Pump body assembly for compressor and compressor

Abstract

The invention relates to the technical field of compressors, and discloses a pump body assembly for a compressor. The pump body assembly comprises a piston and a sliding piece, the piston comprises a first piston body and a second piston body which are arranged in a split mode and are opposite in the axial direction of the piston, the first piston body is provided with a first containing cavity, the second piston body is provided with a second containing cavity, the first piston body abuts against the second piston body, and the first containing cavity and the second containing cavity jointly form a limiting containing space. The sliding piece comprises a connecting end, and the connecting end is embedded into the limiting containing space so that the sliding piece can be connected with the piston. Through the split type assembling mode, the assembling precision requirement of the sliding piece and the piston can be lowered, assembling of the sliding piece and the piston is more convenient, and the assembling difficulty of the sliding piece and the piston is effectively lowered. The invention further discloses the compressor.

Description

Technical Field

[0001] The present application relates to the technical field of compressors, and particularly to a pump body assembly and a compressor for a compressor. Background Art

[0002] Currently, in a rotary compressor, when the piston rotates, the sliding vane will reciprocate radially. In order to enable the sliding vane to closely fit the outer surface of the piston, a spring is usually installed at the tail of the sliding vane, and the sliding vane is closely fitted with the piston under the action of the spring. However, when the compressor is operating at a low frequency, due to the too low suction temperature, liquid-carrying operation of the sliding vane and the piston will occur during the compression process, thereby deteriorating the lubrication effect. This will cause the sliding vane to not always follow the movement of the piston, resulting in the separation of the sliding vane from the piston.

[0003] To prevent the sliding vane from separating from the piston, a related technology discloses a sliding vane anti-separation structure, which includes a piston and a sliding vane cooperating with the piston. A circumferential concave inverted T-shaped groove is formed on the outer peripheral surface of the piston, and a convex block protruding outward is provided at one end of the sliding vane. A pair of pin shafts are provided on opposite sides of the convex block, and the pair of pin shafts cooperate with the inverted T-shaped groove to embed the sliding vane into the piston to prevent the sliding vane from separating from the piston.

[0004] In the process of implementing the embodiments of the present disclosure, it is found that at least the following problems exist in the related technology:

[0005] In the related technology, although the sliding vane can be prevented from separating from the piston by embedding the sliding vane into the piston, the matching structure of the pin shaft and the inverted T-shaped groove has high matching precision requirements, and the assembly process is relatively complex.

[0006] It should be noted that the information disclosed in the above background art section is only used to enhance the understanding of the background of the present application, and therefore may include information that does not constitute the prior art known to those of ordinary skill in the art. Summary of the Invention

[0007] To have a basic understanding of some aspects of the disclosed embodiments, a simple summary is given below. The summary is not a general review, nor is it intended to identify key / important constituent elements or delineate the protection scope of these embodiments, but rather serves as a preface to the subsequent detailed description.

[0008] The embodiments of the present disclosure provide a pump body assembly and a compressor for a compressor to reduce the assembly difficulty between the sliding vane and the piston on the basis of preventing the sliding vane from separating from the piston.

[0009] According to the first aspect of the embodiments of the present invention, a pump body assembly for a compressor is provided, which includes a piston and a sliding vane. The piston includes a first piston body and a second piston body that are separately arranged and opposite to each other along the axial direction of the piston. The first piston body is provided with a first accommodation cavity, and the second piston body is provided with a second accommodation cavity. The first piston body and the second piston body are in contact with each other, and the first accommodation cavity and the second accommodation cavity together form a limit accommodation space. The sliding vane includes a connection end, and the connection end is embedded in the limit accommodation space so that the sliding vane is connected to the piston.

[0010] Optionally, the first piston body is provided with a first limit portion, and the connection end is provided with a first limit cooperation portion. The first limit portion and the first limit cooperation portion cooperate with each other to limit the movement of the connection end along the axial direction of the piston relative to the first piston body. The second piston body is provided with a second limit portion, and the connection end is provided with a second limit cooperation portion. The second limit portion and the second limit cooperation portion cooperate with each other to limit the movement of the connection end along the axial direction of the piston relative to the second piston body.

[0011] Optionally, the first limit portion includes a first limit groove, and the first limit cooperation portion is a first limit boss. The first limit boss is embedded in the first limit groove, and the first limit boss can rotate relative to the first limit groove. The second limit portion includes a second limit groove, and the second limit cooperation portion is a second limit boss. The second limit boss is embedded in the second limit groove, and the second limit boss can rotate relative to the second limit groove.

[0012] Optionally, a cooperation gap is provided between the connection end and the inner wall surface of the limit accommodation space so that the connection end can rotate in the limit accommodation space, thereby enabling the piston to swing relative to the sliding vane. Among them, the cooperation gap between the connection end and the inner wall surface of the limit accommodation space is greater than or equal to 0.03 mm and less than or equal to 0.06 mm.

[0013] Optionally, a first opening is provided on the outer peripheral wall of the first piston body, and the first opening is communicated with the first accommodation cavity. A second opening is provided on the outer peripheral wall of the second piston body, and the second opening is communicated with the second accommodation cavity. The first opening and the second opening are opposite to each other along the axial direction of the piston, and the first opening and the second opening are correspondingly communicated to form an assembly opening. The sliding vane further includes a transition section, and the transition section is provided at one end of the connection end away from the piston. The transition section is connected to the connection end, and the transition section passes through the assembly opening.

[0014] Optionally, the pump body assembly for a compressor further includes a cylinder, which is provided with a working chamber and a sliding vane groove that are communicated with each other. A piston is arranged in the working chamber and can move in the working chamber. The sliding vane is slidably arranged in the sliding vane groove. Along the axial direction of the piston, the cross-sectional shape of the connecting end of the sliding vane is a first arc, and the cross-sectional shape of the limiting accommodation space is a second arc. The centers of the first arc and the second arc coincide. Wherein, the half-width d of the assembly port along the circumferential direction of the piston, the width t of the transition section along the circumferential direction of the piston, the eccentricity e of the piston, the distance L between the center of the second arc and the center of the piston along the radial direction of the cylinder, the length h of the assembly port along the radial direction of the piston, and the radius r of the second arc satisfy the following formula:

[0015]

[0016] Optionally, the sliding vane further includes: a sliding vane body arranged at one end of the transition section away from the connecting end. The sliding vane body is connected to the transition section, and the dimension of the sliding vane body along the axial direction of the piston is greater than the dimension of the assembly port along the axial direction of the piston.

[0017] Optionally, the sliding vane further includes: a sealing portion arranged at one end of the sliding vane body facing the piston. The sealing portion protrudes arcuately towards the piston, and the sealing portion abuts against the outer wall surface of the piston.

