CN114320899A - Compressor, air conditioner and vehicle - Google Patents

Abstract

The compressor comprises a crankshaft, a crank pin, an eccentric sleeve and a scroll disk assembly, wherein one end of the crankshaft is provided with an eccentric hole, one end of the crank pin is inserted into the eccentric hole and is in clearance fit with the eccentric hole, the other end of the crank pin is exposed out of the eccentric hole, the eccentric sleeve is fixedly connected or in clearance fit with the other end of the crank pin, and the scroll disk assembly is connected to the eccentric sleeve; because the clearance fit of crank pin and bent axle, can avoid leading to on the bent axle to correspond the thickness of eccentric orfice outside and take place to warp because of the crank pin interference fit in the bent axle to, avoid arousing the problem that the inner retainer ring raceway of the main bearing warp with bent axle complex, and then, avoid arousing the rotatory precision decline of shafting, finally, reduce the vibration of this compressor operation, furtherly, reduce the noise of this compressor operation, make the vibration of this compressor operation low, the noise is low.

Description

Compressor, air conditioner and vehicle

Technical Field

The application relates to the technical field of refrigeration and heating, in particular to a compressor, an air conditioner and a vehicle.

Background

At present, with the development of new energy automobiles, the requirements of consumers on the noise, vibration and durability of the air conditioner compressor are further improved.

Fig. 1 and 2 are sectional views of a scroll compressor 100' of a type currently used in a vehicle. Generally, the scroll compressor 100 ' has a compact structural design, and in order to improve the strength of the crankshaft assembly, the crankshaft assembly is designed in a split structure, that is, an eccentric hole 1 ' is formed in a crankshaft 2 ', a crank pin 3 ' (also an eccentric pin) is inserted into the eccentric hole 1 ', and the crankshaft 2 ' and the crank pin 3 ' are connected into a whole in an interference fit manner. Since the crankshaft 2 'and the crank pin 3' are eccentrically disposed, the wall thickness between the outer peripheral surface of the crankshaft 2 'and the inner wall surface of the eccentric hole 1' is uneven, and the wall thickness in the eccentric direction is the thinnest. The interference fit between the crank pin 3 'and the crankshaft 2' is usually the position corresponding to the position of the main bearing.

As described above, the eccentric arrangement of the eccentric hole 1 'causes the portion of the crankshaft 2' to be thin and poor in rigidity, and the crank pin 3 'is press-fitted into the crankshaft 2' with interference, which results in poor roundness of the outer peripheral surface of the corresponding position of the crankshaft 2 ', that is, poor roundness of the outer peripheral surface of the corresponding position of the crankshaft 2' to which the main bearing is attached.

As shown in fig. 2, the crank pin 3 ' is press-fitted to the crankshaft 2 ' with interference and eccentrically fitted thereto, and the roundness of the outer peripheral surface of the crankshaft 2 ' is detected by taking any cross section in the interference region section Q, to obtain the result shown in fig. 3. In fig. 3, the roundness of the outer peripheral surface of the crankshaft 2 'reaches 14.9 μm, and the clearance between the main bearing and the crankshaft 2' is usually within 10 μm after the main bearing is assembled on the crankshaft 2 ', and the roundness value significantly exceeds the clearance value between the main bearing and the crankshaft 2', so that the roundness of the main bearing inner retainer ring is directly affected, and the roundness of the main bearing raceway is poor, thereby causing the deformation of the main bearing inner retainer ring, causing the problems of raceway abrasion, peeling and the like, further causing the vibration abnormality of the shafting of the scroll compressor 100 ', and further causing the noise abnormality or even the failure of the scroll compressor 100'.

Disclosure of Invention

An object of the embodiment of the application is to provide a compressor, aim at solving among the prior art bent axle and crank pin interference fit and arouse that the poor main bearing inner retainer ring that leads to of bent axle peripheral face circularity warp to arouse that compressor shafting vibration is unusual, and then arouse the unusual technical problem of compressor noise.

The embodiment of the application is realized in such a way, and the compressor comprises:

the crankshaft is provided with an eccentric hole at one end;

one end of the crank pin is inserted into the eccentric hole, and the other end of the crank pin is exposed out of the eccentric hole;

the eccentric sleeve is sleeved on the other end of the crank pin; and

a scroll assembly connected to the eccentric sleeve;

one end of the crank pin is in clearance fit with the eccentric hole, and the eccentric sleeve is fixedly connected with the other end of the crank pin or in clearance fit with the other end of the crank pin.

In one embodiment, the compressor further comprises a scroll bearing, the eccentric sleeve is fixedly connected to the other end of the crank pin, the scroll bearing is connected between the outer circumferential surface of the eccentric sleeve and the scroll assembly, and a first boss is arranged on the eccentric sleeve and abuts against the side surface of the scroll bearing.

In one embodiment, the compressor further comprises a scroll bearing and a wear plate, the eccentric sleeve is fixedly connected to the other end of the crank pin, the scroll bearing is connected between the outer circumferential surface of the eccentric sleeve and the scroll assembly, and the wear plate is arranged between the side surface of the scroll bearing facing the scroll assembly and the scroll assembly.

In one embodiment, the compressor further comprises an angular limit pin and a first blocking piece, the eccentric sleeve is fixedly connected to the other end of the crank pin, one end of the angular limit pin penetrates through the eccentric sleeve and extends into the crank shaft to form fixed connection, the other end of the angular limit pin is exposed out of the eccentric sleeve, and the first blocking piece is arranged on a partial section of the angular limit pin, which is exposed out of the eccentric sleeve, and abuts against the eccentric sleeve.

In one embodiment, the compressor further comprises an axial stop assembly connected to the crankshaft and the crankpin and adapted to limit the axial position of the crankpin.

In one embodiment, the axial stopper assembly includes an axial stopper pin inserted into the crankshaft and the crank pin in a radial direction of the crankshaft.

