 through which the crankshaft 3 extends into the first bearing hole 111. The limiting stop portion 112 has a limiting mounting groove 1122 that opens toward the first bearing hole 111.

[0055] The thrust member 2 is located in the limiting mounting groove 1122 and is directly opposite the inner ring portion 121 in the axial direction of the crankshaft 3. The limiting stop portion 112 is directly opposite the outer ring portion 122 in the axial direction of the crankshaft 3.

[0056] Specifically, such as Figure 1 and Figure 2 As shown, the mounting bracket 11 is provided with a limiting stop 112. The limiting stop 112 is used to install and limit the first bearing member 12 and the thrust member 2. The limiting stop 112 is located at the end of the first bearing hole 111 away from the moving scroll 8, and a through hole 1121 is formed on the side of the limiting stop 112 near the first cavity 101. The through hole 1121 communicates with the first bearing hole 111 so that the crankshaft 3 can extend into the first bearing hole 111 through the through hole 1121 and connect with the first bearing member 12. Furthermore, the inner peripheral wall of the limiting stop portion 112 is formed with a limiting mounting groove 1122 that opens toward the first bearing hole 111. The limiting mounting groove 1122 is used to install the thrust member 2. Thus, the inner ring portion 121 of the first bearing member 12 can be axially pressed and connected with the thrust member 2 to axially limit the inner ring portion 121. The outer ring portion 122 of the first bearing member 12 is pressed and connected with the inner peripheral wall of the limiting stop portion 112 and axially limited. In this way, the space between the inner ring portion 121 and the outer ring portion 122 can be sealed by the thrust member 2.

[0057] In some embodiments, at least a portion of the outer peripheral wall of the crankshaft 3 is formed as a mating structure 31, that is, a portion of the outer peripheral wall of the crankshaft 3 can be a mating structure 31. The mating structure 31 is the portion of the crankshaft 3 that extends into the first bearing hole 111 and presses against the inner ring portion 121 of the first bearing member 12. The mating structure 31 is configured to have different outer diameters at at least two positions along the axial direction of the crankshaft 3. That is, the outer diameters of the outer peripheral wall of the crankshaft 3 can be set to be different at two, three, or even more positions along the axial direction. In other words, the outer peripheral wall of the crankshaft 3 can form a certain angle with the axial direction of the crankshaft 3, so that the inner ring portion 121 that is interference-fitted with the crankshaft 3 also forms a certain angle with the axial direction of the crankshaft 3. Or the outer peripheral wall of the crankshaft 3 is parallel to the axial direction, but the outer diameter is different at multiple positions, and changes occur, for example, the outer diameter decreases.

[0058] Therefore, after the first bearing component 12 is installed into the first bearing hole 111 and one end of the crankshaft 3 is inserted into the inner ring portion 121, due to the different outer diameter dimensions on the outer peripheral wall of the crankshaft 3 at multiple locations, the inner ring portion 121 of the first bearing component 12 can be squeezed by the outer peripheral wall of the crankshaft 3, forming a slope that is not parallel to the axial direction, that is, forming a certain angle with the axial direction. This allows the inner ring portion 121 to be pre-tightened towards the thrust member 2 when it mates with the outer ring portion 122, achieving tight pressing between the inner ring portion 121 and the thrust member 2, thereby allowing the crankshaft 3 to... During rotation, an axial force pointing towards the thrust member 2 is always generated. The inner ring 121 of the first bearing member 12 can always press against the thrust member 2, thereby achieving a tight seal between the inner ring 121 of the first bearing member 12 and the thrust member 2. Since there is lubricating oil inside the first bearing member 12, it can prevent the pressure on both sides of the mounting bracket 11 from leaking through the gap between the thrust member 2 and the inner ring 121 of the first bearing member 12, thereby preventing the failure of the oil supply circuit inside the first bearing member 12 and improving the reliability of the compressor 100.

[0059] In some embodiments, the outer diameter of the mating structure 31 is configured to decrease axially in the direction away from the thrust member 2. The decreasing method can be step-down, linear, irregular, etc. It is only necessary to satisfy that the outer diameter of the mating structure 31 gradually decreases axially in the direction away from the thrust member 2, so that the inner ring portion 121 of the first bearing member 12 forms a certain angle with the axial direction.

