A compressor, air conditioner and vehicle

Abstract

The application is suitable for the field of refrigeration and heating technology, and provides a compressor, an air conditioner and a vehicle. The compressor comprises a crankshaft, a crank pin, an eccentric sleeve and a scroll assembly. 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 from the eccentric hole. The eccentric sleeve is fixedly connected or in clearance fit with the other end of the crank pin. The scroll assembly is connected to the eccentric sleeve. Due to the clearance fit between the crank pin and the crankshaft, deformation of the thin part on the outer side of the eccentric hole of the crankshaft caused by interference fit of the crank pin on the crankshaft can be avoided, thereby avoiding deformation of the inner blocking ring raceway of the main bearing matched with the crankshaft, further avoiding the decrease of the rotation precision of the shaft system, finally reducing the vibration of the compressor in operation, further reducing the noise of the compressor in operation, and making the vibration and noise of the compressor in operation low.

Description

TECHNICAL FIELD

[0001] The present application relates to the technical field of refrigeration and heating, in particular to a compressor, an air conditioner and a vehicle. BACKGROUND

[0002] At present, with the development of new energy vehicles, consumers have further improved requirements for the noise, vibration and durability of air conditioner compressors.

[0003] Figure 1 And Figure 2 Fig. 1 shows a partial structure cross-sectional schematic diagram of a scroll compressor 100' currently applied to a vehicle. Generally, the structure design of the scroll compressor 100' is relatively compact. In order to improve the strength of the crankshaft assembly, the crankshaft assembly adopts a split structure design, that is, an eccentric hole 1' is formed on the crankshaft 2', a crank pin 3' (i.e. an eccentric pin) is inserted into the eccentric hole 1', and the crankshaft 2' and the crank pin 3' are connected as a whole through interference fit. Since the crankshaft 2' and the crank pin 3' are eccentrically arranged, the wall thickness between the outer circumferential 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 position where the crank pin 3' is interference fit and press-fitted with the crankshaft 2' is usually the position corresponding to the installation of the main bearing.

[0004] According to the above, since the eccentric arrangement of the eccentric hole 1' causes the partial wall thickness of the crankshaft 2' to be thin and the rigidity to be poor, after the crank pin 3' is interference press-fitted into the crankshaft 2', the roundness of the outer circumferential surface of the corresponding position of the crankshaft 2' is poor, that is, the roundness of the outer circumferential surface of the position on the crankshaft 2' corresponding to the installation of the main bearing is poor.

[0005] As shown in Fig. 2, the crank pin 3' is interference press-fitted in the crankshaft 2' and eccentrically matched with the crankshaft 2'. Taking any cross section in the interference area segment Q, the roundness of the outer circumferential surface of the crankshaft 2' is detected, and the result shown in Fig. 3 is obtained. Figure 2 Figure 3 In Fig. 3, the roundness of the outer circumferential surface of the crankshaft 2' has reached 14.9 μm, and generally the gap between the main bearing and the crankshaft 2' after the main bearing is assembled on the crankshaft 2' is within 10 μm. The roundness value is obviously beyond the gap value between the main bearing and the crankshaft 2', and therefore, this will directly affect the roundness of the inner retainer ring of the main bearing, causing the roundness of the raceway of the main bearing to be poor, so that the deformation of the inner retainer ring of the main bearing is caused, resulting in problems such as raceway wear and peeling, and further causing the abnormal vibration of the shaft system of the scroll compressor 100', and further causing the abnormal noise of the scroll compressor 100', and even failure. Figure 3 SUMMARY

[0006] ​​The embodiment of the present application aims to provide a compressor, aiming to solve the technical problem that the poor roundness of the outer circumferential surface of the crankshaft caused by the interference fit between the crankshaft and the crankpin leads to the deformation of the inner blocking ring of the main bearing, thus causing the abnormal vibration of the shafting of the compressor, and further causing the abnormal noise of the compressor.

[0007] The embodiment of the present application is implemented as follows: a compressor comprises:

[0008] a crankshaft, one end of the crankshaft being provided with an eccentric hole;

[0009] a crankpin, one end of the crankpin being inserted into the eccentric hole, and the other end of the crankpin being exposed from the eccentric hole;

[0010] an eccentric sleeve, the eccentric sleeve being sleeved on the other end of the crankpin; and

[0011] a scroll assembly, the scroll assembly being connected to the eccentric sleeve.

[0012] One end of the crankpin is in clearance fit with the eccentric hole, and the eccentric sleeve is fixedly connected to or in clearance fit with the other end of the crankpin.

[0013] In one embodiment, the compressor further comprises a scroll bearing, the eccentric sleeve is fixedly connected to the other end of the crankpin, the scroll bearing is connected between the outer circumferential surface of the eccentric sleeve and the scroll assembly, the eccentric sleeve is provided with a first boss, and the first boss is in abutment with the side surface of the scroll bearing.

[0014] In one embodiment, the compressor further comprises a scroll bearing and a wear-resistant sheet, the eccentric sleeve is fixedly connected to the other end of the crankpin, the scroll bearing is connected between the outer circumferential surface of the eccentric sleeve and the scroll assembly, and the wear-resistant sheet is arranged between the side surface of the scroll bearing facing the scroll assembly and the scroll assembly.

[0015] In one embodiment, the compressor further comprises an angular limiting pin and a first blocking piece, the eccentric sleeve is fixedly connected to the other end of the crankpin, one end of the angular limiting pin penetrates through the eccentric sleeve and is fixedly connected into the crankshaft, the other end of the angular limiting pin is exposed from the eccentric sleeve, and the first blocking piece is arranged on the part of the angular limiting pin exposed from the eccentric sleeve and is in abutment with the eccentric sleeve.