In one embodiment, a first slot communicated with the eccentric hole is formed in the outer peripheral surface of the crankshaft, and a second slot coaxial with and communicated with the first slot is formed in the crank pin; the axial limiting pin is inserted into the first slot and the second slot.

In one embodiment, the second slot extends radially through the crankpin; the end face of the top end of the axial limiting pin is sunk into the first slot.

In one embodiment, the spacing subassembly of axial includes the axial stopper, axial stopper fixed connection in the orientation of bent axle the one end of eccentric cover, the external diameter of the one end of crank pin is greater than the external diameter of the other end of crank pin, be equipped with on the axial stopper along its axial through butt hole, the internal diameter that butts the hole is less than the external diameter of the one end of crank pin and be greater than or equal to the external diameter of the other end of crank pin.

In one embodiment, the other end of the crank pin is fixedly connected with the eccentric sleeve.

In one embodiment, the axial limiting component comprises an axial limiting block and a second blocking piece, the axial limiting block is fixedly connected to one end, facing the eccentric sleeve, of the crankshaft, the outer diameter of one end of the crank pin is larger than the outer diameter of the other end of the crank pin, an abutting hole penetrating in the axial direction of the axial limiting block is formed in the axial limiting block, the inner diameter of the abutting hole is smaller than the outer diameter of one end of the crank pin and larger than or equal to the outer diameter of the other end of the crank pin, the other end of the crank pin penetrates through the axial limiting block and the eccentric sleeve and protrudes out of the eccentric sleeve, the second blocking piece is arranged at the other end of the crank pin and abuts against the end face, facing the scroll disk component, of the eccentric sleeve, and the other end of the crank pin is in clearance fit with the eccentric sleeve.

Another object of the embodiments of the present invention is to provide an air conditioner including the compressor according to the above embodiments.

It is a further object of an embodiment of the present invention to provide a vehicle including the air conditioner of the above embodiment.

The embodiment of the application provides a compressor, air conditioner and vehicle compares in prior art, and its beneficial effect lies in:

the compressor provided by the embodiment of the application can avoid deformation of a thinner part of the outer side of the corresponding eccentric hole on the crankshaft due to interference assembly of the crank pin in the crankshaft through the arrangement of the crank pin inserted in the eccentric hole of the crankshaft and in clearance fit with the crankshaft, thereby avoiding reduction of the rotation precision of the crankshaft and further avoiding the problem of deformation of an inner retainer ring raceway of a main bearing matched with the crankshaft, and finally reducing the rotation vibration of the crankshaft, further reducing the rotation noise of the crankshaft, and ensuring low vibration and low noise of the operation of the compressor; in addition, the air conditioner and the vehicle provided by the embodiment of the application have the advantages that through the design of the compressor, the vibration and the noise of the rotation of the crankshaft in the compressor are low, so that the vibration and the noise of the operation of the air conditioner are low, and further the vibration and the noise of the operation of the vehicle are low.

Drawings

In order to more clearly illustrate the technical solutions in the embodiments of the present application, the drawings needed to be used in the embodiments will be briefly described below, and it is obvious that the drawings in the following description are only some embodiments of the present application, and it is obvious for those skilled in the art to obtain other drawings without creative efforts.

Fig. 1 is a partial longitudinal sectional view schematically illustrating a structure of a compressor in accordance with the related art;

FIG. 2 is a schematic representation of an interference fit of a crankshaft and a crankpin in a prior art compressor;

FIG. 3 is a diagram showing the out-of-roundness of the outer peripheral surface of the crankshaft;

fig. 4 is a schematic longitudinal sectional view of a compressor according to a first embodiment of the present application;

FIG. 5 is an enlarged view at A in FIG. 4;

FIG. 6 is an enlarged view at B in FIG. 4;

FIG. 7 is a schematic longitudinal sectional view of a compressor according to a second embodiment of the present invention;

FIG. 8 is an enlarged view at C in FIG. 7;

FIG. 9 is a schematic longitudinal sectional view of a compressor according to a third embodiment of the present invention;

FIG. 10 is a schematic longitudinal sectional view of a compressor in accordance with a fourth embodiment of the present invention;

FIG. 11 is a schematic longitudinal sectional view of a compressor in accordance with a fifth embodiment of the present invention;

fig. 12 is a schematic longitudinal sectional view of a part of the structure of a compressor according to a sixth embodiment of the present invention.

The designations in the figures mean:

100 '-scroll compressor, 1' -eccentric bore, 2 '-crankshaft, 3' -crank pin;

100 compressor;

1-motor assembly, 11-stator, 12-rotor;

2-crankshaft, 20-eccentric hole, 21-adjusting pin hole, 22-first slot and 23-second mounting hole;

3-crank pin, 30-second slot, 31-second boss, 32-second groove;

4-scroll disk assembly, 40-compression cavity, 41-movable scroll disk, 410-scroll disk bearing mounting hole and 42-static scroll disk;

5-a scroll bearing;

6-eccentric sleeve, 61-first boss;

71-a wearpad;

72-angular limit pin, 720-first groove, 73-first stop, 74-axial limit pin, 75-axial limit block, 750-abutting hole, 751-first mounting hole, 76-fastener, 77-second stop;

91-a low-pressure shell, 910-an air suction port, 92-a support, 93-a throttling element, 94-an oil-gas separator, 940-an air exhaust port, 941-an oil chamber, 95-a main bearing and 96-an auxiliary bearing.

Detailed Description

In order to make the objects, technical solutions and advantages of the present application more apparent, the present application is described in further detail below with reference to the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are merely illustrative of the present application and are not intended to limit the present application.

It will be understood that when an element is referred to as being "secured to" or "disposed on" another element, it can be directly or indirectly secured to or disposed on the other element. When an element is referred to as being "connected to" another element, it can be directly or indirectly connected to the other element. The terms "upper", "lower", "left", "right", and the like, indicate orientations or positional relationships based on the orientations or positional relationships shown in the drawings, and are only for convenience of description, but do not indicate or imply that the referred devices or elements must have a specific orientation, be constructed and operated in a specific orientation, and thus, should not be construed as limiting the patent. The terms "first", "second" and "first" are used merely for descriptive purposes and are not to be construed as indicating or implying relative importance or implicitly indicating the number of technical features. The meaning of "plurality" is two or more unless specifically limited otherwise.