[0060] Therefore, the outer diameter of the mating structure 31 on the side closer to the thrust member 2 is larger than the outer diameter of the mating structure 31 on the side farther from the thrust member 2. This allows the inner ring portion 121, which mates with the mating structure 31, to form a certain angle relative to the axial direction. When the inner ring portion 121 mates with the outer ring portion 122, it can be pre-tightened towards the thrust member 2, thus generating a force towards the thrust member 2. This allows the crankshaft 3 to generate axial tension during movement, or to mitigate the axial tension caused by the tilting of the crankshaft 3. Furthermore, since the outer diameter of the mating structure 31 is... The axial tension decreases in the direction away from the thrust member 2, so the axial tension can always be directed towards one side of the thrust member 2, pressing the thrust member 2 between the inner ring portion 121 of the first bearing member 12 and the inner peripheral wall of the mounting bracket 11, thereby achieving a seal between the inner ring portion 121 of the first bearing member 12 and the thrust member 2. This prevents the pressure on both sides of the mounting bracket 11 from leaking through the gap between the thrust member 2 and the inner ring portion 121 of the first bearing member 12, thereby preventing the leakage of lubricating oil in the first bearing member 12, which could lead to the failure of the oil supply circuit and improve the reliability of the compressor 100.

[0061] like Figures 2-5As shown, the outer peripheral wall end portion of the crankshaft 3 is constructed as a mating structure 31. The inner ring portion 121 of the first bearing member 12 is sleeved on the mating structure 31, and the outer diameter of the mating structure 31 decreases axially in the direction away from the thrust member 2, as shown in the up-down direction in the figure. The outer diameter of the mating structure 31 decreases from bottom to top.

[0062] In addition, such as Figures 6-9 As shown, through simulation calculations, it is verified that when the outer diameter of the mating structure 31 decreases axially in the direction away from the thrust member 2, the crankshaft 3 can generate axial tension or improve the axial tension generated by the tilt of the crankshaft 3, and the direction of the tension is towards the side closer to the thrust member 2. If the outer diameter of the mating structure 31 decreases axially in the direction closer to the thrust member 2, that is, when the decreasing direction is set to the opposite, the direction of the axial tension generated by the crankshaft 3 is in the opposite direction, pointing away from the thrust member 2, which will lead to the deterioration of the axial tension, that is, it is impossible to make the inner ring portion 121 of the first bearing 12 press against the thrust member 2 to achieve the seal between the thrust member 2 and the inner ring portion 121.

[0063] And / or, the outer peripheral wall of the mating structure 31 is constructed as an arc-shaped surface, a straight surface, or an irregular surface.

[0064] In other words, the outer peripheral wall of the mating structure 31 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 2. The specific decreasing method of the outer diameter of the mating structure 31 can be flexibly adjusted according to actual needs and is not limited to what is described in this embodiment.

[0065] And / or, the outer diameter of the mating structure 31 is configured to decrease linearly in the axial direction away from the thrust member 2.

[0066] Specifically, such as Figure 3 As shown, the outer diameter of the mating structure 31 decreases linearly in the axial direction away from the thrust member 2, that is, the outer diameter of the mating structure 31 gradually decreases in a straight line in the cross section. As a result, the outer peripheral wall of the mating structure 31 can form a certain taper in the axial direction (as shown by angle θ in the figure), so that the inner ring portion 121 of the first bearing member 12 forms a certain taper in the axial direction, which in turn can cause the crankshaft 3 to generate an axial pulling force pointing towards the thrust member 2, so that the inner ring portion 121 of the first bearing member 12 can press tightly against the thrust member 2.

[0067] In some embodiments, the mating structure 31 includes at least two cylindrical sub-shaft segments 311, that is, the mating structure 31 may include two, three, four or even more cylindrical sub-shaft segments 311, and the outer diameter of the one of two adjacent cylindrical sub-shaft segments 311 closer to the thrust member 2 is larger than the outer diameter of the one farther away from the thrust member 2. Thus, the outer diameter of the mating structure 31 can be stepped down in the axial direction, thereby allowing the inner ring portion 121 of the first bearing member 12 to be pre-tightened towards the thrust member 2 when it mates with the outer ring portion 122. The crankshaft 3 can generate an axial tensile force pointing towards the thrust member 2, thereby achieving a tight seal between the thrust member 2 and the inner ring portion 121 of the first bearing member 12.

