Crankshaft swing sleeve split assembly, scroll compressor and new energy automobile

Abstract

The invention provides a crankshaft swing sleeve split assembly, a scroll compressor and a new energy automobile, and the crankshaft swing sleeve split assembly comprises a crankshaft, and the end face of a crank pin of the crankshaft is provided with a protruding crank pin and a positioning hole; the balance block comprises a limiting ring, a sleeve hole formed by the limiting ring is sleeved with the crank pin, and the end face of the crank pin protrudes out of the upper end face of the limiting ring; the swing sleeve is provided with a swing sleeve hole and a positioning hole, the crank pin is sleeved with the swing sleeve hole, the swing sleeve abuts against the end face of the crank pin, and a radial gap is formed between the swing sleeve and the balance block; the stop pin penetrates through the positioning hole to be pressed into the positioning hole in an interference mode, the periphery of the stop pin is connected with a stop elastic layer in a sleeved mode, and a circumferential gap is formed between the periphery of the stop elastic layer and the inner periphery of the positioning hole, so that the swing sleeve and the balance block are independent from each other. According to the scroll compressor, the problems of eccentric wear, large vibration noise and short service life of parts caused by upsetting moment can be solved, and the operation stability, the mute effect and the reliability of the scroll compressor are remarkably improved.

Description

TECHNICAL FIELD

[0001] The present application relates to the field of refrigeration equipment, in particular, to a crankshaft swing sleeve split assembly, a scroll compressor and a new energy vehicle. BACKGROUND

[0002] Scroll compressors are widely used in household, commercial air conditioners and new energy vehicles due to their high efficiency, low noise and compact structure. The core working principle of scroll compressors is that a closed cavity with periodic volume change is formed through the translational and rotational movement of the orbiting scroll relative to the fixed scroll, thereby completing the suction, compression and discharge of refrigerant.

[0003] In the transmission mechanism of a scroll compressor, the crankshaft drives the swing sleeve (or eccentric sleeve) through the eccentric crank pin on it, and the swing sleeve drives the orbiting scroll through the bearing. In order to balance the centrifugal force generated during the rotation of the crankshaft, a balance block is usually provided. In the traditional design, the balance block and the swing sleeve are usually made into an integrated structure, or although they are split, they have a close fit.

[0004] However, this traditional structure has inherent defects. In the integrated structure, there is a certain height difference between the center of gravity of the balance block and the geometric center of the swing sleeve. When the compressor is running at high speed, this height difference will produce a significant overturning moment, causing the swing sleeve to tilt. This tilt will cause the outer circular surface of the swing sleeve to come into uneven contact with the bearing of the orbiting scroll (orbiting bearing), i.e. eccentric wear. Eccentric wear not only produces abnormal vibration and noise, but also sharply accelerates the wear of the swing sleeve and the orbiting bearing, shortening the service life of the compressor.

[0005] In the prior art, there are some improvement schemes for the transmission structure of the compressor. For example, comparative document CN118188498A discloses a split structure, which separates the counterweight balance block from the eccentric sleeve, and uses a rigid transmission boss to partially fit with the transmission hole on the eccentric sleeve to transmit torque. Although this scheme helps to improve the mass center offset problem to some extent through the split design, the rigid transmission boss will produce metal collision when it rotates relative to the eccentric sleeve, resulting in "tapping" noise, and the collision impact will also affect the service life of the parts. In addition, the eccentric sleeve and the counterweight balance block are connected through a plug-in fit, and the contact area is large, which still has the risk of friction and wear.

[0006] Another comparative document CN115306679A discloses a flexible positioning pin structure, which buffers the nonlinear load by providing an elastic layer outside the positioning pin. However, this structure sets the flexible component below the swing sleeve and bears the main load, which is prone to fatigue fracture of the positioning pin under high-speed heavy load conditions of the compressor, and may exacerbate the friction between the swing sleeve and the orbiting bearing.

[0007] Therefore, the application provides a crankshaft swing sleeve split assembly based on a novel swing sleeve structure, a scroll compressor and a new energy vehicle. SUMMARY

[0008] In view of the problems in the prior art, the application aims to provide a crankshaft swing sleeve split assembly, a scroll compressor and a new energy vehicle, which overcome the problems of eccentric wear, large vibration noise and short service life caused by overturning moment, and significantly improve the running stability, mute effect and reliability of the scroll compressor.