In order to explain the technical solutions of the present application, the following detailed descriptions are made with reference to specific drawings and examples.

Referring to fig. 4 and 5, the present embodiment first provides a compressor 100 including a motor assembly 1, a crankshaft 2, a crank pin 3, an eccentric sleeve 6, and a scroll assembly 4. The motor assembly 1 comprises a stator 11 and a rotor 12 arranged inside the stator 11, and the crankshaft 2 is connected to the rotor 12 of the motor assembly 1, specifically, the crankshaft 2 penetrates through the rotor 12 and is in interference fit with the rotor 12 (or is connected in a key and key slot fit manner), so that the crankshaft 2 can rotate around the central axis of the crankshaft 2 under the driving of the rotor 12; one end of the crankshaft 2 is provided with an eccentric hole 20 extending in an axial direction thereof, one end of the crank pin 3 (defined herein as a first end of the crank pin 3 for convenience of description hereinafter) is inserted into the eccentric hole 20 and is clearance-fitted with the crankshaft 2, and the other end of the crank pin 3 (also defined herein as a second end of the crank pin 3 for convenience of description hereinafter, which is axially connected to the first end) is located outside the eccentric hole 20; the eccentric sleeve 6 is sleeved on the second end of the crank pin 3, and can be in clearance fit or fixed connection (such as interference fit) with the second end, and the scroll plate assembly 4 is connected to the eccentric sleeve 6. As shown in fig. 4, the compressor 100 further includes a main bearing 95 and a bracket 92, an inner retainer of the main bearing 95 is in interference fit with the outer peripheral surfaces of the corresponding crank pin 3 and eccentric hole 20 of the crankshaft 2, and an outer retainer of the main bearing 95 is in interference fit with the bracket 92, so that the crankshaft 2 is supported on the bracket 92 by the main bearing 95 and is in rotational fit with the bracket 92.

The embodiment of the application provides a compressor 100, through inserting crank pin 3 locate in 2's eccentric orfice 20 of bent axle and with 2 clearance fit of bent axle, can avoid leading to the thickness that corresponds the eccentric orfice 20 outside on bent axle 2 to take place to warp because of 3 interference fit of crank pin in bent axle 2, thereby, avoid arousing the problem that the inner collar raceway of 2 complex main bearings 95 of bent axle warp, and then, avoid arousing the decline of shafting rotation precision, finally, reduce the vibration of this compressor 100 operation, furthermore, reduce the noise of this compressor 100 operation, make the vibration of this compressor 100 operation low, the noise is low.

In the present embodiment, referring to fig. 4, scroll assembly 4 is coupled to eccentric sleeve 6, and scroll assembly 4 includes orbiting scroll 41 coupled to eccentric sleeve 6 and fixed scroll 42 coupled to bracket 92. Under the drive of the motor component 1, the crankshaft 2, the crank pin 3 and the eccentric sleeve 6, the movable scroll disk 41 performs revolution translation around the fixed scroll disk 42 and is engaged with the fixed scroll disk 42 to form a compression cavity 40 with a constantly changing volume.

Referring to fig. 4, the compressor 100 according to the embodiment of the present disclosure further includes a low pressure housing 91 and an air-oil separator 94, the motor assembly 1 and the crankshaft 2 are both disposed in the low pressure housing 91, and the low pressure housing 91 is formed with an air inlet 910, where the air inlet 910 is used for communicating with an air outlet of an evaporator (not shown) through a pipeline (not shown). The bracket 92 is connected to the low pressure housing 91, and one end of the crankshaft 2 away from the eccentric hole 20 is mounted on the low pressure housing 91 through an auxiliary bearing 96, specifically, an inner retainer ring of the auxiliary bearing 96 is in interference fit with an outer peripheral surface of the crankshaft 2, and an outer retainer ring of the auxiliary bearing 96 is pressed into the low pressure housing 91 in interference fit. An air outlet (not shown) is formed in the fixed scroll 42, an air inlet (not shown) of the air-oil separator 94 is connected to the air outlet of the fixed scroll 42, an air outlet 940 of the air-oil separator 94 is communicated with an air inlet of a condenser (not shown) through a pipeline (not shown), and an oil chamber 941 of the air-oil separator 94 is communicated to the inside of the low-pressure housing 91 through the throttling element 93.

The operation of the compressor 100 is such that: under the drive of the crankshaft 2, the crank pin 3 and the eccentric sleeve 6, the movable scroll disk 41 makes revolution translation, and the scroll teeth of the movable scroll disk 41 and the scroll teeth of the fixed scroll disk 42 are meshed with each other to form a compression cavity 40 with constantly changing volume. A mixed fluid containing refrigerant and freezing oil is sucked into the interior (low pressure region) of the low pressure housing 91 through the suction port 910, is further sucked into the compression chamber 40 to be compressed, is discharged into the gas-oil separator 94 through the gas outlet of the fixed scroll 42 to be subjected to gas-oil separation, the separated refrigerant is discharged out of the gas-oil separator 94 (high pressure region) through the gas outlet 940, and is continuously circulated among the compressor 100, the condenser and the evaporator to perform heat exchange, and the separated freezing oil enters the oil chamber 941 and is returned into the low pressure housing 91 through the throttling element 93 to be circulated for lubrication.

With continuing reference to fig. 4 and 6, in one embodiment, the compressor 100 further includes a scroll bearing 5, a scroll bearing mounting hole 410 is formed on a side of the orbiting scroll 41 facing the eccentric sleeve 6, the scroll bearing 5 is mounted in the scroll bearing mounting hole 410, specifically, an inner retainer of the scroll bearing 5 is in interference fit with an outer circumferential surface of the eccentric sleeve 6, and an outer retainer of the scroll bearing 5 is in interference fit with an inner side wall of the scroll bearing mounting hole 410. Therefore, the scroll bearing 5 is respectively fixedly connected with the eccentric sleeve 6 and the movable scroll 41, and the crank pin 3 drives the movable scroll 41 to rotate through the eccentric sleeve 6 and the scroll bearing 5.