[0016] In one embodiment, the compressor further comprises an axial limiting assembly, the axial limiting assembly is connected to the crankshaft and the crankpin, and is used for limiting the axial position of the crankpin.

[0017] In one embodiment, the axial limiting assembly comprises an axial limiting pin, the axial limiting pin is inserted into the crankshaft and the crankpin along the radial direction of the crankshaft.

[0018] In one embodiment, the outer circumferential surface of the crankshaft is provided with a first slot in communication with the eccentric hole, and the crank pin is provided with a second slot coaxial with and in communication with the first slot; the axial limiting pin is inserted into the first slot and the second slot.

[0019] In one embodiment, the second slot extends through the crank pin in the radial direction; and the top end surface of the axial limiting pin is sunken into the first slot.

[0020] In one embodiment, the axial limiting assembly includes an axial limiting block fixedly connected to one end of the crankshaft facing the eccentric sleeve, the outer diameter of one end of the crank pin is greater than the outer diameter of the other end of the crank pin, and the axial limiting block is provided with an abutting hole extending therethrough in the axial direction, the inner diameter of the abutting hole is less than the outer diameter of one end of the crank pin and greater than or equal to the outer diameter of the other end of the crank pin.

[0021] In one embodiment, the other end of the crank pin is fixedly connected to the eccentric sleeve.

[0022] In one embodiment, the axial limiting assembly includes an axial limiting block and a second blocking piece, the axial limiting block is fixedly connected to one end of the crankshaft facing the eccentric sleeve, the outer diameter of one end of the crank pin is greater than the outer diameter of the other end of the crank pin, the axial limiting block is provided with an abutting hole extending therethrough in the axial direction, the inner diameter of the abutting hole is less than the outer diameter of one end of the crank pin and 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 limiting block and the eccentric sleeve and protrudes from the eccentric sleeve, the second blocking piece is arranged on the other end of the crank pin and abuts against the 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.

[0023] Another purpose of the embodiments of the present application is to provide an air conditioner comprising the compressor as described in the above embodiments.

[0024] Still another purpose of the embodiments of the present application is to provide a vehicle comprising the air conditioner as described in the above embodiments.

[0025] The compressor, the air conditioner and the vehicle provided by the embodiments of the present application have the following beneficial effects compared with the prior art:

[0026] The compressor provided in this application embodiment, by setting a crank pin inserted into the eccentric hole of the crankshaft and having a clearance fit with the crankshaft, can avoid deformation of the thinner part on the outer side of the corresponding eccentric hole on the crankshaft due to the interference fit of the crank pin on the crankshaft. This avoids the decrease in crankshaft rotation accuracy, and further avoids the problem of deformation of the inner retaining ring raceway of the main bearing that mates with the crankshaft. Ultimately, it reduces the vibration of the crankshaft rotation and further reduces the noise of the crankshaft rotation, resulting in low vibration and low noise during the operation of the compressor. In addition, the air conditioner and vehicle provided in this application embodiment, by implementing the above-mentioned design of the compressor, result in low vibration and low noise during the crankshaft rotation of the compressor, thereby resulting in low vibration and low noise during the operation of the air conditioner, and consequently, low vibration and low noise during the operation of the vehicle. Attached Figure Description

[0027] To more clearly illustrate the technical solutions in the embodiments of this application, the drawings used in the embodiments will be briefly introduced below. Obviously, the drawings described below are only some embodiments of this application. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0028] Figure 1 This is a partial longitudinal section structural diagram of a compressor in the prior art;

[0029] Figure 2 This is a schematic diagram of the interference fit between the crankshaft and crank pin in a compressor of existing technology;

[0030] Figure 3 It refers to the out-of-roundness of the outer circumference of the crankshaft;

[0031] Figure 4 This is a schematic longitudinal section of the compressor provided in Embodiment 1 of this application;

[0032] Figure 5 yes Figure 4 Enlarged view of point A in the middle;

[0033] Figure 6 yes Figure 4 Enlarged view of point B in the middle;

[0034] Figure 7 This is a partial longitudinal sectional view of the compressor provided in Embodiment 2 of this application;

[0035] Figure 8 yes Figure 7 Enlarged view of point C in the middle;

[0036] Figure 9 This is a partial longitudinal sectional view of the compressor provided in Embodiment 3 of this application;

[0037] Figure 10is a schematic view of a longitudinal section of a part structure of a compressor provided in Embodiment Four of the present application;

[0038] Figure 11 is a schematic view of a longitudinal section of a part structure of a compressor provided in Embodiment Five of the present application;

[0039] Figure 12 is a schematic view of a longitudinal section of a part structure of a compressor provided in Embodiment Six of the present application.

[0040] The meanings of the marks in the figures are as follows:

[0041] 100'- scroll compressor, 1'- eccentric hole, 2'- crankshaft, 3'- crank pin;

[0042] 100 compressor;

[0043] 1- motor assembly, 11- stator, 12- rotor;

[0044] 2- crankshaft, 20- eccentric hole, 21- adjusting pin hole, 22- first insertion slot, 23- second mounting hole;

[0045] 3- crank pin, 30- second insertion slot, 31- second boss, 32- second groove;

[0046] 4- scroll assembly, 40- compression chamber, 41- orbiting scroll, 410- scroll bearing mounting hole, 42- fixed scroll;

[0047] 5- scroll bearing;

[0048] 6- eccentric sleeve, 61- first boss;

[0049] 71- wear plate;

[0050] 72- angular limit pin, 720- first groove, 73- first blocking piece, 74- axial limit pin, 75- axial limit block, 750- abutting hole, 751- first mounting hole, 76- fastener, 77- second blocking piece;

[0051] 91- low-pressure housing, 910- suction port, 92- bracket, 93- throttling element, 94- oil-gas separator, 940- exhaust port, 941- oil chamber, 95- main bearing, 96- auxiliary bearing. DETAILED DESCRIPTION

[0052] In order to make the objectives, technical solutions and advantages of the present application clearer, further detailed description will be made to the present application in combination with the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are only used to explain the present application, and are not used to limit the present application.