[0018] Optionally, the dimension of the first accommodation cavity along the axial direction of the piston is smaller than the dimension of the first piston body along the axial direction of the piston; and / or, the dimension of the second accommodation cavity along the axial direction of the piston is smaller than the dimension of the second piston body along the axial direction of the piston; and / or, the ratio of the dimension of the first opening along the axial direction of the piston to the dimension of the first accommodation cavity along the axial direction of the piston is greater than or equal to 0.5 and less than 1; and / or, the ratio of the dimension of the second opening along the axial direction of the piston to the dimension of the second accommodation cavity along the axial direction of the piston is greater than or equal to 0.5 and less than 1; and / or, the dimension of the connecting end along the axial direction of the piston is greater than the dimension of the transition section along the axial direction of the piston; and / or, the ratio between the dimension of the connecting end along the axial direction of the piston and the dimension of the sliding vane body along the axial direction of the piston is greater than or equal to 0.5.

[0019] According to the second aspect of the embodiments of the present invention, a compressor is provided, which includes the pump body assembly for a compressor as described in any one of the above disclosed embodiments.

[0020] The pump body assembly for a compressor and the compressor provided by the embodiments of the present disclosure can achieve the following technical effects:

[0021] The split design of the piston along its axial direction enables one end of the connecting end of the sliding vane to be pre-positioned and mated with the first accommodation cavity first. When the first piston body and the second piston body are buckled and abutted against each other, the other end of the connecting end is naturally embedded in the second accommodation cavity, thereby enabling overall limiting. The split assembly method can reduce the assembly precision requirements for the sliding vane and the piston, making the assembly of the sliding vane and the piston more convenient and effectively reducing the assembly difficulty of the sliding vane and the piston. The limiting accommodation space is jointly constituted by the first accommodation cavity of the first piston body and the second accommodation cavity of the second piston body. A surface contact is formed between the sliding vane and the piston, providing stable support and limiting effect for the connecting end of the sliding vane. This can effectively improve the connection stability between the sliding vane and the piston, thereby reducing the risk of the sliding vane detaching from the piston during the high-speed operation of the compressor.

[0022] The above general description and the following description are only exemplary and explanatory, and are not used to limit this application. BRIEF DESCRIPTION OF THE DRAWINGS

[0023] One or more embodiments are exemplarily illustrated by corresponding drawings. These exemplary illustrations and the drawings do not constitute a limitation on the embodiments. Elements with the same reference numerals in the drawings are shown as similar elements. The drawings do not constitute a scale limitation, and among them:

[0024] Figure 1 is a schematic structural diagram of a pump body assembly for a compressor provided by an embodiment of the present disclosure;

[0025] Figure 2 is another schematic structural diagram of a pump body assembly for a compressor provided by an embodiment of the present disclosure;

[0026] Figure 3 is Figure 2 a schematic cross-sectional view taken along the A-A direction shown;

[0027] Figure 4 is Figure 3 an enlarged schematic view of part B shown;

[0028] Figure 5 is another schematic structural diagram of a pump body assembly for a compressor provided by an embodiment of the present disclosure;

[0029] Figure 6 is Figure 5 an enlarged schematic view of part C shown;

[0030] Figure 7 is a schematic structural diagram of the assembly of a sliding vane and a piston provided by an embodiment of the present disclosure;

[0031] Figure 8 is another schematic structural diagram of the assembly of a sliding vane and a piston provided by an embodiment of the present disclosure;

[0032] Figure 9 is Figure 8 a schematic cross-sectional view in the D-D direction as shown;

[0033] Figure 10 is a schematic diagram of a piston structure provided by an embodiment of the present disclosure;

[0034] Figure 11 is a schematic diagram of the structure of another piston provided by an embodiment of the present disclosure;

[0035] Figure 12 is Figure 11 a schematic cross-sectional view in the E-E direction as shown;

[0036] Figure 13 is a schematic diagram of the structure of a first piston body provided by an embodiment of the present disclosure;

[0037] Figure 14 is Figure 13 a schematic cross-sectional view in the F-F direction as shown;

[0038] Figure 15 is a schematic diagram of the structure of a sliding vane provided by an embodiment of the present disclosure;

[0039] Figure 16 is a schematic diagram of the structure of another sliding vane provided by an embodiment of the present disclosure.

[0040] Reference numerals:

[0041] 10: Piston; 101: Center of the piston; 11: Limit accommodation space; 111: Second arc; 112: Center of the second arc; 12: Assembly port; 13: Outer wall surface;

[0042] 20: First piston body; 21: First accommodation cavity; 22: First limit portion; 221: First limit groove; 23: First opening; 24: First limit space;

[0043] 30: Second piston body; 31: Second accommodation cavity; 32: Second limit portion; 321: Second limit groove; 33: Second opening; 34: Second limit space;

[0044] 40: Sliding vane; 41: Connection end; 411: First limit fitting portion; 412: First limit boss; 413: Second limit fitting portion; 414: Second limit boss; 415: First arc; 42: Transition section; 43: Sliding vane body; 44: Sealing portion;

[0045] 50: Crankshaft;

[0046] 60: Cylinder; 61: Working cavity; 62: Sliding vane groove. Detailed implementation manners

[0047] In order to understand the features and technical content of the embodiments of the present disclosure in more detail, the implementation of the embodiments of the present disclosure will be described in detail below with reference to the accompanying drawings. The accompanying drawings are for reference and illustration only and are not used to limit the embodiments of the present disclosure. In the following technical description, for the sake of explanation, numerous details are provided to give a thorough understanding of the disclosed embodiments. However, one or more embodiments may still be implemented without these details. In other cases, well-known structures and devices may be shown in a simplified manner to simplify the drawings.

[0048] In the embodiments of the present disclosure, terms such as "first" and "second" in the specification, claims, and the above-mentioned drawings are used to distinguish similar objects and do not necessarily describe a specific order or sequence. It should be understood that such data can be interchanged under appropriate circumstances for the embodiments of the present disclosure described herein. In addition, the terms "comprising" and "having" and any variations thereof are intended to cover non-exclusive inclusion.

[0049] In the embodiments of the present disclosure, the orientation or positional relationship indicated by terms such as "upper", "lower", "inner", "middle", "outer", "front", and "rear" is based on the orientation or positional relationship shown in the drawings. These terms are mainly used to better describe the embodiments of the present disclosure and their embodiments, and are not used to limit that the indicated devices, elements, or components must have a specific orientation or be constructed and operated in a specific orientation. Moreover, in addition to being able to represent an orientation or positional relationship, some of the above terms may also be used to represent other meanings. For example, the term "upper" may also be used to represent a certain attachment relationship or connection relationship in some cases. For those of ordinary skill in the art, the specific meanings of these terms in the embodiments of the present disclosure can be understood according to specific circumstances.