In this embodiment, the crank pin 3 and the crank shaft 2 are in clearance fit, and the crank pin 3 can still drive the eccentric sleeve 6 to translate in the radial direction of the crank shaft 2, and the eccentric sleeve 6 further drives the movable scroll disk 41 to translate. However, in the axial direction of the crankshaft 2, the crank pin 3 is easily displaced, which may cause the eccentric sleeve 6 to be displaced axially, and further, the eccentric sleeve 6 directly impacts the movable scroll 41 after being displaced axially, which may easily cause abrasion and damage between the eccentric sleeve 6 and the movable scroll 41, and correspondingly generate noise.

In this regard, in one embodiment, as shown in fig. 4 and 6, a solution to the problem of collision between the eccentric sleeve 6 and the orbiting scroll 41 is proposed for the embodiment of the present application. The outer peripheral surface of one end of the eccentric sleeve 6 facing away from the orbiting scroll 41 has a larger outer diameter than that at other positions, thereby forming a first boss 61. The inner retainer ring of the scroll bearing 5 is fitted to the outer peripheral surface of the end of the eccentric sleeve 6 having a smaller outer diameter. Therefore, the eccentric sleeve 6 is axially limited by the abutting of the first boss 61 and the scroll bearing 5, the axial play displacement S of the eccentric sleeve 6 can be significantly reduced or even 0, the eccentric sleeve 6 can be prevented from moving toward the movable scroll 41 along the axial direction of the crankshaft 2 and colliding against the bottom surface of the movable scroll 41, further, collision and abrasion between the eccentric sleeve 6 and the movable scroll 41 can be prevented, and further, noise generated by collision and friction between the eccentric sleeve 6 and the movable scroll 41 can be prevented.

In this embodiment, the eccentric sleeve 6 and the crank pin 3 may be in a clearance fit as described above, or may be in a fixed connection, such as an interference fit. In an alternative embodiment, the eccentric sleeve 6 is fixedly connected with the crank pin 3. The purpose of setting up like this is that, eccentric cover 6 and crank pin 3 fixed connection are as an organic whole, can reduce between the two and radially probably take place collision and the possible relative displacement of axial, and crank pin 3 and eccentric cover 6 are driven by bent axle 2 as an entirety and are made eccentric rotation for crank pin 3 is more steady to the drive that moves vortex dish 41, thereby, the vibration when reducible moves vortex dish 41 and rotates, and then, the noise when reducible moves vortex dish 41 and rotates, and guarantee to move the sealed reliability of meshing between vortex dish 41 and the quiet vortex dish 42.

Referring to fig. 7 and 8, another solution to solve the problem of collision between the eccentric sleeve 6 and the orbiting scroll 41 is proposed in the embodiments of the present application. In this embodiment, the compressor 100 further includes a wear plate 71, and the wear plate 71 is provided between the bottom surface of the scroll bearing mounting hole 410 and the end surface of the eccentric sleeve 6 facing the orbiting scroll 41. That is, the wear-resistant plate 71 occupies the axial gap between the bottom surface of the scroll bearing mounting hole 410 and the end surface of the eccentric sleeve 6 facing the orbiting scroll 41, so that the play displacement amount S of the eccentric sleeve 6 in the axial direction can be significantly reduced to even 0, and similarly, the eccentric sleeve 6 can be prevented from moving toward the orbiting scroll 41 along the axial direction of the crankshaft 2 and colliding against the bottom surface of the orbiting scroll 41, and further, collision and abrasion between the eccentric sleeve 6 and the orbiting scroll 41 can be prevented, and further, noise generated between the eccentric sleeve 6 and the orbiting scroll 41 due to collision and friction can be prevented.

The wear-resistant plate 71 may be made of a material with good wear resistance, such as a metal material, specifically, chromium carbide, high manganese steel, tungsten carbide, or the like, or a plastic material with good wear resistance, specifically, fluoroplastic, nylon, or the like. Optionally, the wearpad 71 is a metal sheet.

The thickness of the wear-resistant plate 71 is set according to the internal dimensions of the compressor 100, so that the amount of displacement S of the eccentric sleeve 6 in the axial direction is preferably as small as possible, and is not particularly limited herein.

In this embodiment, the eccentric sleeve 6 and the crank pin 3 may be in a clearance fit as described above, or may be in a fixed connection, such as an interference fit. In an alternative embodiment, the eccentric sleeve 6 is fixedly connected to the crank pin 3, for example, by interference fit. Thus, the eccentric sleeve 6 and the crank pin 3 are fixedly connected into a whole, possible collision in the radial direction and possible axial relative displacement between the two can be reduced, the crank pin 3 and the eccentric sleeve 6 are driven by the crank shaft 2 as a whole to eccentrically rotate, so that the crank pin 3 can drive the movable scroll disk 41 more stably, further vibration during rotation of the movable scroll disk 41 can be reduced, further, noise during rotation of the movable scroll disk 41 can be reduced, and the sealing reliability of meshing between the movable scroll disk 41 and the fixed scroll disk 42 can be ensured.