[0053] It is to be noted that when a component is referred to as being "fixed" or "set" on another component, it can be directly or indirectly fixed or set on the other component. When a component is referred to as being "connected" to another component, it can be directly or indirectly connected to the other component. The terms "upper", "lower", "left", "right", and the like indicate the orientation or positional relationship based on the orientation or positional relationship shown in the drawings, and are only for the convenience of description, and do not indicate or imply that the device or element referred to must have a particular orientation, be constructed and operated in a particular orientation, and therefore cannot be understood as a limitation on the patent. The terms "first", "second" are only for the convenience of description, and cannot be understood as indicating or implying relative importance or implicitly indicating the number of technical features. The meaning of "a plurality of" is two or more, unless otherwise specifically limited.

[0054] In order to illustrate the technical solutions described in the present application, the following will be described in detail in combination with specific drawings and examples.

[0055] Please refer to Figure 4 and Figure 5 , the present embodiment first provides a compressor 100, which comprises a motor assembly 1, a crankshaft 2, a crank pin 3, an eccentric sleeve 6 and a scroll assembly 4. Among them, the motor assembly 1 comprises a stator 11 and a rotor 12 arranged inside the stator 11, the crankshaft 2 is connected to the rotor 12 of the motor assembly 1, specifically, the crankshaft 2 passes through the rotor 12 and is in interference fit (or connected in the form of key and key groove) with the rotor 12, so that the crankshaft 2 can rotate around its own center axis under the driving of the rotor 12; one end of the crankshaft 2 is provided with an eccentric hole 20 extending along its axial direction, one end of the crank pin 3 (defined as the first end of the crank pin 3 here for the convenience of description in the following) is inserted into the eccentric hole 20 and is in clearance fit with the crankshaft 2, the other end of the crank pin 3 (also defined as the second end of the crank pin 3 here for the convenience of description in the following, which is connected with the first end in the axial direction) 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 assembly 4 is connected to the eccentric sleeve 6. As shown in Figure 4 , the compressor 100 further comprises a main bearing 95 and a bracket 92, the inner retainer ring of the main bearing 95 is in interference fit with the corresponding crank pin 3 and the outer peripheral surface of the eccentric hole 20 of the crankshaft 2, and the outer retainer ring of the main bearing 95 is in interference fit with the bracket 92, so that the crankshaft 2 is supported on the bracket 92 through the main bearing 95 and is in rotational fit with the bracket 92.

[0056] The compressor 100 provided by the embodiment of the present application can avoid deformation of the corresponding thin thickness outside the eccentric hole 20 of the crankshaft 2 caused by interference assembly of the crank pin 3 to the crankshaft 2, thereby avoiding deformation of the inner blocking ring raceway of the main bearing 95 matched with the crankshaft 2, further avoiding the decrease of the rotation precision of the shaft system, finally, reducing the vibration of the operation of the compressor 100, further reducing the noise of the operation of the compressor 100, so that the vibration and noise of the operation of the compressor 100 are low.

[0057] In the embodiment of the present application, referring to Figure 4 , the scroll assembly 4 is connected to the eccentric sleeve 6, and the scroll assembly 4 comprises a moving scroll 41 connected to the eccentric sleeve 6 and a stationary scroll 42 connected to the bracket 92. Under the driving of the motor assembly 1, the crankshaft 2, the crank pin 3 and the eccentric sleeve 6, the moving scroll 41 revolves around the stationary scroll 42 and is engaged with the stationary scroll 42 to form a compression chamber 40 with a continuously changing volume.

[0058] Referring to Figure 4 , the compressor 100 provided by the embodiment of the present application further comprises a low-pressure shell 91 and an oil-gas separator 94, and the motor assembly 1 and the crankshaft 2 are arranged in the low-pressure shell 91, and the low-pressure shell 91 is formed with a suction port 910 for communicating with an outlet of an evaporator (not shown) through a pipeline (not shown). The bracket 92 is connected to the low-pressure shell 91, and the end of the crankshaft 2 away from the eccentric hole 20 is installed on the low-pressure shell 91 through a secondary bearing 96. Specifically, the inner blocking ring of the secondary bearing 96 is interference-fitted with the outer periphery of the crankshaft 2, and the outer blocking ring of the secondary bearing 96 is interference-pressed into the low-pressure shell 91. The stationary scroll 42 is provided with an outlet (not shown), and the inlet of the oil-gas separator 94 is connected to the outlet of the stationary scroll 42, the outlet 940 of the oil-gas separator 94 is communicated with the inlet of a condenser (not shown) through a pipeline (not shown), and the oil chamber 941 of the oil-gas separator 94 is communicated to the inside of the low-pressure shell 91 through the throttling element 93.

[0059] The working process of the compressor 100 is as follows: under the driving of the crankshaft 2, the crank pin 3 and the eccentric sleeve 6, the orbiting scroll 41 makes an orbiting translation, the teeth of the orbiting scroll 41 and the teeth of the fixed scroll 42 are in meshing with each other, forming the compression chamber 40 with a variable volume. The mixed fluid containing the refrigerant and the refrigeration oil is sucked into the interior of the low-pressure shell 91 (low-pressure area) through the suction port 910, and is further sucked into the compression chamber 40 for compression, and is discharged to the oil-gas separator 94 through the gas outlet of the fixed scroll 42 for oil-gas separation. The separated refrigerant is discharged from the oil-gas separator 94 (high-pressure area) through the discharge port 940, and is circulated between the compressor 100, the condenser and the evaporator for heat exchange. The separated refrigeration oil enters the oil chamber 941, and returns to the low-pressure shell 91 through the throttling element 93 for circulation and lubrication.