[0050] In addition, the terms "arranged", "connected", and "fixed" should be understood in a broad sense. For example, "connected" can be a fixed connection, a detachable connection, or an integral structure; it can be a mechanical connection or an electrical connection; it can be directly connected, or indirectly connected through an intermediate medium, or there is internal communication between two devices, elements, or components. For those of ordinary skill in the art, the specific meanings of the above terms in the embodiments of the present disclosure can be understood according to specific circumstances.

[0051] Unless otherwise specified, the term "plurality" means two or more.

[0052] In the embodiments of the present disclosure, the character " / " indicates that the objects before and after are in an "or" relationship. For example, A / B means: A or B.

[0053] The term "and / or" is an associative relationship describing an object and indicates that three relationships can exist. For example, A and / or B means: A or B, or, A and B these three relationships.

[0054] It should be noted that, without conflict, the embodiments in the present disclosure and the features in the embodiments may be combined with each other.

[0055] Combined with Figures 1 - 16 As shown, the present disclosure provides a pump body assembly for a compressor, including a piston 10 and a sliding vane 40.

[0056] The piston 10 includes a first piston body 20 and a second piston body 30 that are separately arranged and axially opposite to each other along the piston 10. The first piston body 20 is provided with a first accommodation cavity 21, and the second piston body 30 is provided with a second accommodation cavity 31. The first piston body 20 and the second piston body 30 are in contact with each other, and the first accommodation cavity 21 and the second accommodation cavity 31 together form a limiting accommodation space 11; the sliding vane 40 includes a connecting end 41, and the connecting end 41 is embedded in the limiting accommodation space 11 so that the sliding vane 40 is connected to the piston 10.

[0057] The piston's radial direction is as shown in the x-axis direction in Figure 7 The piston's circumferential direction is as shown in the y-axis direction in Figure 7 The piston's axial direction is as shown in the z-axis direction in Figure 7

[0058] Using the pump body assembly for a compressor provided by the embodiments of the present disclosure, the split design of the piston 10 along its own axis enables one end of the connecting end 41 of the sliding vane 40 to be pre-positioned and fitted with the first accommodation cavity 21 first. When the first piston body 20 and the second piston body 30 are buckled and in contact with each other, the other end of the connecting end 41 is naturally embedded in the second accommodation cavity 31, thereby enabling overall limitation. The split assembly method can reduce the assembly accuracy requirements for the sliding vane 40 and the piston 10, making the assembly of the sliding vane 40 and the piston 10 more convenient and effectively reducing the assembly difficulty of the sliding vane 40 and the piston 10. The limiting accommodation space 11 is jointly formed by the first accommodation cavity 21 of the first piston body 20 and the second accommodation cavity 31 of the second piston body 30. A surface contact is formed between the sliding vane 40 and the piston 10, providing stable support and limitation for the connecting end 41 of the sliding vane 40. This can effectively improve the connection stability between the sliding vane 40 and the piston 10, thereby reducing the risk of the sliding vane 40 detaching from the piston 10 during the high-speed operation of the compressor.

[0059] Optionally, combined with Figures 1 - 3 As shown, the pump body assembly further includes a cylinder 60 and a crankshaft 50. The cylinder 60 is provided with a working cavity 61 and a sliding vane groove 62 that are communicated with each other; the piston 10 is arranged in the working cavity 61 and can move in the working cavity. The first piston body 20 and the second piston body 30 are sleeved outside the crankshaft 50; the sliding vane 40 is movably arranged in the sliding vane groove 62.

[0060] ​The crankshaft 50 limits the first piston body 20 and the second piston body 30, and at the same time, the inner wall surface of the working chamber 61 also limits the first piston body 20 and the second piston body 30. In addition, the connecting end 41 of the sliding vane 40 is connected to the piston 10, so that the sliding vane 40 also limits the piston 10. In this way, through multi-faceted limiting, the dislocation of the first piston body 20 and the second piston body 30 can be effectively prevented. It can be understood that other connecting structures can also be provided between the first piston body 20 and the second piston body 30 for fastening.

[0061] Optionally, as shown in Figure 12 the first accommodating cavity 21 and the second accommodating cavity 31 correspond to each other along the axial direction of the piston 10.

[0062] When the first accommodating cavity 21 and the second accommodating cavity 31 correspond to each other along the axial direction of the piston 10, during the assembly process, the connecting end 41 of the sliding vane 40 can be accurately aligned with and embedded in the first accommodating cavity 21 and the second accommodating cavity 31, so as to realize the precise connection between the sliding vane 40 and the piston 10 and improve the connection reliability between the sliding vane 40 and the piston 10. After the connecting end 41 of the sliding vane 40 is embedded in the first accommodating cavity 21 and the second accommodating cavity 31, it can form a uniform and stable support in the axial direction of the piston 10, which can effectively reduce the shaking and offset of the sliding vane 40 during the movement of the piston 10 and enhance the connection stability between the sliding vane 40 and the piston 10.

[0063] The first piston body and the second piston body are symmetrically arranged along the axial direction of the piston, making the overall structure of the piston symmetric. This symmetry can ensure that the piston is uniformly stressed during the movement process, reduce vibration and noise caused by asymmetric structure, and improve the movement smoothness of the piston. The sliding vane 40 is symmetrically arranged along the axial direction of the piston, so that the sliding vane can be evenly distributed and stressed on both sides in the axial direction of the piston. This symmetry can make the contact between the sliding vane and the inner wall of the cylinder more uniform during the movement of the piston, reduce wear and improve the sealing performance.

[0064] Optionally, as shown in Figure 4 the first piston body 20 is provided with a first limiting portion 22, the connecting end 41 is provided with a first limiting and mating portion 411, and the first limiting portion 22 cooperates with the first limiting and mating portion 411 to limit the movement of the connecting end 41 relative to the first piston body 20 along the axial direction of the piston 10; the second piston body 30 is provided with a second limiting portion 32, the connecting end 41 is provided with a second limiting and mating portion 413, and the second limiting portion 32 cooperates with the second limiting and mating portion 413 to limit the movement of the connecting end 41 relative to the second piston body 30 along the axial direction of the piston 10.

[0065] By the cooperation of the first limiting portion 22 and the first limiting mating portion 411, and the cooperation of the second limiting portion 32 and the second limiting mating portion 413, the movement of the connecting end 41 of the sliding vane 40 along the axial direction of the piston 10 relative to the first piston body 20 and the second piston body 30 is respectively restricted, so that the axial displacement of the sliding vane 40 during the movement of the piston 10 can be effectively avoided. This makes the connection between the sliding vane 40 and the piston 10 more stable and reliable, reducing the risk of the sliding vane 40 detaching from the piston 10. In addition, during the assembly process, the mutual cooperation of the first limiting portion 22 and the first limiting mating portion 411, and the second limiting portion 32 and the second limiting mating portion 413 can also provide clear positioning and guidance for the connecting end 41 of the sliding vane 40, enabling the sliding vane 40 to be accurately installed on the piston 10, and the position in the axial direction of the piston 10 to be precisely controlled.