[0009] Embodiments of the application provide a compressor, comprising:

[0010] A crankshaft, wherein an end face of a crank pin of the crankshaft is provided with a protruding crank pin and a positioning hole;

[0011] A balance block, wherein the balance block comprises a limiting ring, a sleeve hole of the limiting ring is sleeved with the crank pin, and the end face of the crank pin is protruded from an upper end face of the limiting ring;

[0012] A swing sleeve, wherein the swing sleeve is provided with a swing sleeve hole and a positioning hole, the swing sleeve hole is sleeved with the crank pin, the swing sleeve is abutted with the end face of the crank pin, and a radial gap is formed between the swing sleeve and the balance block;

[0013] A stop pin, wherein the stop pin is pressed into the positioning hole in an interference fit, an outer periphery of the stop pin is sleeved with a stop elastic layer, a circumferential gap is formed between the outer periphery of the stop elastic layer and an inner periphery of the positioning hole, and the swing sleeve and the balance block are independent of each other.

[0014] Preferably, a height difference between the end face of the crank pin and the upper end face of the limiting ring is less than or equal to 10 mm.

[0015] Preferably, a radial gap is formed between the swing sleeve and the balance block, and the radial gap is greater than or equal to 0.5 mm.

[0016] Preferably, the stop elastic layer is a rubber O-ring, and a hardness range of the rubber O-ring is 60-90 IRHD.

[0017] Preferably, an axis of the stop pin is parallel to and eccentrically arranged with a main axis of the crankshaft.

[0018] Preferably, an axis of the positioning hole is parallel to and eccentrically arranged with the main axis of the crankshaft.

[0019] Preferably, an axis of the swing sleeve hole is parallel to an axis of the positioning hole.

[0020] Embodiments of the application also provide a scroll compressor, characterized in that the scroll compressor comprises the above-mentioned crankshaft swing sleeve split assembly and further comprises:

[0021] a motor, driving the rotation of the crankshaft;

[0022] a bearing, sleeving the swing sleeve;

[0023] a moving scroll, connected with the bearing, the motor driving the rotation of the moving scroll through the crankshaft.

[0024] Preferably, when the scroll compressor is running, the moving scroll drives the swing sleeve to rotate without contacting the balance block.

[0025] The embodiment of the present application also provides a new energy automobile, characterized by comprising the scroll compressor.

[0026] The crankshaft swing sleeve split assembly, the scroll compressor and the new energy automobile of the present application can overcome the problems of eccentric wear, large vibration noise and short service life caused by overturning moment, and significantly improve the running stability, mute effect and reliability of the scroll compressor. BRIEF DESCRIPTION OF DRAWINGS

[0027] Other features, objects and advantages of the present application will become more apparent from the following detailed description of non-limiting embodiments with reference to the attached drawings.

[0028] Figure 1 It is a perspective view of a crankshaft swing sleeve split assembly of the present application.

[0029] Figure 2 It is an exploded view of a crankshaft swing sleeve split assembly of the present application.

[0030] Figure 3 It is a top view of a crankshaft swing sleeve split assembly of the present application.

[0031] Figure 4 It is Figure 3 a sectional view along A-A direction.

[0032] Figure 5 It is Figure 4 a local enlarged view of the B area.

[0033] Figure 6 It is an exploded view of the crankshaft swing sleeve split assembly and the moving scroll in the scroll compressor of the present application.

[0034] REFERENCE NUMERALS

[0035] 1 crankshaft

[0036] 2 swing sleeve

[0037] 3 balance block

[0038] 4 stop pin

[0039] 5. Top surface

[0040] 6-hole sleeve

[0041] 7 positioning holes

[0042] 8 Limiting rings

[0043] 9. Swing sleeve hole

[0044] 10. Short shaft section

[0045] 11 Positioning Holes

[0046] 12 bearings

[0047] 13. Moving scroll plate

[0048] 14 Crankpin end face

[0049] 15 Crank pins

[0050] 16. Stopping elastic layer

[0051] G circumferential clearance

[0052] W radial clearance

[0053] H height difference Detailed Implementation

[0054] The following specific examples illustrate the implementation methods of this application. Those skilled in the art can easily understand the other advantages and effects of this application from the content disclosed herein. This application can also be implemented or applied through other different specific embodiments, and various details in this application can be modified or changed according to different viewpoints and application systems without departing from the spirit of this application. It should be noted that, unless otherwise specified, the embodiments and features in the embodiments of this application can be combined with each other.