[0068] Specifically, such as Figure 4 As shown, the mating structure 31 includes two connected cylindrical sub-shaft segments 311, as... Figure 4 As shown in the vertical direction, the lower cylindrical sub-shaft segment 311, which is closer to the thrust member 2, has a larger outer diameter than the upper cylindrical sub-shaft segment 311, which is farther away from the thrust member 2. This results in the outer diameter of the crankshaft 3 decreasing axially away from the thrust member 2, and further allows the inner ring portion 121 of the first bearing member 12 to form a certain angle with the axial direction.

[0069] It should be noted that the number of cylindrical sub-shaft segments 311 is not limited to that shown in this embodiment, and can be flexibly adjusted according to actual needs, as long as the outer diameter of the cylindrical sub-shaft segments 311 decreases in the direction away from the thrust member 2.

[0070] And / or, the mating structure 31 includes at least one cylindrical sub-shaft segment 311 and at least one tapered sub-shaft segment 312. That is, the mating structure 31 may include one, two, three or more cylindrical sub-shaft segments 311 and one, two, three or more tapered sub-shaft segments 312. The outer diameter of the tapered sub-shaft segment 312 gradually decreases in the direction away from the thrust member 2, and the outer diameter of the cylindrical sub-shaft segment 311 also gradually decreases in the direction away from the thrust member 2. Thus, the outer diameter of the mating structure 31 decreases axially, which allows the inner ring portion 121 to be pre-tightened in the direction closer to the thrust member 2 when it mates with the outer ring portion 122. The crankshaft 3 can generate an axial tensile force pointing towards the thrust member 2, thereby achieving a tight seal between the thrust member 2 and the inner ring portion 121 of the first bearing member 12.

[0071] Specifically, such as Figure 5 As shown, the mating structure 31 includes a cylindrical sub-shaft segment 311 and a conical sub-shaft segment 312 connected together, as... Figure 5As shown in the vertical direction, the lower part of the mating structure 31 is a cylindrical sub-shaft segment 311, and the upper part of the mating structure 31 is a tapered sub-shaft segment 312. The outer diameter of the tapered sub-shaft segment 312 gradually decreases upward, that is, it gradually decreases in the direction away from the thrust member 2. Thus, the outer diameter of the mating structure 31 decreases in the axial direction away from the thrust member 2, which further allows the inner ring portion 121 of the first bearing member 12 to form a certain angle with the axial direction.

[0072] It should be noted that the number of cylindrical sub-shaft segments 311 and tapered sub-shaft segments 312 is not limited to that shown in this embodiment, and can be flexibly adjusted according to actual needs, as long as the outer diameter of the cylindrical sub-shaft segments 311 and tapered sub-shaft segments 312 decreases in the direction away from the thrust member 2.

[0073] In some embodiments, the outer diameter of the end of the mating structure 31 away from the thrust member 2 is D1, and the outer diameter of the end of the mating structure 31 close to the thrust member 2 is D2, where D1 < D2.

[0074] Specifically, such as Figures 3-5 As shown, D1 is the outer diameter of the end of the mating structure 31 furthest from the thrust member 2, i.e., the outer diameter of the end furthest from the thrust member 2, and D2 is the outer diameter of the end of the mating structure 31 closest to the thrust member 2, i.e., the outer diameter of the end closest to the thrust member 2. Wherein, D1 < D2, that is, the outer diameter of the end of the mating structure 31 furthest from the thrust member 2 is smaller than the outer diameter of the end of the mating structure 31 closest to the thrust member 2, thereby achieving a decrease in the outer diameter of the mating structure 31.

[0075] It is understandable that the greater the difference between the values ​​of D1 and D2, the greater the change in the outer diameter of the mating structure 31 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 outer diameter of the mating structure 31 along the axial direction, i.e., the smaller the decrease. Consequently, the angle between the inner ring portion 121 of the first bearing member 12 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 121 toward the thrust member 2 can be achieved.

[0076] And / or, the maximum value of the change in the outer diameter of the mating structure 31 is less than the clearance of the first bearing component 12.

[0077] In other words, the difference between the outer diameter D1 of the mating structure 31 at the end away from the thrust member 2 and the outer diameter D2 of the mating structure 31 at the end close to the thrust member 2 needs to be less than the first bearing clearance of the first bearing member 12. Being less than the first bearing clearance can prevent the first bearing member 12 from being excessively squeezed, which would result in excessive rotational resistance, and ensure that the first bearing member 12 can play a smooth rotational bearing role.

[0078] Therefore, while achieving a tight seal between the thrust member 2 and the inner ring 121 of the first bearing member 12, the first bearing member 12 can be prevented from being too tight, thereby ensuring the normal operation of the first bearing member 12, ensuring the flexibility and stability of the first bearing member 12 during operation, and thus improving the reliability of the compressor 100.