[0066] Optionally, in combination Figure 4 , Figure 9 and Figure 12 As shown, the first limiting portion 22 includes a first limiting groove 221, the first limiting mating portion 411 is a first limiting boss 412, and the first limiting boss 412 is embedded in the first limiting groove 221; the second limiting portion 32 includes a second limiting groove 321, the second limiting mating portion 413 is a second limiting boss 414, and the second limiting boss 414 is embedded in the second limiting groove 321.

[0067] By embedding the first limiting boss 412 into the first limiting groove 221 and the second limiting boss 414 into the second limiting groove 321, the connecting end 41 of the sliding vane 40 is limited from both sides in the axial direction of the piston 10, so that the position of the sliding vane 40 in the axial direction of the piston 10 is precisely fixed. The matching manner between the first limiting groove 221 and the first limiting boss 412, and the second limiting groove 321 and the second limiting boss 414 provides clear and precise positioning for the assembly between the connecting end 41 of the sliding vane 40 and the piston 10. During assembly, only need to align the first limiting boss 412 with the first limiting groove 221 and the second limiting boss 414 with the second limiting groove 321 and then embed them, the operation is simple and convenient, which can effectively improve the assembly efficiency and reduce the problems caused by the deviation of the assembly position.

[0068] Optionally, a radial matching gap is provided between the first limiting boss 412 and the first limiting groove 221 to enable the first limiting boss 412 to rotate relative to the first limiting groove 221; a radial matching gap is provided between the second limiting boss 414 and the second limiting groove 321 to enable the second limiting boss 414 to rotate relative to the second limiting groove 321.

[0069] The radial mating clearance provides a certain degree of rotational freedom for the connecting end 41 of the sliding vane 40. When embedding the connecting end 41 of the sliding vane 40 into the first receiving cavity 21 and the second receiving cavity 31, the sliding vane 40 can be adjusted and positioned more easily, reducing the difficulty and complexity of assembly and improving the assembly efficiency. During the operation of the compressor, the sliding vane 40 needs to closely fit the outer wall surface 13 of the piston 10 to achieve a good sealing effect. The radial mating clearance allows the connecting end 41 to rotate relative to the limiting receiving space 11 within a certain range, enabling the piston 10 to swing around the connecting end 41 of the sliding vane 40. This helps the sliding vane 40 better adapt to the movement trajectory of the piston 10, improves the sealing performance, and thus ensures the normal operation and working efficiency of the compressor.

[0070] Optionally, as shown in Figure 4 and Figure 12 , the first receiving cavity 21 and the second receiving cavity 31 are arranged oppositely along the axial direction of the piston 10. A first limiting groove 221 is formed at one end of the first receiving cavity 21 away from the second piston body 30, and a second limiting groove 321 is formed at one end of the second receiving cavity 31 away from the first piston body 20; the connecting end 41 extends along the axial direction of the piston 10. A first limiting boss 412 is formed at the first end of the connecting end 41 along the axial direction of the piston 10, and a second limiting boss 414 is formed at the second end of the connecting end 41 along the axial direction of the piston 10.

[0071] When the connecting end 41 is embedded into the limiting receiving space 11 jointly formed by the first receiving cavity 21 and the second receiving cavity 31, the first limiting boss 412 cooperates with the first limiting groove 221, and the second limiting boss 414 cooperates with the second limiting groove 321, thereby realizing the articulated cooperation between the connecting end 41 and the limiting receiving space 11. This forms a movable connection mode similar to a door hinge between the connecting end 41 and the limiting receiving space 11, and the limiting receiving space 11 forms a hinge hole, providing a rotational freedom for the connecting end 41 of the sliding vane 40.

[0072] Optionally, a mating clearance is provided between the connecting end 41 and the inner wall surface of the limiting receiving space 11 to enable the connecting end 41 to rotate within the limiting receiving space 11, so that the piston 10 can swing relative to the sliding vane 40; wherein, the mating clearance between the connecting end 41 and the inner wall surface of the limiting receiving space 11 is greater than or equal to 0.03 mm and less than or equal to 0.06 mm.

[0073] During the operation of the compressor, the piston 10 swings around the connecting end 41 of the vane 40, which can reduce the rotation of the piston 10 and avoid excessive energy consumption. A matching clearance is provided between the connecting end 41 and the inner wall surface of the limiting accommodation space 11, which can provide flow space for the lubricating oil, help to achieve lubrication of the piston 10 and the vane 40, reduce the friction loss between the two, and extend the service life of the compressor. At the same time, the matching clearance can also provide space for the connecting end 41 to provide rotational freedom. Since the connecting end 41 of the vane of the embodiment of the present disclosure is embedded in the limiting accommodation space 11 of the piston, the connecting end 41 is limited at both ends along the axial direction of the piston, which can prevent the vane from detaching from the piston. Therefore, the matching clearance between the connecting end and the inner wall surface of the limiting accommodation space can be appropriately increased, which can achieve a better lubrication effect and prevent the vane from detaching.

[0074] When the fitting clearance between the connection end 41 and the inner wall surface of the limit accommodating space 11 is greater than or equal to 0.03 mm, it can provide sufficient flow space for the lubricating oil, thereby improving the lubrication effect between the connection end 41 and the inner wall surface of the limit accommodating space 11. The lubricating oil can form an effective lubricating film between the connection end 41 and the inner wall surface of the limit accommodating space 11, thereby reducing the friction coefficient between the two and reducing the heat and wear generated by friction. The connection end 41 can rotate in the limit accommodating space 11, thereby allowing the piston 10 to swing relative to the vane 40 within a certain range. This enables the piston 10 to better adapt to the movement trajectory of the vane 40, reduce the self-rotation of the piston 10, avoid excessive energy consumption due to excessive self-rotation of the piston 10, and improve the operating efficiency of the compressor.

[0075] When the fitting clearance between the connecting end 41 and the inner wall surface of the limiting accommodating space 11 is less than or equal to 0.06 mm, it can avoid the situation where the sliding vane 40 shakes excessively or separates from the piston 10 during movement due to excessive fitting clearance, thereby improving the connection stability between the sliding vane 40 and the piston 10, thereby improving the reliability of the compressor during high-speed operation.