[0055] The embodiments of this application will now be described in detail with reference to the accompanying drawings, so that those skilled in the art can easily implement the application. This application may be embodied in many different forms and is not limited to the embodiments described herein.

[0056] In the present specification, the expressions "one embodiment", "some embodiments", "exemplary", "detailed example", or "some examples" etc. mean that the particular feature, structure, material, or characteristic being referred to is included in at least one embodiment or example of the present application. Moreover, such expressions do not necessarily refer to the same embodiment or example. Furthermore, such expressions do not necessarily refer to any one or the same embodiment or example. In addition, if an embodiment or example incorporated into the present application refers to another embodiment or example incorporated into the present application, such expression does not mean that each embodiment or example must include the referred embodiment or example, unless specifically stated otherwise.

[0057] In addition, the terms "first", "second", etc. are used herein only to describe various elements, and do not connote any specific importance or imply any relative importance between the elements. Thus, a first element discussed above could be termed a second element without changing the meaning of the description. In the present specification, the meaning of "a plurality" is two or more, unless otherwise explicitly defined specifically.

[0058] In order to clearly illustrate the present application, devices irrelevant to the description are omitted, and the same or similar components are designated by the same reference numerals throughout the specification.

[0059] Throughout the specification, when it is said that an element is "connected" to another element, it includes not only a case where it is "directly connected" but also a case where it is "indirectly connected" with other elements interposed therebetween. In addition, when it is said that an element "includes" a certain component, it does not exclude other components unless otherwise specifically stated, but means that other components can be further included.

[0060] When it is said that an element is "on" another element, it can be directly on the other element, but can also be on the other element with other elements interposed therebetween. When it is said that an element is "directly on" another element, there are no other elements interposed therebetween.

[0061] Although the terms first, second, etc. can be used herein to describe various elements, these elements should not be limited by these terms. These terms are only used to distinguish one element from another. For example, a first interface and a second interface, etc. As used herein, the singular forms "a", "an" and "the" are intended to include the plural forms as well, unless the context clearly indicates otherwise. It will be further understood that the terms "comprises", "comprising", "includes" and / or "including", when used herein, specify the presence of stated features, steps, operations, elements, components, items, and / or groups but do not preclude the presence or addition of one or more other features, steps, operations, elements, components, items, and / or groups thereof. As used herein, the terms "or" and "and / or" are to be interpreted as inclusive, i.e., as meaning either item by itself or any combination of the items. Thus, "A, B or C" or "A, B and / or C" means "any of the following: A; B; C; A and B; A and C; B and C; A, B and C". This definition applies to all uses of the terms "or" and "and / or", unless a context dictates otherwise.

[0062] The professional terms used herein are used only to refer to specific embodiments and are not intended to limit the present application. The singular form is used herein, unless the context clearly indicates otherwise, to include the plural form. The meaning of "include" used in the specification is to specify a certain feature, region, integer, step, operation, element, and / or component, and is not to exclude the presence or addition of other features, regions, integers, steps, operations, elements, and / or components.

[0063] Although not differently defined, the technical and scientific terms used herein include the technical terms used herein and the scientific terms, all of which have the same meaning as generally understood by a person skilled in the art to which the present application pertains. The terms defined in a generally used dictionary are additionally explained to have the meaning consistent with the content of the related technical documents and the current prompt, unless defined, and should not be over-interpreted as an ideal or very formal meaning.