Referring to fig. 9, another solution to solve the problem of collision between the eccentric sleeve 6 and the orbiting scroll 41 is provided in the embodiment of the present application. In this embodiment, the compressor 100 further includes an angular limit pin 72 and a first blocking member 73. The angular stopper pin 72 is used to adjust the eccentricity of the eccentric sleeve 6 with respect to the crankshaft 2 so that the movable scroll 41 and the fixed scroll 42 can be engaged with each other. Specifically, an adjusting pin hole 21 extending along the axial direction of the crankshaft 2 is further formed in one end of the crankshaft 2 facing the movable scroll 41, the adjusting pin hole 21 and the eccentric hole 20 are arranged in parallel and at an interval, one end of an angular limit pin 72 is inserted into the adjusting pin hole 21 and fixedly connected with the crankshaft 2, the other end of the angular limit pin 72 penetrates through the eccentric sleeve 6 and protrudes out of the end face of the eccentric sleeve 6 facing the scroll assembly 4, and a first blocking piece 73 is arranged on a partial section of the angular limit pin 72, which is exposed out of the eccentric sleeve 6, and abuts against the end face of the eccentric sleeve 6 facing the movable scroll 41. Accordingly, the first stopper 73 restricts the eccentric sleeve 6 to the angular stopper pin 72, and the eccentric sleeve 6 can be prevented from moving in the axial direction of the angular stopper pin 72, thereby preventing the eccentric sleeve 6 from directly striking the movable scroll 41.

In this case, the eccentric sleeve 6 and the second end of the crank pin 3 may be in a clearance fit as described above, or may be fixedly connected, such as an interference fit. In an alternative embodiment, the eccentric sleeve 6 is fixedly connected to the second end of the crank pin 3, so that the crank pin 3 and the eccentric sleeve 6 are integrally connected. On the basis that the eccentric sleeve 6 is axially restricted by the first blocking member 73, the axial position of the crank pin 3 is also restricted, so that the displacement of the crank pin 3 in the axial direction and the radial collision that may occur between the crank pin and the eccentric sleeve 6 can be reduced, and further, the connection of the crankshaft 2, the crank pin 3, and the eccentric sleeve 6 is more stable, the rotation of the crankshaft 2, the crank pin 3, and the eccentric sleeve 6 is also more stable, and finally, the operation of the compressor 100 is more stable.

One end of the angular limit pin 72 is inserted into the adjusting pin hole 21 of the crankshaft 2 and is in interference fit with the crankshaft 2. In this way, the fixed connection between the angular stopper pin 72 and the crankshaft 2 is achieved, and the axial position of the angular stopper pin 72 is restricted. Of course, without limitation, in alternative embodiments, the angular limit pin 72 and the crankshaft 2 may be fixedly connected in other manners.

It should be noted that, in the above embodiment, although the angular limit pin 72 is also inserted into the crankshaft 2 in an interference manner, since the diameter of the angular limit pin 72 is generally small, and the position of the adjustment pin hole 21 is also closer to the central axis of the crankshaft 2, a relatively thin area is not formed between the adjustment pin hole 21 and the outer peripheral surface of the crankshaft 2, and the interference fit between the angular limit pin 72 and the crankshaft 2 does not significantly affect the roundness of the outer peripheral surface of the crankshaft 2, thereby avoiding causing deformation of the inner retainer raceway of the main bearing 95, further avoiding causing a reduction in the rotational accuracy of the shaft system of the compressor 100, further avoiding causing vibration in the operation of the compressor 100, and avoiding noise in the operation of the compressor 100.

The connection between the angular limit pin 72 and the eccentric sleeve 6 is not limited, and may be interference fit, clearance fit, transition fit, or the like. Optionally, the angular limit pin 72 is in clearance fit with the eccentric sleeve 6, so that the angular limit pin 72 can conveniently penetrate through the eccentric sleeve 6, so as to simplify the assembly step between the angular limit pin 72 and the eccentric sleeve 6 and reduce the assembly cost of the compressor 100. In the specific assembling process, after the angular limit pin 72 passes through the eccentric sleeve 6, the first blocking piece 73 is mounted at one end of the angular limit pin 72 protruding out of the eccentric sleeve 6.

The first blocking member 73 may be annular and is annularly arranged on the angular limit pin 72; alternatively, the first blocking member 73 may be non-annular, but may be configured to protrude relatively in the radial direction on the outer circumferential surface of the angular limit pin 72, in this case, the number of the first blocking members 73 may be one or more, and a plurality of the first blocking members 73 may be arranged along the circumferential direction of the angular limit pin 72.

In an alternative embodiment, referring to fig. 9, the first blocking member 73 is annular and is disposed around the angular limit pin 72. In this regard, the other end of the angular stopper pin 72 (i.e., the end protruding from the eccentric sleeve 6) is formed with an annular first groove 720, and the first blocking member 73 is disposed in the first groove 720, so that the position of the first blocking member 73 itself in the axial direction of the angular stopper pin 72 can be substantially fixed in a simple manner, and further, the axial position of the eccentric sleeve 6 can be defined by fixing the axial position of the first blocking member 73 itself.

The first blocking member 73 may be a metal member, specifically made of a material with good wear resistance, such as chromium carbide, high manganese steel, tungsten carbide, or a plastic member with good wear resistance, and specifically made of a material such as fluoroplastic, nylon, or the like.

In addition, in other alternative embodiments, the first blocking member 73 is configured to protrude relatively in the radial direction on the outer circumferential surface of the angular stopper pin 72, and the first blocking member 73 may be fixed to the angular stopper pin 72 by means of insertion, adhesion, welding, or the like according to its own specific material, which is not particularly limited herein.

In one embodiment, referring to fig. 10 to 12, the compressor 100 includes an axial limiting member connected to the crankshaft 2 and the crank pin 3 and used for limiting the axial position of the crank pin 3 relative to the crankshaft 2. That is, because in the eccentric hole 20 on crank shaft 2 was inserted to crank pin 3 clearance fit, crank pin 3 can move in eccentric hole 20 along the axial of crank shaft 2, this embodiment is at first through setting up the spacing subassembly of axial and come to restrict the axial displacement of crank pin 3 in eccentric hole 20 to, guarantee crank pin 3's axial position. Several specific implementations of the axial stop assembly are provided below.