[0060] Please continue to refer to Figure 4 and Figure 6 In one embodiment, the compressor 100 further comprises a scroll bearing 5, the side of the orbiting scroll 41 facing the eccentric sleeve 6 is formed with a scroll bearing mounting hole 410, and the scroll bearing 5 is mounted in the scroll bearing mounting hole 410. Specifically, the inner retainer of the scroll bearing 5 is in interference fit with the outer circumferential surface of the eccentric sleeve 6, and the outer retainer of the scroll bearing 5 is in interference fit with the inner side wall of the scroll bearing mounting hole 410. In this way, the scroll bearing 5 is fixedly connected with the eccentric sleeve 6 and the orbiting scroll 41 respectively, and the crank pin 3 drives the orbiting scroll 41 to rotate through the eccentric sleeve 6 and the scroll bearing 5.

[0061] In this embodiment, the crank pin 3 is in clearance fit with the crankshaft 2, and in the radial direction of the crankshaft 2, the crank pin 3 can still drive the eccentric sleeve 6 to make a translation, and the eccentric sleeve 6 further drives the orbiting scroll 41 to make a translation. However, in the axial direction of the crankshaft 2, the crank pin 3 is prone to displacement, which may cause the eccentric sleeve 6 to make an axial displacement, and further, the eccentric sleeve 6 directly impacts on the orbiting scroll 41 after making an axial displacement, which is easy to cause wear or even damage between the eccentric sleeve 6 and the orbiting scroll 41, and corresponding noise and the like.

[0062] To this end, in one embodiment, as Figure 4 and Figure 6The outer circumferential surface of the end of the eccentric sleeve 6 away from the orbiting scroll 41 has a larger outer diameter than the outer circumferential surface of the other end of the eccentric sleeve 6, thereby forming a first boss 61. The inner retainer of the orbiting bearing 5 is in contact with the outer circumferential surface of the end of the eccentric sleeve 6 having a smaller outer diameter. Thus, the eccentric sleeve 6 is limited in the axial direction by the abutment of the first boss 61 of the eccentric sleeve 6 and the orbiting bearing 5, and the amount of displacement S of the eccentric sleeve 6 in the axial direction can be significantly reduced or even be zero. The eccentric sleeve 6 can be prevented from moving along the axial direction of the crankshaft 2 to hit the bottom surface of the orbiting scroll 41, and the collision and abrasion between the eccentric sleeve 6 and the orbiting scroll 41 can be avoided. Further, the noise generated by the collision and abrasion between the eccentric sleeve 6 and the orbiting scroll 41 can be avoided.

[0063] In this embodiment, the eccentric sleeve 6 and the crank pin 3 can be in clearance fit or fixed connection, such as interference fit. In an alternative embodiment, the eccentric sleeve 6 and the crank pin 3 are fixedly connected. The purpose of this arrangement is that the eccentric sleeve 6 and the crank pin 3 are fixedly connected as a whole, and the collision between the eccentric sleeve 6 and the crank pin 3 in the radial direction and the possible relative displacement in the axial direction can be reduced. The crank pin 3 and the eccentric sleeve 6 are driven to rotate eccentrically by the crankshaft 2 as a whole, and the driving of the orbiting scroll 41 by the crank pin 3 is more stable. Thus, the vibration of the orbiting scroll 41 during rotation can be reduced, and the noise generated by the rotation of the orbiting scroll 41 can be reduced. The sealing reliability of the meshing between the orbiting scroll 41 and the fixed scroll 42 can be ensured.

[0064] Please refer to Figure 7 and Figure 8 Another solution to the problem of collision between the eccentric sleeve 6 and the orbiting scroll 41 is provided in this embodiment. In this embodiment, the compressor 100 further comprises a wear-resistant sheet 71 arranged between the bottom surface of the orbiting bearing mounting hole 410 and the end surface of the eccentric sleeve 6 facing the orbiting scroll 41. That is, the wear-resistant sheet 71 occupies the axial gap between the bottom surface of the orbiting bearing mounting hole 410 and the end surface of the eccentric sleeve 6 facing the orbiting scroll 41. Thus, the amount of displacement S of the eccentric sleeve 6 in the axial direction can be significantly reduced or even be zero. Similarly, the eccentric sleeve 6 can be prevented from moving along the axial direction of the crankshaft 2 to hit the bottom surface of the orbiting scroll 41, and the collision and abrasion between the eccentric sleeve 6 and the orbiting scroll 41 can be avoided. Further, the noise generated by the collision and abrasion between the eccentric sleeve 6 and the orbiting scroll 41 can be avoided.

[0065] The wear-resistant sheet 71 can be made of a material with good wear resistance, such as a metal material, specifically, chromium carbide, high manganese steel, tungsten carbide, or a plastic material with good wear resistance, specifically, fluoroplastic, nylon, etc. Alternatively, the wear-resistant sheet 71 is a metal sheet.

[0066] The thickness of the wear-resistant sheet 71 is set according to the specific size of the interior of the compressor 100, and preferably is as small as possible, without being particularly limited.