[0064] Figure 1 A perspective view of a crankshaft swing set sub-assembly according to the present application. Figure 2 An exploded view of a crankshaft swing set sub-assembly according to the present application. Figure 3 A top view of a crankshaft swing set sub-assembly according to the present application. Figure 4 A perspective view of a crankshaft swing set sub-assembly according to the present application. Figure 3 A sectional view in the direction of A-A. Figure 5 A perspective view of a crankshaft swing set sub-assembly according to the present application. Figure 4 A partial enlarged view of the B region. As Figures 1 to 5As shown, the split assembly of the crankshaft balance sleeve of the present application comprises a crankshaft 1, a balance sleeve 2, a balance weight 3, and a stop pin 4. The crankpin end face 14 of the short shaft part 10 of the crankshaft 1 is provided with a protruding crankpin 15 and a positioning hole 7. The balance weight 3 comprises a limiting ring 8, the sleeve hole 6 of which is sleeved over the crankpin 15, so that the crankpin end face 14 protrudes from the upper end face 5 of the limiting ring 8. The balance sleeve 2 is provided with a balance sleeve hole 9 and a positioning hole 11, the balance sleeve hole 9 is sleeved with the crankpin 15, so that the balance sleeve 2 abuts against the crankpin end face 14, and a radial gap 17 is formed between the balance sleeve 2 and the balance weight 3. The stop pin 4 is inserted into the positioning hole 7 in an interference fit, and the outer periphery of the stop pin 4 is sleeved with a stop elastic layer 16, and a circumferential gap G is formed between the outer periphery of the stop elastic layer 16 and the inner periphery of the positioning hole 11, so that the balance sleeve 2 and the balance weight 3 are not in contact with each other and are independent of each other. The split balance sleeve of the present application is designed to be lightweight, and only needs to drive itself and associated small parts to move, the balance sleeve 2 and the balance weight 3 are not directly connected, the balance weight 3 is fixed to the crankshaft, and the crankpin end face 14 is higher than the balance weight end face 5, the balance sleeve 2 is matched with the crankshaft 1 through the stop pin "gap + rigid and flexible positioning pin buffer", thereby optimizing the problem of height difference between the outer circle center of the balance sleeve and the center of the balance sleeve, and combining the rigid and flexible structure of the stop pin, reducing the overturning moment generated during the operation of the compressor, thereby improving the eccentric wear problem of the dynamic disc bearing and the balance sleeve, reducing the collision and wear of the balance sleeve and the dynamic disc bearing, and further improving the noise and increasing the service life.

[0065] In a preferred embodiment, the axis of the stop pin 4 is parallel to and eccentric to the main axis of the crankshaft 1, but not limited thereto.

[0066] In a preferred embodiment, the axis of the positioning hole 7 is parallel to and eccentric to the main axis of the crankshaft 1, but not limited thereto.

[0067] In a preferred embodiment, the axis of the balance sleeve hole 9 is parallel to the axis of the positioning hole 11, but not limited thereto.

[0068] In a preferred embodiment, the balance sleeve 2 and the balance weight 3 are of a split structure, and the weight of the balance sleeve 2 in the present application is 1 / 5 to 1 / 2 of the weight of a traditional integrated balance sleeve (the balance sleeve and the balance weight are integrated), but not limited thereto.

[0069] Figure 5 For Figure 4 The local enlarged view of the middle B area. Figure 5 The height difference H between the balance weight upper end face 5 and the crankpin end face 14, the radial gap W between the balance sleeve 2 and the balance weight 3, and the gap G between the stop elastic layer 16 and the positioning hole 11 are clearly shown. It can be seen that there is a gap in both height and radial directions between the balance weight 3 and the balance sleeve 2 in the present application, so that the balance weight 3 and the balance sleeve 2 do not contact each other (to ensure that the balance weight 3 and the balance sleeve 2 are always not in contact), and the rotation of the balance sleeve 2 does not drive the balance weight 3 to move.

[0070] In a preferred embodiment, the height difference H between the crank pin end face 14 and the upper end face 5 of the limit ring 8 is less than or equal to 10 mm, but not limited thereto.

[0071] In a preferred embodiment, the height difference H is one of 3 mm, 4 mm, 5 mm, 6 mm, 7 mm, 8 mm, 9 mm, but not limited thereto.

[0072] In a preferred embodiment, a radial gap W is formed between the swing sleeve 2 and the balance block 3, and the radial gap W is greater than or equal to 0.5 mm, but not limited thereto.

[0073] In a preferred embodiment, the radial gap W is one of 0.1 mm, 0.2 mm, 0.3 mm, 0.4 mm, but not limited thereto.

[0074] In a preferred embodiment, the stop elastic layer 16 is a rubber O-ring, and the hardness range is 60 IRHD to 90 IRHD (International Rubber Hardness Standard), but not limited thereto.

[0075] In a preferred embodiment, the hardness of the stop elastic layer 16 is one of 65 IRHD, 70 IRHD, 75 IRHD, 80 IRHD, 85 IRHD, but not limited thereto.