[0076] The embodiment of the present disclosure defines that the fitting clearance between the connection end 41 and the inner wall surface of the position-limiting accommodation space 11 is greater than or equal to 0.03 mm and less than or equal to 0.06 mm. Within this fitting clearance range, the connection stability, lubricity and movement flexibility between the sliding vane 40 and the piston 10 can be effectively balanced, thereby improving the operating stability and reliability of the compressor. It is understood that the fitting clearance between the connection end 41 and the inner wall surface of the position-limiting accommodation space 11 can be 0.03 mm, 0.04 mm, 0.05 mm or 0.06 mm.

[0077] Optionally, combined Figure 4 and Figures 9 - 12As shown, a first opening 23 is provided on the outer peripheral wall of the first piston body 20, and the first opening 23 communicates with the first accommodation cavity 21; a second opening 33 is provided on the outer peripheral wall of the second piston body 30, and the second opening 33 communicates with the second accommodation cavity 31. The first opening 23 and the second opening 33 are arranged opposite to each other along the axial direction of the piston 10, and the first opening 23 and the second opening 33 are correspondingly communicated to enclose an assembly port 12. The sliding vane 40 further includes a transition section 42, and the transition section 42 is arranged at one end of the connecting end 41 away from the piston 10. The transition section 42 is connected to the connecting end 41, and the transition section 42 passes through the assembly port 12.

[0078] By respectively providing the first opening 23 and the second opening 33 on the outer peripheral walls of the first piston body 20 and the second piston body 30, and making the first opening 23 and the second opening 33 opposite and communicating with each other along the axial direction of the piston 10 to enclose the assembly port 12, a passing channel is provided for the transition section 42 of the sliding vane 40. When one end of the connecting end 41 is predetermined to be located in the first accommodation cavity 21 of the first piston body 20, one end of the transition section 42 is correspondingly embedded in the first opening 23. The second piston body 30 abuts against the first piston body 20, the other end of the connecting end 41 is located in the second accommodation cavity 31, and the other end of the transition section 42 is correspondingly embedded in the second opening 33, thereby improving the convenience and accuracy of assembly. The transition section 42 of the sliding vane 40 passes through the assembly port 12, so that the sliding vane 40 is not only connected to the piston 10 through the embedding of the connecting end 41, but also the connection strength between the sliding vane 40 and the piston 10 is further enhanced through the passing of the transition section 42.

[0079] Optionally, the size of the transition section 42 is smaller than the size of the assembly port 12, so that there is a clearance between the transition section 42 and the assembly port 12.

[0080] The existence of the clearance provides an adjustment space for the sliding vane 40 during the installation of the transition section 42, which helps to ensure the accurate installation and positioning of the sliding vane 40. The clearance provides an appropriate degree of freedom of movement for the sliding vane 40, enabling the sliding vane 40 to be adjusted more flexibly with the movement of the piston 10. The existence of the clearance also provides a space for the flow of lubricating oil, which helps to form an effective lubricating film between the transition section 42 of the sliding vane 40 and the assembly port 12, reducing the friction coefficient. During the operation of the compressor, the piston 10 will perform reciprocating motion and may be affected by lateral forces and thermal expansion and undergo certain deformation. The clearance allows the transition section 42 to have a certain degree of movement within the assembly port 12, so that the sliding vane 40 can better adapt to the movement and deformation of the piston 10, reducing stress concentration and wear caused by movement or deformation, and extending the service life of the sliding vane 40 and the piston 10.

[0081] Optionally, the width of the transition section 42 is smaller than the width of the connecting end 41, and the size of the assembly port 12 is smaller than the inner diameter of the limit accommodation space 11.

[0082] The width of the transition section 42 is smaller than that of the connection end 41, resulting in a width difference between the transition section 42 and the connection end 41. The connection end 41 with a relatively large size can be stably embedded in the limit accommodation space 11 to achieve an effective limiting function and realize a reliable connection between the sliding vane 40 and the piston 10. At the same time, the transition section 42 can avoid interference with the assembly port 12 during movement. During the movement of the piston 10 and the sliding vane 40, the transition section 42 can move flexibly within the assembly port 12 and will not collide or jam with the assembly port 12 due to its excessive size, ensuring the smooth movement of the sliding vane 40 and the piston 10. When the connection end 41 extends along the axial direction of the piston 10 in a cylindrical shape, the width of the transition section 42 is smaller than the diameter of the connection end 41.

[0083] Optionally, in combination Figures 10 - 12 As shown, the first piston body 20 and the second piston body 30 are symmetrically arranged along the axial direction of the piston, and the sliding vane is symmetrically arranged along the axial direction of the piston.

[0084] The first piston body 20 and the second piston body 30 being symmetrically arranged along the axial direction of the piston means that the overall structures of the first piston body 20 and the second piston body 30 are symmetrically arranged along the axial direction of the piston. For example, the first accommodation cavity 21 provided in the first piston body 20 and the second accommodation cavity 31 provided in the second piston body 30 are symmetrically arranged along the axial direction of the piston, and the first opening and the second opening are symmetrically arranged along the axial direction of the piston. The sliding vane 40 being symmetrically arranged along the axial direction of the piston means that the connection end, the transition section, and the sliding vane body are all symmetrically arranged along the axial direction of the piston.

[0085] Optionally, in combination Figure 6 As shown, the pump body assembly for a compressor further includes a cylinder 60. The cylinder 60 is provided with a working cavity 61 and a sliding vane groove 62 that are connected and communicate with each other. The piston 10 is arranged in the working cavity 61 and can move within the working cavity 61. The sliding vane 40 is slidably arranged in the sliding vane groove 62. Along the axial direction of the piston, the cross-sectional shape of the connection end 41 of the sliding vane is a first arc 415, and the cross-sectional shape of the limit accommodation space 11 is a second arc 111. The centers of the first arc 415 and the second arc 112 coincide. Among them, the half-width d of the assembly port 12 along the circumferential direction of the piston 10, the width t of the transition section 42 along the circumferential direction of the piston 10, the eccentricity e of the piston 10, the distance L between the center 112 of the second arc and the center 101 of the piston along the radial direction of the cylinder, the length h of the assembly port 12 along the radial direction of the piston 10, and the radius r of the second arc 111 satisfy the following formula:

[0086]

[0087] When the compressor is running, the piston 10 swings in the working chamber of the cylinder. When the piston moves to 90° in the working chamber, it is at the top dead center in the working chamber. When the piston moves to 270° in the working chamber, it is at the bottom dead center in the working chamber. When the piston 10 is at the top dead center or the bottom dead center, the swing angle of the piston 10 relative to the sliding vane is the largest. At this time, the side wall of the mounting port of the piston 10 and the transition section 42 of the sliding vane 40 are at the limit point where interference occurs. If the clearance between the side wall of the mounting port of the piston 10 and the transition section 42 of the sliding vane 40 is greater than 0 when at the top dead center or the bottom dead center, that is, the piston does not interfere with the sliding vane when at the top dead center or the bottom dead center, it can be ensured that the piston 10 will not interfere with the sliding vane 40 during the entire swing stroke.