Specifically, referring to fig. 10, in the embodiment, the axial limiting component includes an axial limiting pin 74, a first slot 22 communicating with the eccentric hole 20 is formed on the outer circumferential surface of the crankshaft 2 at a position corresponding to the eccentric hole 20, a second slot 30 coaxial with and communicating with the first slot 22 is formed on the crank pin 3 corresponding to the first slot 22, and the axial limiting pin 74 is inserted into the first slot 22 along the radial direction of the crankshaft 2 and further extends to the second slot 30. Since the axial stopper pin 74 cannot be axially separated from the first slot 22 and the second slot 30, the axial stopper pin 74 can limit the axial position of the crank pin 3, and prevent the crank pin 3 from sliding in the axial direction of the crankshaft 2.

In an alternative embodiment, the second slot 30 may extend radially through the crank pin 3, i.e. the second slot 30 is a through hole. This is intended to allow the crank pin 3 to be completely restrained by the axial stopper pin 74, and the axial stopper pin 74 has a greater length into the interior of the crankshaft 2, so that the axial stopper pin 74 is more easily held in the radial direction of the crankshaft 2 without being displaced, and further, it is more advantageous to keep the axial position of the crank pin 3 fixed. Of course, not limited thereto, in other alternative embodiments, to simplify the arrangement of the second slot 30, the second slot 30 may not penetrate the crank pin 3, that is, the second slot 30 is a blind hole.

Further, as shown in fig. 10, the first insertion grooves 22 are formed at opposite sides of the inner wall surface of the eccentric hole 20, that is, the bottom of the first insertion groove 22 is formed on the crankshaft 2, and the first insertion groove 22 allows the axial stopper pin 74 to be further extended and inserted into the crankshaft 2 after penetrating the crank pin 3. The purpose of this arrangement is that the length of the axial limiting pin 74 inside the crankshaft 2 is further increased, and the axial limiting pin 74 is completely limited by the first slot 22 in the radial direction, so that the axial limiting pin 74 can always keep along the radial direction of the crankshaft 2 and the crank pin 3, and the possibility that the axial limiting pin 74 is deviated in the axial direction is further reduced, and the axial limitation of the crank pin 3 is always ensured.

Alternatively, as shown in fig. 10, the tip end surface of the axial stopper pin 74 (the end surface facing away from the bottom of the first slot 22) sinks into the first slot 22, that is, the tip end surface of the axial stopper pin 74 does not protrude out of the outer peripheral surface of the crankshaft 2. The purpose of this is that the tip end surface of the axial stopper pin 74 does not interfere with the inner race of the main bearing 95, and therefore, the fitting between the outer peripheral surface of the crankshaft 2 and the inner race of the main bearing 95 is not affected by the arrangement of the axial stopper pin 74.

The axial limit pin 74 and the crankshaft 2 may be in clearance fit, transition fit, interference fit, or the like, and the axial limit pin 74 and the crank pin 3 may also be in clearance fit, transition fit, interference fit, or the like. Optionally, clearance fits may be formed between the axial limit pin 74 and the crankshaft 2 and between the axial limit pin 74 and the crank pin 3, so as to simplify assembly between the axial limit pin 74 and the crankshaft 2 and assembly between the axial limit pin 74 and the crank pin 3, and reduce assembly cost of the compressor 100; in addition, the axial limit pin 74 and the crankshaft 2 are in clearance fit, so that deformation of the thin wall of the crankshaft 2 caused by interference fit can be avoided, and the roundness of the outer peripheral surface of the crankshaft 2 can be further favorably ensured, so that the rotation precision of the crankshaft 2 is ensured, further, vibration during rotation of the crankshaft 2 is avoided, and finally, noise caused by rotation of the crankshaft 2 is avoided.

In addition, an internal thread (not shown) may be formed at the bottom of the first insertion groove 22, and an external thread (not shown) may be formed at the bottom end of the axial stopper pin 74, and after the axial stopper pin 74 is inserted into the first insertion groove 22 and the second insertion groove 30, the bottom thereof is threadedly engaged with and fixedly connected to the crankshaft 2. In this way, the stability of the installation of the axial limiting pin 74 in the first slot 22 can be further improved, and the stability of the axial position and the radial position of the axial limiting pin 74 can be ensured.

Through the aforesaid setting, the axial position of crank pin 3 can be injectd, on this basis, can be fixed connection between eccentric cover 6 and the crank pin 3, if interference connection, the second end interference of crank pin 3 inserts in the eccentric cover 6. Therefore, the position of the eccentric sleeve 6 in the axial direction is also limited, the eccentric sleeve 6 does not directly impact the movable scroll 41 after being displaced along the axial direction of the crankshaft 2, the impact and the abrasion between the eccentric sleeve 6 and the movable scroll 41 are avoided, and the noise generated between the eccentric sleeve 6 and the movable scroll 41 due to the impact and the friction is further avoided. Of course, in other alternative embodiments, other fixed connection modes between the eccentric sleeve 6 and the crank pin 3 can be selected, and are not limited in particular.

Referring to fig. 11, in this embodiment, the axial limiting component includes an axial limiting block 75, the axial limiting block 75 is fixedly connected to one end of the crankshaft 2 facing the eccentric sleeve 6, an outer diameter of a first end of the crank pin 3 is greater than an outer diameter of a second end of the crank pin, an abutting hole 750 axially penetrating through two opposite end faces of the crank pin 3 is disposed on the axial limiting block 75, and an inner diameter of the abutting hole 750 is smaller than an outer diameter of the first end of the crank pin 3 and is greater than or equal to an outer diameter of the second end of the crank pin 3. As such, the second end of the crank pin 3 can pass through the abutment hole 750 of the axial stopper 75, while the first end of the crank pin 3 cannot pass through the abutment hole 750. Thus, by the cooperation of the axial stopper 75, the axial stopper 75 is engaged with the crank pin 3, so that the play of the crank pin 3 in the axial direction can be restricted, and the axial position of the crank pin 3 can be defined.