[0076] The present application relates to a crankshaft swing sleeve split structure for a scroll compressor, specifically comprising a crankshaft, a swing sleeve, a balance block and a stop pin. The balance block is fixed on the crankshaft, and the end face thereof is lower than the crank pin end face of the crankshaft to reduce the overturning moment. The swing sleeve and the balance block are completely split structure, and a radial gap exists between them to avoid mutual friction. The stop pin is fixed on the crankshaft, and an external stop elastic layer is sleeved thereon, which is gap-fitted with the positioning hole on the swing sleeve to form a "rigid-flexible composite" buffer positioning structure. The present application effectively solves the problems of eccentric wear, large vibration and noise and short service life of components of the traditional integrated swing sleeve caused by the overturning moment by optimizing the mass distribution and introducing flexible buffering, and significantly improves the running stability, silent effect and reliability of the scroll compressor.

[0077] Compared with the prior art, the crankshaft swing sleeve split structure provided by the present application has the following significant advantages:

[0078] 1. The crankshaft swing sleeve split structure of the present application can fundamentally reduce the overturning moment: by setting the upper end face of the balance block below the crank pin end face, the mass center of the balance block is lowered, the overturning moment causing the swing sleeve to tilt is effectively reduced, and the eccentric wear problem of the swing sleeve and the dynamic disc bearing is alleviated from the source.

[0079] 2. The crankshaft swing sleeve split structure of the present application can completely eliminate friction between components: the swing sleeve and the balance block of the present application are completely separated and have a radial gap, eliminating friction loss between them and prolonging the service life of the components.

[0080] 3. The crankshaft swing sleeve split structure of the present application can effectively reduce noise and vibration: the present application adopts a "rigid and flexible composite" stop pin and swing sleeve gap cooperation, avoiding rigid collision of the swing sleeve during rotation and the positioning structure, eliminating the "tapping" abnormal sound, and significantly improving the quietness of the compressor.

[0081] 4. The crankshaft swing sleeve split structure of the present application can improve reliability and service life: based on the above advantages, the structure greatly reduces the wear, impact and unbalanced load of the key moving parts, thereby comprehensively improving the reliability and service life of the scroll compressor in operation.

[0082] 5. The crankshaft swing sleeve split structure of the present application can be simple in structure and easy to implement: the structure is ingeniously changed without the need for complex processes or expensive materials, and is convenient to manufacture and assemble, which is conducive to industrialization and popularization.

[0083] Figure 6 The present application is a scroll compressor with a crankshaft swing sleeve split assembly and a moving scroll. As shown in Figure 6 The present application also provides a scroll compressor Figure 6 which shows the layout structure of the scroll compressor, comprising the crankshaft swing sleeve split assembly as described above, and further comprising a motor (not shown in the figure), a bearing 12, and a moving scroll 13. Among them, the motor drives the rotation of the crankshaft 1. The bearing 12 is sleeved with the swing sleeve 2. The moving scroll 13 is connected with the bearing 12, and the motor drives the moving scroll 13 to rotate through the crankshaft 1. The scroll compressor of the present application has a height difference between the center of gravity of the balance block of the integral swing sleeve outer ring and the swing sleeve, which is easy to produce overturning moment when the compressor is working, resulting in eccentric wear of the swing sleeve and the bearing, producing noise and shortening the service life of the moving disc bearing.

[0084] In a preferred embodiment, when the scroll compressor is running, the moving scroll 13 drives the swing sleeve 2 to rotate without contacting the balance block 3, but not limited thereto. The scroll compressor system of the present application can also reduce component eccentric wear, reduce vibration and noise, prolong service life, and improve the running stability, quietness and reliability of the scroll compressor due to the adoption of the above-mentioned crankshaft swing sleeve split assembly.

[0085] The specific embodiments of the present application include:

[0086] As Figures 1 to 5As shown, the application provides a split structure of a crankshaft swing sleeve for a scroll compressor, which mainly consists of a crankshaft 1, a swing sleeve 2, a balance block 3 and a stop pin assembly. A crankpin 15 and a positioning hole 7 are arranged on a crankpin end face 14 of a crankpin end of the crankshaft 1. The balance block 3 comprises a limiting ring 8, the limiting ring 8 forms a sleeve hole 6 which sleeves the crankpin 15, and the crankpin end face 14 is protruded from an upper end face 5 of the limiting ring 8. The swing sleeve 2 is provided with a swing sleeve hole 9 and a positioning hole 11, the swing sleeve hole 9 sleeves the crankpin 15, and the swing sleeve 2 abuts against the crankpin end face 14, and a radial gap 17 is formed between the swing sleeve 2 and the balance block 3. The stop pin 4 penetrates the positioning hole 11 to screw the positioning hole 7, and an outer periphery of the stop pin 4 sleeves a stop elastic layer 16, a circumferential gap G is formed between the outer periphery of the stop elastic layer 16 and an inner periphery of the positioning hole 11, so that the swing sleeve 2 and the balance block 3 are independent of each other.