[0088] Along the axial direction of the piston 10, both the connecting end 41 and the cross-section of the limit accommodating space 11 are designed with arcs and their centers coincide, so that the connecting end 41 can better adapt to the shape of the limit accommodating space 11, improve the assembly accuracy, and can also form a tighter seal between the piston 10 and the sliding vane 40.

[0089] Since the top dead center and the bottom dead center are two symmetrical positions, the present application takes the relationship between various parameters when the piston is at the top dead center as an example to illustrate the solution. Combining Figure 5 and Figure 6 as shown, taking the example when the piston 10 runs to the top dead center position of 90°. At this time, the clearance S between the side wall of the mounting port of the piston 10 and the transition section 42 of the sliding vane 40 is greater than 0. The clearance S between the side wall of the mounting port of the piston 10 and the transition section 42 of the sliding vane 40 is equal to the difference of the auxiliary line segment in the figure. S>0, that is Combining Figure 5 and Figure 6 the auxiliary lines in can be calculated to obtain l3 = h×cosβ, where the angles α, β, γ are the auxiliary angles as shown in Figure 5 and Figure 6 .

[0090] Therefore, the radius r of the second arc 111, the length h of the assembly port 12 along the radial direction of the piston 10, and the width t of the transition section 42 along the circumferential direction of the piston 10 satisfy the following formula:

[0091]

[0092] When moving to the 90° or 270° position of the working chamber within the working chamber, the schematic line segment of the eccentricity e of the piston 10 is exactly perpendicular to the schematic line segment of the distance L along the radial direction of the cylinder between the center 112 of the second arc and the center 101 of the piston. Combining with the trigonometric function relationships among the schematic line segments corresponding to the half-width d of the assembly port 12 along the circumferential direction of the piston 10, the width t of the transition section 42 along the circumferential direction of the piston 10, the length h of the assembly port 12 along the radial direction of the piston 10, and the radius r of the second arc 111, it can be obtained that:

[0093]

[0094] Thus, the formula is obtained:

[0095]

[0096] The above formula provides a verification method for detecting whether the requirements of production are met between the sliding vane 40 and the piston 10. When each parameter satisfies the relationship of the above formula, it can ensure that the piston 10 does not interfere with the transition section 42 of the sliding vane 40 during the swinging process. The left side of the formula involves multiple parameters, including the half-width d of the assembly port 12 along the circumferential direction of the piston 10, the width t of the transition section 42 along the circumferential direction of the piston 10, the eccentricity e of the piston 10, the distance L along the radial direction of the cylinder between the center 112 of the second arc and the center 101 of the piston, and the length h of the assembly port 12 along the radial direction of the piston 10. The right side of the formula involves multiple parameters, including the radius r of the second arc 111, the half-width d of the assembly port 12 along the circumferential direction of the piston 10, the eccentricity e of the piston 10, and the distance L along the radial direction of the cylinder between the center 112 of the second arc and the center 101 of the piston. From the above derivation process, it can be seen that through the condition that the left side of the formula is greater than the right side of the formula, the gap S between the side wall of the installation port of the piston 10 and the transition section 42 of the sliding vane 40 can be made greater than 0, so as to ensure that during the movement of the piston 10 and the sliding vane 40, the transition section 42 will not interfere with the assembly port 12. In this way, under complex working conditions such as the swinging of the piston 10, the transition section 42 can move smoothly within the assembly port 12 without jamming or collision phenomena, thus ensuring the normal operation of the compressor. At the same time, through the precise cooperation of the eccentricity e of the piston 10 and the distance L along the radial direction of the cylinder between the center 112 of the second arc and the center 101 of the piston, the piston 10 will not collide with the inner wall of the cylinder or other components due to excessive deviation during the movement process, which can improve the movement stability of the piston 10.

[0097] Optionally, when the piston is at the top dead center or bottom dead center within the working chamber, the distance along the radial direction of the cylinder between the end of the sliding vane body facing the piston and the center of the limit accommodation space is the first distance, and the distance along the radial direction of the cylinder between the notch edge of the installation port and the center of the limit accommodation space is the second distance, and the first distance is greater than the second distance.

[0098] The first distance is asFigure 6 As shown in H, the second distance is as Figure 6 shown in X.

[0099] The connecting end of the sliding vane is embedded in the mounting hole of the piston. The end of the sliding vane body faces the piston, and the sliding vane body moves along the sliding vane groove of the cylinder outside the piston. When the piston is at the top dead center or bottom dead center in the working chamber, the distance along the radial direction of the cylinder between the end of the sliding vane body facing the piston and the center of the limiting accommodation space is the first distance, and the distance along the radial direction of the cylinder between the notch edge of the mounting port and the center of the limiting accommodation space is the second distance. When the first distance is greater than the second distance, a gap is formed between the end of the sliding vane body facing the piston and the notch edge of the mounting port, so as to avoid contact, collision or interference phenomenon between the sliding vane body and the notch edge of the mounting port of the piston during the movement process.

[0100] Optionally, the sliding vane 40 further includes a sliding vane body 43. The sliding vane body 43 is arranged at one end of the transition section 42 away from the connecting end 41. The sliding vane body 43 is connected to the transition section 42, and the dimension of the sliding vane body 43 along the axial direction of the piston 10 is greater than the dimension of the assembly port 12 along the axial direction of the piston 10.

[0101] The transition section 42 passes through the assembly port 12. The dimension of the sliding vane body 43 along the axial direction of the piston 10 is greater than the dimension of the assembly port 12, and at the same time, the dimension of the sliding vane body 43 along the axial direction of the piston 10 is also greater than the dimension of the transition section 42 along the axial direction of the piston 10. The dimension of the sliding vane body 43 along the axial direction of the piston 10 is greater than the dimension of the assembly port 12 along the axial direction of the piston 10. In this way, the sliding vane body 43 can effectively cover the assembly port 12 during the movement of the piston 10, preventing the gas on both sides of the sliding vane 40 in the working chamber from flowing through the assembly port 12. When the piston 10 drives the sliding vane 40 to move, the sliding vane body 43 can form a good sealing surface on the outer wall surface 13 of the piston 10, improving the volumetric efficiency of the compressor. The dimension of the sliding vane body 43 along the axial direction of the piston 10 being greater than the dimension of the transition section 42 along the axial direction of the piston 10 provides better structural stability for the sliding vane 40. During the movement of the piston 10, the sliding vane body 43 can withstand greater gas pressure, reduce the deformation and wear of the sliding vane 40, and extend the service life of the sliding vane 40.