[0067] In this embodiment, the eccentric sleeve 6 and the crank pin 3 can be in clearance fit, or can be fixedly connected, such as interference fit. In an alternative embodiment, the eccentric sleeve 6 and the crank pin 3 are fixedly connected, such as interference fit. In this way, the eccentric sleeve 6 and the crank pin 3 are fixedly connected as a whole, which can reduce the radial collision and the axial relative displacement between the eccentric sleeve 6 and the crank pin 3, and the crank pin 3 and the eccentric sleeve 6 are driven to rotate eccentrically by the crankshaft 2 as a whole, so that the driving of the crank pin 3 on the orbiting scroll 41 is more stable, and the vibration of the orbiting scroll 41 during rotation is reduced, further, the noise of the orbiting scroll 41 during rotation is reduced, and the sealing reliability of the meshing between the orbiting scroll 41 and the fixed scroll 42 is ensured.

[0068] Please refer to Figure 9 This is another solution to the problem of collision between the eccentric sleeve 6 and the orbiting scroll 41 proposed by the embodiment of the present application. In this embodiment, the compressor 100 further comprises an angular limiting pin 72 and a first blocking piece 73. The angular limiting pin 72 is used to adjust the eccentric amount of the eccentric sleeve 6 relative to the crankshaft 2, so that the orbiting scroll 41 and the fixed scroll 42 can be meshed. Specifically, the end of the crankshaft 2 facing the orbiting scroll 41 is further provided with an adjusting pin hole 21 extending along the axial direction thereof, the adjusting pin hole 21 is parallel to and spaced apart from the eccentric hole 20, one end of the angular limiting pin 72 is inserted into the adjusting pin hole 21 and fixedly connected with the crankshaft 2, the other end of the angular limiting pin 72 penetrates the eccentric sleeve 6 and protrudes from the end face of the eccentric sleeve 6 facing the scroll assembly 4, and the first blocking piece 73 is arranged on the part of the angular limiting pin 72 exposed from the eccentric sleeve 6 and abuts against the end face of the eccentric sleeve 6 facing the orbiting scroll 41. Thus, the first blocking piece 73 limits the eccentric sleeve 6 on the angular limiting pin 72, which can prevent the eccentric sleeve 6 from moving axially along the angular limiting pin 72, thereby preventing the eccentric sleeve 6 from directly colliding with the orbiting scroll 41.

[0069] At this time, the second end of the eccentric sleeve 6 and the crank pin 3 can be in clearance fit, or can be fixedly connected, such as interference fit. In an alternative embodiment, the second end of the eccentric sleeve 6 and the crank pin 3 are fixedly connected, so that the crank pin 3 and the eccentric sleeve 6 are connected as a whole. On the basis of the axial limitation of the eccentric sleeve 6 by the first blocking piece 73, the axial position of the crank pin 3 is also limited, so that the axial displacement of the crank pin 3 and the radial collision between the crank pin 3 and the eccentric sleeve 6 can be reduced, and 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 more stable, and finally the operation of the compressor 100 is more stable.

[0070] The one end of the angular limiting 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 limiting pin 72 and the crankshaft 2 is achieved, and the axial position of the angular limiting pin 72 is limited. Of course, it is not limited to this, and in other alternative embodiments, the fixed connection between the angular limiting pin 72 and the crankshaft 2 can be achieved in other ways.

[0071] It should be noted that in the above embodiment, although the angular limiting pin 72 is also inserted into the crankshaft 2 in interference fit, since the diameter of the angular limiting pin 72 is usually small, and the position of the adjusting pin hole 21 is closer to the central axis of the crankshaft 2, there will not be a relatively thin area between the adjusting pin hole 21 and the outer circumferential surface of the crankshaft 2, and the interference fit between the angular limiting pin 72 and the crankshaft 2 will not significantly affect the roundness of the outer circumferential surface of the crankshaft 2, thereby avoiding causing the deformation of the inner raceway of the main bearing 95, and further avoiding causing the problem of the decrease in the rotation accuracy of the shafting of the compressor 100, and further avoiding causing the vibration and noise of the operation of the compressor 100.

[0072] The connection between the angular limiting pin 72 and the eccentric sleeve 6 is not limited to interference fit, clearance fit or transition fit, etc. Alternatively, the angular limiting pin 72 and the eccentric sleeve 6 are in clearance fit, so that the angular limiting pin 72 can pass through the eccentric sleeve 6, thereby simplifying the assembly steps between the angular limiting pin 72 and the eccentric sleeve 6, and reducing the assembly cost of the compressor 100. In the specific assembly process, after the angular limiting pin 72 passes through the eccentric sleeve 6, the first blocking piece 73 is installed on the end of the angular limiting pin 72 protruding from the eccentric sleeve 6.

[0073] The first blocking piece 73 can be annular and annularly arranged on the angular limiting pin 72, or the first blocking piece 73 can be non-annular and relatively protruding in the radial direction on the outer circumferential surface of the angular limiting pin 72. At this time, the number of the first blocking piece 73 can be one or more, and the plurality of first blocking pieces 73 can be arranged along the circumferential direction of the angular limiting pin 72.

[0074] In an alternative embodiment, please refer to Figure 9 The first blocking piece 73 is annular and annularly arranged on the angular limiting pin 72. For this, the other end of the angular limiting pin 72 (i.e. the end protruding from the eccentric sleeve 6) forms a first annular groove 720, and the first blocking piece 73 is arranged in the first annular groove 720, so that the axial position of the first blocking piece 73 on the angular limiting pin 72 can be fixed in a simple way, and further, the axial position of the eccentric sleeve 6 can be limited by the fixed axial position of the first blocking piece 73.

[0075] The first blocking piece 73 can be a metal piece, and the specific material can be a material with good wear resistance, such as chromium carbide, high manganese steel, tungsten carbide, or the like. Alternatively, the first blocking piece 73 can be a plastic piece with good wear resistance, and the specific material can be fluoroplastic, nylon, or the like.