[0087] Specifically, the crankshaft 1 is a power input shaft of the compressor, which is driven to rotate by a motor. An eccentric crankpin 15 is arranged on an upper portion of the crankshaft 1, and a top end of the crankpin 15 is a flat crankpin end face 14 for supporting the swing sleeve 2.

[0088] The balance block 3 is usually made of high-density metal, which is fixedly installed on the crankshaft 1 by means of key connection, interference fit or bolt connection. The balance block 3 is provided with a balance block sleeve hole 6 through which the crankpin 15 penetrates. According to the core design of the application, the upper end face 5 of the balance block 3 is processed to be lower than the crankpin end face 14, thereby forming a height difference H. The height difference H is preferably controlled within a range of ≤10 mm. By reducing the installation height of the balance block 3, the mass center of the balance block 3 is lowered, thereby significantly reducing the overturning moment acting on the swing sleeve 2 when the crankshaft 1 rotates.

[0089] The swing sleeve 2 is an independent annular member, which is preferably designed to be lightweight, and the weight of the swing sleeve 2 is about 1 / 5 to 1 / 2 of the corresponding part in the traditional integrated structure. The swing sleeve 2 is provided with two main holes: one is a swing sleeve hole 9 for penetrating the crankpin 15, so that the swing sleeve 2 can be sleeved on the crankpin 15 and tightly abut against the crankpin end face 14; the other is a positioning hole 11. After the swing sleeve 2 is installed, a gap G of not less than 0.5 mm is reserved in the radial direction between the lower portion of the swing sleeve 2 and the balance block 3. The gap G ensures that the swing sleeve 2 and the balance block 3 do not physically contact in any working state, and completely avoids the friction therebetween.

[0090] The stop pin assembly is composed of a stop pin 4 and a stop elastic layer 16. The stop pin 4 is a rigid pin shaft, the bottom of which is fixed in a corresponding mounting hole of the crankshaft 1. The stop elastic layer 16 is preferably an O-shaped ring of rubber material, the hardness of which is between 60 and 90 IRHD, and it is interference-fitted on the middle and upper part of the stop pin 4. After assembly, the stop pin 4 with the stop elastic layer 16 extends into the positioning hole 11 of the swing sleeve 2. The key point is that the outer diameter of the stop elastic layer 16 is slightly smaller than the inner diameter of the positioning hole 11, so that a clearance fit is formed between them, rather than a tight fit or an interference fit.

[0091] As shown in Figure 6 The working principle of the present application is as follows: when the compressor starts, the crankshaft 1 is driven to rotate by the motor. The balance block 3 fixed on the crankshaft 1 rotates synchronously, balancing the centrifugal force of the crankshaft. Since the centroid of the balance block 3 moves downward, the overturning moment generated is small, and the swing sleeve 2 is not prone to tilting. The rotation of the crankshaft 1 is transmitted to the swing sleeve 2 through the crank pin 15. The swing sleeve 2 drives the orbiting scroll 13 connected thereto to perform rotary motion under the drive of the crank pin 15 (the bearing 12 fixed below the orbiting scroll 13 is driven by the crank pin 15 to rotate, thereby driving the orbiting scroll 13 to rotate). During the motion, when the orbiting scroll 13 slightly retreats due to load changes or other reasons, it will tend to rotate relative to the crankshaft 1, and the inner wall of the positioning hole 11 of the swing sleeve 2 will tend to contact the stop elastic layer 16 of the stop pin assembly. Since it is a clearance fit and there is an elastic layer, this contact is flexible and buffered, effectively absorbing impact energy and avoiding direct and violent collision between metals, thereby eliminating the unpleasant "click" collision noise and protecting the stop pin 4 and the positioning hole 11 of the swing sleeve 2 from damage. Throughout the process, the swing sleeve 2 and the balance block 3 always maintain a height difference H and a gap W, so they do not interfere with each other and there is no friction loss. In summary, through a series of cooperatively designed structural improvements, the present application systematically solves the technical problems of large overturning moment, eccentric wear, high noise and short service life that have long existed in the transmission mechanism of scroll compressors, and has high practical value and wide application prospects.