[0102] Optionally, in combination with Figure 9As shown, the first limiting boss 412 and the second limiting boss 414 are respectively provided at both ends of the connecting end 41 along the axial direction of the piston 10, and the first limiting boss 412 and the second limiting boss 414 respectively extend towards both sides of the connecting end 41 along the axial direction of the piston 10. The sliding vane body 43 includes a first end and a second end along the axial direction of the piston 10, and the transition section 42 includes a first end face and a second end face along the axial direction of the piston 10. A first limiting space 24 is formed between the first end of the sliding vane body 43, the first end face of the transition section 42 and the first limiting boss 412, and the outer groove wall of the first limiting groove 221 is embedded in the first limiting space 24; a second limiting space 34 is formed between the second end of the sliding vane body 43, the second end face of the transition section 42 and the second limiting boss 414, and the outer groove wall of the second limiting groove 321 is embedded in the second limiting space 34.

[0103] The outer groove wall of the first limiting groove 221 is embedded in the first limiting space 24, and the outer groove wall of the second limiting groove 321 is embedded in the second limiting space 34, which makes the connection between the sliding vane 40 and the piston 10 tighter and more firm. It can prevent the sliding vane 40 from loosening during the movement of the piston 10. At the same time, it can also stably limit between the first piston body 20 and the second piston body 30 of the piston 10 through the sliding vane 40, restricting the relative movement of the first piston body 20 and the second piston body 30 in the circumferential direction of the piston 10, and effectively preventing the dislocation of the first piston body 20 and the second piston body 30.

[0104] Optionally, combined Figure 12 and Figure 16 As shown, the dimension of the connecting end 41 along the axial direction of the piston 10 is greater than the dimension of the transition section 42 along the axial direction of the piston 10, and the dimension of the sliding vane body 43 along the axial direction of the piston 10 is greater than the dimension of the transition section 42 along the axial direction of the piston 10, so as to form a step difference between the connecting end 41, the transition section 42 and the sliding vane body 43 in the axial direction of the piston 10.

[0105] The stepped step difference formed between the connecting end 41, the transition section 42 and the sliding vane body 43 in the axial direction of the piston 10 can effectively improve the limiting stability of the connection between the sliding vane 40 and the piston 10.

[0106] Optionally, combined Figure 8 、 Figure 12 and Figure 16 As shown, the sliding vane 40 further includes a sealing portion 44. The sealing portion 44 is provided at one end of the sliding vane body 43 facing the piston 10. The sealing portion 44 protrudes in an arc shape towards the piston 10, and the sealing portion 44 abuts against the outer wall surface 13 of the piston 10.

[0107] The sealing portion 44 is provided at one end of the sliding vane body 43 facing the piston 10. The sealing portion 44 protrudes in an arc shape towards the piston 10, enabling the seal to always closely fit the outer wall surface 13 of the piston 10, effectively improving the sealing performance between the sliding vane 40 and the piston 10, thereby enhancing the compression efficiency of the compressor.

[0108] Optionally, as shown in Figure 7 、 Figure 15 and Figure 16 , the dimension of the sliding vane body 43 along the axial direction of the piston 10 is greater than the dimension of the transition portion along the axial direction of the piston 10. The sealing portion 44 is provided at both ends of the transition portion along the axial direction of the piston 10, and the end face of the sealing portion 44 along the axial direction of the piston 10 is flush with the end face of the sliding vane body 43 along the axial direction of the piston 10.

[0109] The dimension of the sliding vane body 43 along the axial direction of the piston 10 is greater than that of the transition portion. The sealing portion 44 is provided at both ends of the transition portion and the end faces are flush with the end face of the sliding vane body 43, which can fill the gap between the transition portion and the piston 10 to form a more complete sealing surface. The sliding vane body 43 has a larger dimension and the transition portion has a smaller dimension. The sealing portion 44 is flush with the end face of the sliding vane body 43, which can also enhance the overall structural stability of the sliding vane 40.

[0110] Optionally, as shown in Figure 13 and Figure 14 , the dimension of the first accommodation cavity 21 along the axial direction of the piston is smaller than the dimension of the first piston body 20 along the axial direction of the piston.

[0111] The dimension of the first accommodation cavity 21 along the axial direction of the piston is as shown by k1 in Figure 14 . The dimension of the first piston body 20 along the axial direction of the piston is as shown by b in Figure 14 .

[0112] This enables the first accommodation cavity 21 to be completely located inside the first piston body 20, which can improve the compactness of the structure of the first piston body and avoid affecting the cooperative work between the first piston body 20 and other components. At the same time, this can also prevent the first accommodation cavity 21 from penetrating the end face of the first piston body 20 along the axial direction of the piston, thereby maintaining the integrity and sealing performance of the end face of the first piston body 20.

[0113] Optionally, the dimension of the second accommodation cavity 31 along the axial direction of the piston is smaller than the dimension of the second piston body 30 along the axial direction of the piston.

[0114] This enables the second accommodation cavity 31 to be completely located inside the second piston body 30, which can improve the compactness of the structure of the first piston body and avoid affecting the cooperative work between the second piston body 30 and other components. At the same time, this can also prevent the second accommodation cavity 31 from penetrating the end face of the second piston body 30 along the axial direction of the piston, thereby maintaining the integrity and sealing performance of the end face of the second piston body 30.

[0115] Optionally, the ratio of the dimension of the first opening 23 along the piston axis to the dimension of the first receiving cavity 21 along the piston axis is greater than or equal to 0.5 and less than 1; and / or, the ratio of the dimension of the second opening 33 along the piston axis to the dimension of the second receiving cavity 31 along the piston axis is greater than or equal to 0.5 and less than 1.

[0116] The dimension of the first opening 23 along the piston axis is as Figure 14 shown by k2 in the figure. The dimension of the first receiving cavity 21 along the piston axis is as Figure 14 shown by k1 in the figure.

[0117] The first piston body 20 and the second piston body 30 are symmetrically arranged along the axis of the piston. Therefore, in the axial direction of the piston, the shapes and dimensions of the first piston body 20 and the second piston body 30 are mirror-symmetrical. Hereinafter, the ratio range of the dimension of the first opening 23 along the piston axis to the dimension of the first receiving cavity 21 along the piston axis will be taken as an example for illustration.

[0118] When the ratio of the dimension of the first opening 23 along the axis of the piston 10 to the dimension of the first receiving cavity 21 along the axis of the piston 10 is greater than or equal to 0.5, a larger accommodation space can be provided for the transition portion, which helps the transition section 42 of the sliding vane 40 to smoothly pass through the first opening 23, reducing the assembly difficulty and improving the flexibility and efficiency of assembly.

[0119] When the ratio of the dimension of the first opening 23 along the axis of the piston 10 to the dimension of the first receiving cavity 21 along the axis of the piston 10 is less than 1, a height difference can exist between the first receiving cavity 21 and the first opening 23. The piston 10 wall surface corresponding to this height difference can limit the connection end 41, effectively preventing the connection end 41 from detaching from the first receiving cavity 21. This height difference also provides space for the setting of the first limiting groove 221.