[0076] In addition, in other optional embodiments, the first blocking piece 73 is arranged to protrude radially on the outer circumferential surface of the angular limiting pin 72. At this time, the first blocking piece 73 can be fixed on the angular limiting pin 72 by insertion, adhesion, welding, or the like, according to the specific material of the first blocking piece 73, and no specific limitation is made herein.

[0077] In an embodiment, referring to Figure 10 to Figure 12 The compressor 100 includes an axial limiting assembly connected to the crankshaft 2 and the crank pin 3, and configured to limit the axial position of the crank pin 3 relative to the crankshaft 2. That is, since the crank pin 3 is inserted into the eccentric hole 20 on the crankshaft 2 in a clearance fit, the crank pin 3 can move in the axial direction of the crankshaft 2 in the eccentric hole 20. In this embodiment, the axial movement of the crank pin 3 in the eccentric hole 20 is first limited by providing the axial limiting assembly, so as to ensure the axial position of the crank pin 3. In the following, several specific implementation modes of the axial limiting assembly are provided.

[0078] Specifically, referring to Figure 10 In this embodiment, the axial limiting assembly includes an axial limiting pin 74, a first insertion slot 22 is formed on the outer circumferential surface of the crankshaft 2 at a position corresponding to the eccentric hole 20, the first insertion slot 22 is connected to the eccentric hole 20, and a second insertion slot 30 coaxial with the first insertion slot 22 and connected thereto is arranged on the crank pin 3 corresponding to the first insertion slot 22. The axial limiting pin 74 is inserted into the first insertion slot 22 in the radial direction of the crankshaft 2 and further extends into the second insertion slot 30. Since the axial limiting pin 74 cannot be separated from the first insertion slot 22 and the second insertion slot 30 in the axial direction, the axial limiting pin 74 can limit the axial position of the crank pin 3 to avoid the axial sliding of the crank pin 3 along the crankshaft 2.

[0079] In an optional embodiment, the second insertion slot 30 can penetrate the crank pin 3 in the radial direction, that is, the second insertion slot 30 is a through hole. The purpose of this arrangement is that the crank pin 3 can be completely limited by the axial limiting pin 74, the length of the axial limiting pin 74 entering the inside of the crankshaft 2 is greater, so that the axial limiting pin 74 is more likely to remain in the radial direction of the crankshaft 2 without deviation, thereby being more conducive to fixing the axial position of the crank pin 3. Of course, it is not limited to this, and in other optional embodiments, in order to simplify the arrangement of the second insertion slot 30, the second insertion slot 30 can not penetrate the crank pin 3, that is, the second insertion slot 30 is a blind hole.

[0080] Further, as Figure 10As shown, the first slot 22 is formed on the opposite sides of the inner wall surface of the eccentric hole 20, that is, the bottom of the first slot 22 is formed on the crankshaft 2, and the first slot 22 allows the axial limiting pin 74 to further extend into the crankshaft 2 after penetrating the crankpin 3. The purpose of such arrangement is to further increase the length of the axial limiting pin 74 inside the crankshaft 2, and the axial limiting pin 74 is completely limited in the radial direction by the first slot 22, so that the axial limiting pin 74 can always keep along the radial direction of the crankshaft 2 and the crankpin 3, and the possibility of the axial limiting pin 74 being offset in the axial direction is further reduced, thereby ensuring that the crankpin 3 is always axially limited.

[0081] Optionally, as shown, the top end surface of the axial limiting pin 74 (the end surface away from the bottom of the first slot 22) is sunken into the first slot 22, that is, the top end surface of the axial limiting pin 74 does not protrude from the outer peripheral surface of the crankshaft 2. The purpose of such arrangement is that the top end surface of the axial limiting pin 74 does not interfere with the inner retainer of the main bearing 95, so that the arrangement of the axial limiting pin 74 does not affect the cooperation between the outer peripheral surface of the crankshaft 2 and the inner retainer of the main bearing 95. Figure 10

[0082] The axial limiting pin 74 and the crankshaft 2 can be clearance fit, transition fit or interference fit, and the axial limiting pin 74 and the crankpin 3 can also be clearance fit, transition fit or interference fit. Optionally, the axial limiting pin 74 and the crankshaft 2 can be clearance fit, and the axial limiting pin 74 and the crankpin 3 can also be clearance fit, so as to simplify the assembly of the axial limiting pin 74 and the crankshaft 2, and the assembly of the axial limiting pin 74 and the crankpin 3, and reduce the assembly cost of the compressor 100. In addition, the clearance fit between the axial limiting pin 74 and the crankshaft 2 can also avoid the deformation of the thin wall of the crankshaft 2 caused by interference fit, which is further conducive to ensuring the roundness of the outer peripheral surface of the crankshaft 2, thereby ensuring the rotation accuracy of the crankshaft 2, and further avoiding the vibration of the crankshaft 2 during rotation, and finally avoiding the noise caused by the rotation of the crankshaft 2.

[0083] In addition, the bottom of the first slot 22 can also be formed with internal threads (not shown), and the bottom end of the axial limiting pin 74 is formed with external threads (not shown), and after the axial limiting pin 74 is inserted into the first slot 22 and the second slot 30, the bottom of the axial limiting pin 74 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.