Wherein, alternatively, the outer diameter of the first end of the crank pin 3 may be uniform, as shown in fig. 11; alternatively, the outer diameter of the first end of the crank pin 3 may be non-uniform, and it is understood that the inner diameter of the abutting hole 750 being smaller than the outer diameter of the first end of the crank pin 3 means that the inner diameter of the abutting hole 750 is smaller than the maximum outer diameter of the first end of the crank pin 3; the outer diameter of the second end of the crank pin 3 may be uniform or non-uniform, and only needs to be able to pass through the abutting hole 750.

Specifically, in the present embodiment, the outer diameter of the first end of the crank pin 3 is uniform, and the outer diameter of the second end is also uniform, as shown in fig. 11, a second boss 31 is formed between the first end and the second end of the crank pin 3, and the axial stopper 75 abuts against the end surface of the second boss 31 facing the orbiting scroll 41.

Through the aforesaid setting, the axial position of crank pin 3 can be injectd, on this basis, can be fixed connection between eccentric cover 6 and the crank pin 3, like interference fit, the second end interference of crank pin 3 inserts in eccentric cover 6. Therefore, the position of the eccentric sleeve 6 in the axial direction is also limited, the eccentric sleeve 6 does not directly impact the movable scroll 41 after being displaced along the axial direction of the crankshaft 2, the impact and the abrasion between the eccentric sleeve 6 and the movable scroll 41 are avoided, and the noise generated between the eccentric sleeve 6 and the movable scroll 41 due to the impact and the friction is further avoided. Of course, in other alternative embodiments, other fixed connection modes between the eccentric sleeve 6 and the crank pin 3 can be selected, and are not limited in particular.

Wherein, optionally, referring to fig. 11, the axial limiting assembly further includes a fastener 76, and the fastener 76 is used for fastening and connecting the axial limiting block 75 with an end of the crankshaft 2 facing the eccentric sleeve 6.

In an alternative embodiment, the fastening member 76 may pass through the axial stopper 75 from an end of the axial stopper 75 facing the orbiting scroll 41, and be fixedly coupled with the crankshaft 2.

Specifically, the fastener 76 may be a bolt, a screw, or the like that is interference pressed into the crankshaft 2 or threadedly engaged with the crankshaft 2, respectively. As shown in fig. 11, in this embodiment, the axial limiting block 75 is provided with a first mounting hole 751 extending in the axial direction thereof, the first mounting hole 751 is a through hole, an end surface of the crankshaft 2 abutting against the axial limiting block 75 is provided with a second mounting hole 23 extending in the axial direction thereof, and the fastening member 76 is inserted into the first mounting hole 751 and the second mounting hole 23 in sequence from one end of the axial limiting block 75 facing away from the crankshaft 2 and is fixed in the first mounting hole 751 and the second mounting hole 23, so that the fastening member 76 is fixedly connected to the axial limiting block 75 and the crankshaft 2. Correspondingly, the first and second mounting holes 751 and 23 may be smooth-walled holes or threaded holes.

Also, it can be understood that the diameter of the fastening member 76 is small and the second mounting hole 23 can be opened close to the central axis of the crankshaft 2, and even if the fastening member 76 is connected to the crankshaft 2 by interference fit or threaded engagement, the roundness of the outer peripheral surface of the crankshaft 2 is not affected, and further, the fit between the crankshaft 2 and the inner retainer of the main bearing 95 is not affected.

Further, referring to fig. 11, in this embodiment, an end of the fastening member 76 facing the eccentric sleeve 6 is sunk into the first mounting hole 751, or an end surface of the fastening member 76 facing the end of the eccentric sleeve 6 is flush with an end surface of the axial stopper 75 facing the end of the eccentric sleeve 6. This is intended to avoid the fastener 76 protruding beyond the axial stopper 75 from affecting the positioning of the eccentric sleeve 6.

Referring to fig. 12, compared to the embodiment shown in fig. 11, the embodiment is modified in that the eccentric sleeve 6 and the second end of the crank pin 3 may be non-fixedly connected, such as non-interference fit, and may specifically be clearance fit, so that the assembly between the eccentric sleeve 6 and the crank pin 3 may be simplified. Specifically, in the present embodiment, the second end of the crank pin 3 passes through the eccentric sleeve 6 and is in clearance fit with the eccentric sleeve 6, and the end surface of the second end of the crank pin 3 protrudes from the end surface of the eccentric sleeve 6 facing the orbiting scroll 41, and on this basis, a second stopper 77 is added, and the second stopper 77 is disposed on a partial section of the crank pin 3 protruding from the eccentric sleeve 6 facing the orbiting scroll 41, and abuts against the end surface of the eccentric sleeve 6 facing the orbiting scroll 41, so that the second stopper 77 defines the axial position of the eccentric sleeve 6 on the crank pin 3.

The second blocking member 77 may be annular and annularly provided on the crank pin 3; the second stoppers 77 may be non-annular, but may be relatively protruded in a radial direction on the outer circumferential surface of the crank pin 3, in which case, the number of the second stoppers 77 may be one or more, and a plurality of the second stoppers 77 may be arranged along the circumferential direction of the crank pin 3.

Alternatively, the second blocking member 77 is annular and is annularly provided on the crank pin 3. An annular second groove 32 is formed in the outer peripheral surface of the crank pin 3 on the side protruding from the eccentric sleeve 6, and a second stopper 77 is provided in the second groove 32.

The second blocking member 77 may be a metal member, such as chromium carbide, high manganese steel, tungsten carbide, or a plastic member with good wear resistance, such as fluoroplastic, nylon, or the like.

Further, in other alternative embodiments, the second blocking member 77 may have a structure that relatively protrudes in a radial direction on the outer circumferential surface of the crank pin 3, and the second blocking member 77 may be fixed to a portion of the crank pin 3 protruding from the eccentric sleeve 6 toward the orbiting scroll 41 by means of insertion, adhesion, welding, or the like, according to a specific material thereof, which is not particularly limited herein.

The embodiment of the present application further provides an air conditioner (not shown), which includes the compressor 100 according to the above embodiments.