[0079] In some embodiments, the mating structure is configured as a mating protrusion (not shown in the figure) protruding from the outer peripheral wall of the crankshaft 3, the mating protrusion pressing against the inner peripheral wall of the inner ring portion 121.

[0080] That is, the outer peripheral wall of the crankshaft 3 can protrude outward by a certain distance to form a mating protrusion. The mating protrusion presses against the inner peripheral wall of the inner ring and is in an interference fit with the inner ring 121. The shape of the mating protrusion can be annular, irregular protrusion, etc., as long as the inner ring 121 can be tilted relative to the axial direction of the crankshaft 3 so that the inner ring 121 is pre-tightened toward the thrust member 2.

[0081] In some embodiments, the mating protrusion is configured as an annular protrusion, and the outer diameter of the annular protrusion is larger than the outer diameter of the crankshaft 3.

[0082] That is, the outer peripheral wall of the crankshaft 3 can protrude outward in the radial direction by a certain distance to form an annular protrusion, so that the outer diameter of the annular protrusion is larger than the outer diameter of the crankshaft 3, and the outer peripheral wall of the annular protrusion is pressed and connected to the inner peripheral wall of the inner ring 121.

[0083] 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 crankshaft 3.

[0084] Multiple mating protrusions can be formed by spacing them out radially outward along the circumferential direction on the outer peripheral wall of the crankshaft 3. The number of mating protrusions can be set to two, three or even more, and they can be evenly spaced apart along the circumferential direction of the crankshaft 3. The outer peripheral wall of the mating protrusions is pressed against the inner peripheral wall of the inner ring 121. The surface of the outer peripheral wall of the mating protrusions can be a plane, an inclined plane, an irregular surface, etc.

[0085] In some embodiments, the outer 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 crankshaft 3, and the first mating slope is in contact with and presses against the inner peripheral wall of the inner ring portion 121.

[0086] That is, the outer diameter of the annular protrusion changes along the axial direction to form the first mating inclined surface. For example, the outer 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 crankshaft 3, forming a certain angle with the axial direction. Thus, after the outer peripheral wall of the first mating inclined surface is tightly pressed and connected with the inner peripheral wall of the inner ring 121, the inner ring 121 can be tilted relative to the axial direction of the crankshaft 3, forming a certain angle with the axial direction. Then, the inner ring 121 is pre-tightened towards the thrust member 2, realizing the seal between the inner ring 121 and the thrust member 2.

[0087] In some embodiments, the mating structure 31 is configured as a mating part (not shown in the figure) sleeved on the outside of the crankshaft 3, and the outer diameter of the mating part is larger than the outer diameter of the crankshaft 3.

[0088] The mating structure 31 is configured as a mating part installed outside the crankshaft 3. That is, the outer peripheral wall of the mating part is pressed and connected to the inner peripheral wall of the inner ring 121, and the inner peripheral wall of the mating part is pressed and connected to the outer peripheral wall of the crankshaft 3. The mating part can be separated and disassembled relative to the crankshaft 3, which is flexible and convenient.

[0089] In some embodiments, the mating part is press-fitted to the outer peripheral wall of the crankshaft 3, thereby achieving a tight connection between the mating part and the outer peripheral wall of the crankshaft 3, which in turn facilitates the pre-tightening of the inner ring 121 toward the thrust member 2 after the mating part is installed and fitted with the inner ring 121.

[0090] The mating component can be a separate structural component. When installing the crankshaft 3 and the first bearing component 12, the mating component can be sleeved on the outside of the crankshaft 3 and installed together into the first bearing component 12 to achieve the installation and mating of the mating component and the inner ring 121 of the first bearing component 12. The structure is simple and the installation is convenient.

[0091] And / or, the outer peripheral wall of the mating part is formed with a second mating slope (not shown in the figure), the second mating slope is inclined relative to the axial direction of the crankshaft 3, and the second mating slope is in contact with and presses against the inner peripheral wall of the inner ring portion 121.

[0092] That is, the inner diameter of the outer peripheral wall of the mating part can be gradually reduced or gradually increased to form a second mating slope, so that the second mating slope can be tilted relative to the axial direction of the crankshaft 3, forming a certain angle with the axial direction. Thus, after the outer peripheral wall of the second mating slope is tightly pressed and connected to the inner peripheral wall of the inner ring 121, the inner ring 121 can be tilted relative to the axial direction of the crankshaft 3, forming a certain angle with the axial direction. Then, the inner ring 121 is pre-tightened towards the thrust member 2, realizing the seal between the inner ring 121 and the thrust member 2.