[0084] ​By the above arrangement, the axial position of the crank pin 3 is defined, on the basis of which the eccentric sleeve 6 and the crank pin 3 can be fixedly connected, such as interference fit, the second end of the crank pin 3 is interference inserted into the eccentric sleeve 6. In this way, the axial position of the eccentric sleeve 6 is also defined, the eccentric sleeve 6 cannot directly impact the dynamic scroll 41 after displacement along the axial direction of the crankshaft 2, avoiding the impact and wear between the eccentric sleeve 6 and the dynamic scroll 41, further avoiding the noise generated by the impact and friction between the eccentric sleeve 6 and the dynamic scroll 41. Of course, in other alternative embodiments, other fixed connection modes can be selected between the eccentric sleeve 6 and the crank pin 3, which are not particularly limited here.

[0085] Please refer to Figure 11 In this embodiment, the axial limiting assembly includes an axial limiting block 75, which is fixedly connected to one end of the crankshaft 2 facing the eccentric sleeve 6, the outer diameter of the first end of the crank pin 3 is greater than that of the second end, and the axial limiting block 75 is provided with an abutting hole 750 penetrating through the opposite end faces in the axial direction, the inner diameter of the abutting hole 750 is less than the outer diameter of the first end of the crank pin 3 and greater than or equal to the outer diameter of the second end of the crank pin 3. In this way, the second end of the crank pin 3 can pass through the abutting hole 750 of the axial limiting block 75, while the first end of the crank pin 3 cannot pass through the abutting hole 750. In this way, by cooperating with the axial limiting block 75, the axial limiting block 75 is clamped with the crank pin 3, so that the axial movement of the crank pin 3 can be limited, and the axial position of the crank pin 3 is defined.

[0086] Optionally, the outer diameter of the first end of the crank pin 3 can be uniform, as shown in Figure 11 ; or the outer diameter of the first end of the crank pin 3 can also be non-uniform, it can be understood that at this time, the inner diameter of the abutting hole 750 less than the outer diameter of the first end of the crank pin 3 means that the inner diameter of the abutting hole 750 is less 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 can be uniform or non-uniform, as long as it can pass through the abutting hole 750.

[0087] Specifically in this 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 Figure 11 , the second end and the second end of the crank pin 3 form a second boss 31, and the axial limiting block 75 abuts against the end face of the second boss 31 facing the dynamic scroll 41.

[0088] By the above arrangement, the axial position of the crank pin 3 is defined, and on this basis, the eccentric sleeve 6 and the crank pin 3 can be fixedly connected, such as interference fit, the second end of the crank pin 3 is inserted into the eccentric sleeve 6 in interference fit. In this way, the position of the eccentric sleeve 6 in the axial direction is also defined, and the eccentric sleeve 6 cannot directly impact the moving scroll 41 after displacement along the axial direction of the crankshaft 2, avoiding the impact and wear between the eccentric sleeve 6 and the moving scroll 41, and further avoiding the noise generated by the impact and friction between the eccentric sleeve 6 and the moving scroll 41. Of course, in other alternative embodiments, other fixed connection modes can be selected between the eccentric sleeve 6 and the crank pin 3, which are not particularly limited here.

[0089] Optionally, referring to Figure 11 , the axial limiting assembly further comprises a fastener 76, and the fastener 76 is used to fasten and connect the axial limiting block 75 and the end of the crankshaft 2 facing the eccentric sleeve 6.

[0090] In an alternative embodiment, the fastener 76 can pass through the axial limiting block 75 from the end of the axial limiting block 75 facing the moving scroll 41, and is fixedly connected with the crankshaft 2.

[0091] Specifically, the fastener 76 can be a bolt, a screw or the like structure, which is respectively pressed into interference with the crankshaft 2 or threadedly engaged with the crankshaft 2. As Figure 11 shown, in this embodiment, the axial limiting block 75 is provided with a first mounting hole 751 extending along the axial direction thereof, the first mounting hole 751 is a through hole, the end face of the crankshaft 2 abutting against the axial limiting block 75 is provided with a second mounting hole 23 extending along the axial direction thereof, and the fastener 76 is inserted into the first mounting hole 751 and the second mounting hole 23 from the end of the axial limiting block 75 away from the crankshaft 2 in sequence, and is fixed in the first mounting hole 751 and the second mounting hole 23, so that the fixed connection between the fastener 76 and the axial limiting block 75, the crankshaft 2 is realized. Correspondingly, the first mounting hole 751 and the second mounting hole 23 can be a hole with smooth inner wall or a threaded hole.

[0092] Similarly, it can be understood that the diameter of the fastener 76 is small, and the position where the second mounting hole 23 is provided can be close to the central axis of the crankshaft 2, even if the fastener 76 is connected with the crankshaft 2 in interference fit or threaded engagement, it will not affect the roundness of the outer peripheral surface of the crankshaft 2, and further will not affect the cooperation between the crankshaft 2 and the inner retainer of the main bearing 95.

[0093] Further, referring to Figure 11In this embodiment, the end of the fastener 76 facing the eccentric sleeve 6 is sunk into the first mounting hole 751, or the end surface of the end of the fastener 76 facing the eccentric sleeve 6 is flush with the end surface of the end of the axial limiting block 75 facing the eccentric sleeve 6. The purpose is to avoid the fastener 76 affecting the setting of the position of the eccentric sleeve 6 due to protruding from the axial limiting block 75.

[0094] Please refer to Figure 12 , compared with Figure 11 The difference between this embodiment and the embodiment shown in the figure is that the eccentric sleeve 6 and the second end of the crank pin 3 can be non-fixedly connected, such as non-interference fit, specifically clearance fit, which can simplify the assembly between the eccentric sleeve 6 and the crank pin 3. Specifically, in this 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, the end surface of the second end of the crank pin 3 protrudes from the end surface of the eccentric sleeve 6 facing the driving vortex disc 41, and on this basis, a second blocking piece 77 is arranged on the part of the crank pin 3 protruding from the eccentric sleeve 6 facing the driving vortex disc 41 and abuts against the end surface of the eccentric sleeve 6 facing the driving vortex disc 41, so that the second blocking piece 77 limits the axial position of the eccentric sleeve 6 on the crank pin 3.