The air conditioner according to the embodiment of the present application includes the compressor 100 according to the above embodiment, and thus has advantages and effects corresponding to the compressor 100. Therefore, in the air conditioner, the roundness is good at each position of the outer peripheral surface of the crankshaft 2 corresponding to the position of the eccentric hole 20 in the compressor 100, and the inner retainer raceway of the main bearing 95 fitted to the crankshaft 2 is not deformed, so that the vibration during the operation of the air conditioner is low, and the noise during the operation of the air conditioner is low.

Specifically, the air conditioner may further include a condenser (not shown) and an evaporator (not shown), wherein an air outlet of the evaporator is communicated with the air suction port 910 on the low pressure housing 91, and the condenser is communicated with an air outlet 940 of the air-oil separator 94, and the specific operation process can be referred to the above description. In this way, a complete heat exchange circuit is formed between the compressor 100 and the condenser and the evaporator in the air conditioner to perform cooling and/or heating.

The embodiment of the present application further provides a vehicle (not shown) including the air conditioner according to the above embodiment.

Likewise, the vehicle provided by the embodiment of the present application has advantages and effects corresponding to those of the compressor 100 described above due to the inclusion of the air conditioner of the embodiment described above. Therefore, the air conditioner of the vehicle has advantages of low running vibration and low noise, and the vehicle also has advantages of low running vibration and low noise.

The specific structure of the vehicle is not limited, and may be any vehicle capable of being equipped with the air conditioner. For example, the vehicle generally includes a vehicle body (not shown), a vehicle head (not shown) provided at a position forward of the vehicle body, and the like, and the air conditioner may be provided at least partially in the vehicle head.

The specific type of the vehicle is not limited, for example, the vehicle may be a conventional fuel vehicle, and may also be a new energy vehicle, which includes, but is not limited to, a pure electric vehicle, an extended range electric vehicle, a hybrid electric vehicle, a fuel cell electric vehicle, a hydrogen engine vehicle, and the like, and this embodiment is not particularly limited thereto.

The above description is only exemplary of the present application and should not be taken as limiting the present application, as any modification, equivalent replacement, or improvement made within the spirit and principle of the present application should be included in the protection scope of the present application.

Claims (13)

1. A compressor, comprising:

the crankshaft is provided with an eccentric hole at one end;

one end of the crank pin is inserted into the eccentric hole, and the other end of the crank pin is exposed out of the eccentric hole;

the eccentric sleeve is sleeved on the other end of the crank pin; and

a scroll assembly connected to the eccentric sleeve;

the crank pin structure is characterized in that one end of the crank pin is in clearance fit with the eccentric hole, and the eccentric sleeve is fixedly connected with or in clearance fit with the other end of the crank pin.

2. The compressor as claimed in claim 1, further comprising a scroll bearing, the eccentric sleeve being fixedly coupled to the other end of the crank pin, the scroll bearing being coupled between an outer circumferential surface of the eccentric sleeve and the scroll assembly, the eccentric sleeve being provided with a first boss abutting against a side surface of the scroll bearing.

3. The compressor of claim 1, further comprising a scroll bearing and a wear plate, the eccentric sleeve being fixedly coupled to the other end of the crank pin, the scroll bearing being coupled between an outer circumferential surface of the eccentric sleeve and the scroll assembly, and the wear plate being disposed between a side of the scroll bearing facing the scroll assembly and the scroll assembly.

4. The compressor of claim 1, further comprising an angular position-limiting pin and a first blocking member, wherein the eccentric sleeve is fixedly connected to the other end of the crank pin, one end of the angular position-limiting pin penetrates through the eccentric sleeve and extends into the crank shaft to form a fixed connection, the other end of the angular position-limiting pin is exposed out of the eccentric sleeve, and the first blocking member is disposed on a partial section of the angular position-limiting pin exposed out of the eccentric sleeve and abuts against the eccentric sleeve.

5. The compressor of claim 1, further comprising an axial stop assembly coupled to the crankshaft and the crankpin for limiting an axial position of the crankpin.

6. The compressor of claim 5, wherein the axial limit assembly includes an axial limit pin inserted into the crankshaft and the crank pin in a radial direction of the crankshaft.

7. The compressor as claimed in claim 6, wherein a first slot communicating with the eccentric hole is provided on an outer circumferential surface of the crankshaft, and a second slot coaxial and communicating with the first slot is provided on the crank pin; the axial limiting pin is inserted into the first slot and the second slot.

8. The compressor of claim 7, wherein the second slot extends radially through the crank pin; the end face of the top end of the axial limiting pin is sunk into the first slot.

9. The compressor of claim 5, wherein the axial limiting assembly includes an axial limiting block fixedly connected to an end of the crankshaft facing the eccentric sleeve, an outer diameter of one end of the crank pin is greater than an outer diameter of the other end of the crank pin, the axial limiting block is provided with a butting hole penetrating in an axial direction thereof, and an inner diameter of the butting hole is smaller than the outer diameter of one end of the crank pin and is greater than or equal to the outer diameter of the other end of the crank pin.

10. The compressor of any one of claims 6 to 9, wherein the other end of the crank pin is fixedly connected with the eccentric sleeve.

11. The compressor of claim 5, wherein the axial stopper assembly includes an axial stopper fixedly coupled to an end of the crankshaft facing the eccentric sleeve, an outer diameter of an end of the crank pin is greater than an outer diameter of the other end of the crank pin, the axial stopper is provided with a contact hole axially penetrating therethrough, an inner diameter of the contact hole is smaller than the outer diameter of the end of the crank pin and is greater than or equal to the outer diameter of the other end of the crank pin, the other end of the crank pin passes through the axial stopper and the eccentric sleeve and protrudes from the eccentric sleeve, and the second stopper is disposed on the other end of the crank pin and contacts an end surface of the eccentric sleeve facing the scroll assembly, and the other end of the crank pin is in clearance fit with the eccentric sleeve.

12. An air conditioner characterized by comprising the compressor of any one of claims 1 to 11.

13. A vehicle comprising the compressor of claim 12.

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