[0092] The new energy vehicle of the present application also comprises the new energy vehicle as described above. The related technical features are as described above, and will not be repeated here. The new energy vehicle of the present application can also reduce the part eccentric wear, reduce the vibration noise, prolong the service life, and improve the running stability, the mute effect and the reliability of the scroll compressor due to the adoption of the compressor as described above. The present application effectively avoids the problem of the tilting of the swing sleeve when the crankshaft rotates due to the over-heavy balance block in the traditional balance block and swing sleeve integrated structure. The excessive wear of the swing sleeve and the dynamic disc bearing is reduced, and the service life of the swing sleeve and the dynamic disc bearing is ultimately significantly prolonged, and the overall running stability and reliability of the compressor are improved. The present application also utilizes the flexible buffer of the rubber in the stop pin 4 to avoid the direct impact of the swing sleeve 2 and the metal of the stop pin. The new energy vehicle of the present application can reduce the vehicle noise and vibration when the compressor is running, and optimize the riding experience of the passengers.

[0093] In summary, the present application aims to provide a crankshaft swing sleeve split assembly, a scroll compressor and a new energy vehicle, which can overcome the problems of eccentric wear, large vibration noise and short service life of components caused by the overturning moment, and significantly improve the running stability, mute effect and reliability of the scroll compressor.

[0094] The above is a further detailed description of the present application in combination with specific preferred embodiments, and cannot be considered as limiting the specific implementation of the present application to these descriptions. For ordinary skilled persons in the technical field to which the present application belongs, some simple deductions or substitutions can be made without departing from the concept of the present application, and all of them should be considered as falling within the protection scope of the present application.

Claims

1. A crankshaft swing sleeve split assembly, characterized in that, include: A crankshaft (1) has a protruding crank pin (15) and a positioning hole (7) on the crank pin end face (14). A balance block (3) includes a limiting ring (8), the sleeve hole (6) formed by the limiting ring (8) passes through the crank pin (15), and the end face (14) of the crank pin protrudes from the upper end face (5) of the limiting ring (8). A swing sleeve (2) is provided with a swing sleeve hole (9) and a positioning hole (11). The swing sleeve hole (9) is fitted with the crank pin (15), so that the swing sleeve (2) abuts against the end face (14) of the crank pin. A radial gap (17) is formed between the swing sleeve (2) and the balance block (3). A stop pin (4) passes through the positioning hole (11) and is pressed into the positioning hole (7) with an interference fit. A stop elastic layer (16) is sleeved on the outer periphery of the stop pin (4). A circumferential gap (G) is formed between the outer periphery of the stop elastic layer (16) and the inner periphery of the positioning hole (11), so that the swing sleeve (2) and the balance block (3) are independent of each other.

2. The crankshaft swing sleeve split assembly as described in claim 1, characterized in that, The height difference (H) between the crank pin end face (14) and the upper end face (5) of the limiting ring (8) is less than or equal to 10 mm.

3. The crankshaft swing sleeve split assembly as described in claim 1, characterized in that, A radial gap (W) is formed between the swing sleeve (2) and the balance block (3), and the radial gap (W) is greater than or equal to 0.5 mm.

4. The crankshaft swing sleeve split assembly as described in claim 1, characterized in that, The stop elastic layer (16) is a rubber O-ring with a hardness range of 60 to 90 IRHD.

5. The crankshaft swing sleeve split assembly as described in claim 1, characterized in that, The axis of the stop pin (4) is parallel to and eccentrically set with respect to the main axis of the crankshaft (1).

6. The crankshaft swing sleeve split assembly according to claim 1, characterized in that, The axis of the positioning hole (7) is parallel to and eccentrically set with respect to the main axis of the crankshaft (1).

7. The crankshaft swing sleeve split assembly according to claim 1, characterized in that, The axis of the swing sleeve hole (9) is parallel to the axis of the positioning hole (11).

8. A scroll compressor, characterized in that, Including the crankshaft swing sleeve split assembly as described in any one of claims 1 to 6, further comprising: An electric motor drives the crankshaft (1) to rotate; A bearing (12) is fitted onto the swing sleeve (2); A rotating scroll (13) is connected to the bearing (12), and the motor drives the rotating scroll (13) to rotate through the crankshaft (1).

9. The scroll compressor as described in claim 8, characterized in that, When the scroll compressor is running, the moving scroll (13) drives the swing sleeve (2) to rotate without contacting the balance block (3).

10. A new energy vehicle, characterized in that, Including the scroll compressor as described in claim 8.

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