[0095] The second blocking piece 77 can be annular and annularly arranged on the crank pin 3; the second blocking piece 77 can also be non-annular but relatively protruding in the radial direction on the outer circumferential surface of the crank pin 3, at this time, the number of the second blocking piece 77 can be one or more, and multiple second blocking pieces 77 can be arranged along the circumference of the crank pin 3.

[0096] Optionally, the second blocking piece 77 is annular and annularly arranged on the crank pin 3. The outer circumferential surface of the crank pin 3 protruding from the eccentric sleeve 6 forms an annular second groove 32, and the second blocking piece 77 is arranged in the second groove 32.

[0097] The second blocking piece 77 can be a metal piece, specifically made of materials such as chromium carbide, high manganese steel, tungsten carbide, etc., or a plastic piece with good wear resistance, specifically made of materials such as fluoroplastic, nylon, etc.

[0098] In addition, in other optional embodiments, the second blocking piece 77 can be relatively protruding in the radial direction on the outer circumferential surface of the crank pin 3, and the second blocking piece 77 can be fixed on the part of the crank pin 3 protruding from the eccentric sleeve 6 facing the driving vortex disc 41 by means of insertion, adhesion, welding, etc. according to the specific material, which is not particularly limited here.

[0099] The embodiments of the present application also provide an air conditioner (not shown), which comprises the compressor 100 of the above-mentioned embodiments.

[0100] The air conditioner provided by the embodiment of the present application has the advantages and effects corresponding to the compressor 100. Therefore, in the air conditioner, the roundness of the outer circumferential surface of the crankshaft 2 at the position corresponding to the eccentric hole 20 is good, the inner blocking ring raceway of the main bearing 95 matched with the crankshaft 2 is not deformed, the vibration of the air conditioner during operation is low, and the noise of the air conditioner during operation is low.

[0101] Specifically, the air conditioner can further include a condenser (not shown) and an evaporator (not shown), wherein the air outlet of the evaporator is communicated with the air inlet 910 on the low-pressure shell 91, and the condenser is communicated with the air outlet 940 of the oil-gas separator 94. The specific working process can be referred to the above description. In this way, the compressor 100 in the air conditioner and the condenser and the evaporator form a complete heat exchange circuit to perform refrigeration and / or heating.

[0102] The embodiment of the present application further provides a vehicle (not shown) comprising the air conditioner provided by the above embodiment.

[0103] Similarly, the vehicle provided by the embodiment of the present application has the advantages and effects corresponding to the compressor 100 due to the air conditioner provided by the above embodiment. Therefore, in the vehicle, the air conditioner has the advantages of low vibration and low noise during operation, and the vehicle also has the advantages of low vibration and low noise during operation.

[0104] The specific structure of the vehicle is not limited, and the vehicle can be any vehicle capable of assembling the air conditioner. For example, the vehicle generally includes a vehicle body (not shown) and a vehicle head (not shown) arranged at a front position of the vehicle body, and the air conditioner can be at least partially arranged in the vehicle head.

[0105] The specific type of the vehicle is not limited, for example, the vehicle can be a traditional fuel vehicle, or a new energy vehicle, and the new energy vehicle includes but is not limited to a pure electric vehicle, a range-extended electric vehicle, a hybrid electric vehicle, a fuel cell electric vehicle, a hydrogen engine vehicle, etc., and the embodiment does not particularly limit the new energy vehicle.

[0106] The above description is only the preferred embodiment of the present application, and is not used to limit the present application. Any modification, equivalent replacement and improvement made within the spirit and principle of the present application should be included in the protection scope of the present application.

Claims

1. A compressor, comprising: A crankshaft, wherein an eccentric hole is provided at one end of the crankshaft, and the crankshaft has a thin-walled region located on one side of the eccentric hole; A crank pin, one end of which is inserted into the eccentric hole, and the other end of which protrudes from the eccentric hole; An eccentric sleeve is fitted onto the other end of the crank pin; and The scroll assembly is connected to the eccentric sleeve; The characteristic is that one end of the crank pin is clearance-fitted with the eccentric hole, and the eccentric sleeve is fixedly connected to the other end of the crank pin; The compressor also includes an axial limiting component, which is connected to the crankshaft and the crank pin and is used to limit the axial position of the crank pin. The axial limiting assembly includes an axial limiting pin, which is inserted radially into the thin-walled region of the crankshaft and the crank pin. The axial limiting pin and the thin-walled region are in clearance fit; the axial limiting pin and the crank pin are in clearance fit. The crankshaft has a first slot on its outer circumferential surface that communicates with the eccentric hole. The crank pin has a second slot that is coaxial with and communicates with the first slot. The second slot passes through the crank pin radially. The bottom of the first slot has an internal thread, and the bottom end of the axial limiting pin has an external thread. The axial limiting pin is inserted into the first slot and the second slot, and the bottom end of the axial limiting pin engages with the internal thread of the first slot on the crankshaft.

2. The compressor as described in claim 1, characterized in that, The top end face of the axial limiting pin is recessed into the first slot.

3. The compressor as described in claim 2, characterized in that, The first slot is formed on opposite sides of the inner wall of the eccentric hole, and the bottom end of the axial limiting pin passes through the crank pin and is inserted into the crankshaft.

4. An air conditioner, characterized in that, The compressor includes any one of claims 1 to 3.

5. A vehicle, characterized in that, Includes the compressor described in claim 4.

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