[0093] In some embodiments, the compressor 100 further includes an eccentric pin 9 and an eccentric sleeve 4. The other end of the crankshaft 3 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.

[0094] like Figure 1 As shown, the crankshaft 3 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 3 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 3 moves, the eccentric pin 9 can drive the eccentric sleeve 4 and the moving scroll 8 to move inside the stationary scroll 7.

[0095] The axis of the first eccentric hole is offset from the axis of the crankshaft 3, the axis of the second eccentric hole is offset from the axis of the eccentric sleeve 4, and the axis of the crankshaft 3 is offset from the axis of the eccentric sleeve 4.

[0096] Thus, the crankshaft 3 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.

[0097] In some embodiments, the moving scroll 8 is formed with a second bearing hole that opens toward the first bearing hole 111. 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.

[0098] Specifically, such as Figure 1 As shown, the moving scroll 8 has a second bearing hole that is open to the first bearing hole 111 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.

[0099] 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.

[0100] 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.

[0101] 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.

[0102] In some embodiments, the high-pressure housing is suitable for electric compressors using R134a, R744, R290, and R1234yf refrigerants to ensure that the compressor can withstand certain pressures and temperatures, thus ensuring the reliability of the compressor.

[0103] The present invention also proposes an air conditioning device.

[0104] 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 31 is provided outside the crankshaft 3. The mating structure 31 is installed and mated with an inner ring portion 121, and the inner ring portion 121 is tilted relative to the axial direction of the crankshaft 3 so that the inner ring portion 121 is pre-tightened towards the thrust member 2. This ensures that the crankshaft 3 can always generate an axial component force pointing towards the thrust member 2 during operation, allowing the inner ring portion 121 of the first bearing member 12 to always press against the thrust member 2. This achieves a tight seal between the inner ring portion 121 of the first bearing member 12 and the thrust member 2, preventing lubricating oil leakage, improving the reliability of the compressor 100, and thus improving the reliability and service life of the air conditioning device.

[0105] The present invention also proposes a vehicle.

[0106] 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.

[0107] 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.

[0108] 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.

[0109] 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. The outer ring portion is interference-fitted with the first bearing hole. 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 passes through the inner ring portion and is interference-fitted with the inner ring portion to be 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. The crankshaft is provided with a mating structure, which is installed and mated with the inner ring portion and tilts the inner ring portion relative to the axial direction of the crankshaft so that the inner ring portion is pre-tightened 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 installed at 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 outer peripheral wall of the crankshaft is formed as the mating structure, and the mating structure is configured such that the outer diameter dimensions are different at at least two locations along the axial direction of the crankshaft.

4. The compressor according to claim 3, characterized in that, The outer diameter of the mating structure is configured to decrease axially in a direction away from the thrust member; And / or, the outer peripheral wall surface of the mating structure is constructed as an arc-shaped surface, a straight surface, or an irregular surface; And / or, the outer 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-shaft segments, and the outer diameter of the one of the two adjacent cylindrical sub-shaft segments closer to the thrust member is larger than the outer diameter of the one farther away from the thrust member; And / or, the mating structure includes at least one cylindrical sub-shaft segment and at least one tapered sub-shaft segment, and the outer diameter of the tapered sub-shaft segment gradually decreases in the direction away from the thrust member.

6. The compressor according to claim 3, characterized in that, The outer diameter of the end of the mating structure away from the thrust member is D1, and the outer 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 outer 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 constructed as a mating protrusion protruding from the outer peripheral wall of the crankshaft, and the mating protrusion abuts against the inner peripheral wall of the inner ring portion.

8. The compressor according to claim 7, characterized in that, The mating protrusion is an annular protrusion, and the outer diameter of the annular protrusion is larger than the outer diameter of the crankshaft. 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 crankshaft.

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

10. The compressor according to claim 1 or 2, characterized in that, The fitting structure is configured as a fitting part sleeved on the outside of the crankshaft, and the outer diameter of the fitting part is larger than the outer diameter of the crankshaft.

11. The compressor according to claim 10, characterized in that, The fitting is press-fitted into the outer peripheral wall of the crankshaft; And / or, the outer 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 crankshaft, and the second mating slope being in contact with and pressing against the inner peripheral wall of the inner 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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