[0120] The embodiment of the present disclosure defines that the ratio of the dimension of the first opening 23 along the axis of the piston 10 to the dimension of the first receiving cavity 21 along the axis of the piston 10 is greater than or equal to 0.5 and less than 1, which can balance the assembly space of the transition section 42 and the limitation of the connection end 41 in the setting of the first opening 23 and the first receiving cavity 21. It can be understood that the ratio of the dimension of the first opening 23 along the axis of the piston 10 to the dimension of the first receiving cavity 21 along the axis of the piston 10 can be 0.5, 0.6, 0.7, 0.8, 0.9 or 0.95.

[0121] The ratio of the dimension of the second opening 33 along the axial direction of the piston to the dimension of the second receiving cavity 31 along the axial direction of the piston is greater than or equal to 0.5 and less than 1, which can achieve a similar effect to that between the first opening and the first receiving cavity, and can balance the assembly space of the second opening 33 and the second opening 33 provided in the transition section 42 and the limit of the connection end 41. The ratio of the dimension of the second opening 33 along the axial direction of the piston 10 to the dimension of the second receiving cavity 31 along the axial direction of the piston 10 can be 0.5, 0.6, 0.7, 0.8, 0.9 or 0.95.

[0122] Optionally, the dimension of the connection end 41 along the axial direction of the piston 10 is greater than the dimension of the transition section 42 along the axial direction of the piston 10.

[0123] The dimension of the connection end 41 along the axial direction of the piston 10 is as Figure 16 shown as b1 in Figure 16 . The dimension of the transition section 42 along the axial direction of the piston 10 is as

[0124] shown as b2 in

[0125] When the dimension of the connection end 41 along the axial direction of the piston 10 is greater than the dimension of the transition section 42 along the axial direction of the piston 10, a stepped structure with a height difference is formed between the connection end 41 and the transition section 42, so that a better limiting effect can be formed between the sliding vane 40 and the limiting receiving space 11 of the piston 10. This makes the connection between the sliding vane 40 and the piston 10 more firm and can prevent the sliding vane 40 from loosening from the piston 10. In addition, this stepped structure makes the positioning of the sliding vane 40 more accurate in the axial direction of the piston 10, facilitating the alignment and installation of the sliding vane 40 during assembly and improving the assembly efficiency.

[0126] Optionally, the ratio of the dimension of the connection end 41 along the axial direction of the piston 10 to the dimension of the sliding vane body 43 along the axial direction of the piston 10 is greater than or equal to 0.5 and less than or equal to 1. Figure 16 The dimension of the connection end 41 along the axial direction of the piston 10 is as Figure 16 shown as b1 in

[0127] When the ratio of the dimension of the connection end 41 along the axial direction of the piston 10 to the dimension of the sliding vane body 43 along the axial direction of the piston 10 is greater than or equal to 0.5, the dimension of the connection end 41 along the axial direction of the piston 10 is large enough, so that the connection part between the sliding vane 40 and the piston 10 has sufficient strength. This enables the sliding vane 40 to withstand greater radial and axial forces, improving the reliability and stability of the connection between the sliding vane 40 and the piston 10.

[0128] When the ratio of the dimension of the connection end 41 along the axial direction of the piston 10 to the dimension of the sliding vane body 43 along the axial direction of the piston 10 is less than or equal to 1, the dimension of the connection end 41 along the axial direction of the piston 10 is less than or equal to the dimension of the sliding vane body 43 along the axial direction of the piston 10, maintaining the coordination of the overall structure of the sliding vane 40. This can avoid unnecessary weight increase and space occupation caused by the oversize dimension of the connection end 41, and at the same time enable the smooth assembly and movement of the sliding vane 40 within the piston 10.

[0129] In the embodiment of the present disclosure, it is defined that the ratio of the dimension of the connection end 41 along the axial direction of the piston 10 to the dimension of the sliding vane body 43 along the axial direction of the piston 10 is greater than or equal to 0.5 and less than or equal to 1, which can ensure the connection strength between the sliding vane 40 and the piston 10 while maintaining the coordination of the overall structure of the sliding vane 40. It can be understood that the ratio of the dimension of the connection end 41 along the axial direction of the piston 10 to the dimension of the sliding vane body 43 along the axial direction of the piston 10 can be 0.5, 0.6, 0.7, 0.8, 0.9 or 1.

[0130] The embodiment of the present disclosure provides a compressor, including a pump body assembly for a compressor as described in any one of the above-mentioned disclosed embodiments.

[0131] The compressor provided by the embodiment of the present disclosure, because it includes the pump body assembly for a compressor as described in any one of the above-mentioned disclosed embodiments, thus has all the beneficial effects of the pump body assembly for a compressor as described in any one of the above-mentioned disclosed embodiments, which will not be elaborated herein.

[0132] The above description and the drawings fully illustrate the embodiments of the present disclosure so that those skilled in the art can practice them. Other embodiments may include structural and other changes. Embodiments represent only possible variations. Unless explicitly required, individual components and functions are optional, and the order of operations may vary. Parts and features of some embodiments may be included in or substituted for parts and features of other embodiments. The embodiments of the present disclosure are not limited to the structures already described and shown in the drawings, and various modifications and changes can be made without departing from its scope. The scope of the present disclosure is limited only by the appended claims.

Claims

1. A pump body assembly for a compressor, characterized in that, Comprising: A piston, including a first piston body and a second piston body which are separately arranged and opposite to each other along the axial direction of the piston. The first piston body is provided with a first accommodation cavity, and the second piston body is provided with a second accommodation cavity. The first piston body and the second piston body are abutted against each other, and the first accommodation cavity and the second accommodation cavity jointly form a limit accommodation space; A sliding vane, including a connection end, and the connection end is embedded in the limit accommodation space so that the sliding vane is connected to the piston.

2. The pump body assembly for a compressor according to claim 1, wherein The first piston body is provided with a first limit portion, and the connection end is provided with a first limit cooperation portion. The first limit portion and the first limit cooperation portion cooperate with each other to limit the movement of the connection end relative to the first piston body along the axial direction of the piston; The second piston body is provided with a second limit portion, and the connection end is provided with a second limit cooperation portion. The second limit portion and the second limit cooperation portion cooperate with each other to limit the movement of the connection end relative to the second piston body along the axial direction of the piston.

3. The pump body assembly for a compressor according to claim 2, wherein The first limit portion includes a first limit groove, and the first limit cooperation portion is a first limit boss, and the first limit boss is embedded in the first limit groove; The second limit portion includes a second limit groove, and the second limit cooperation portion is a second limit boss, and the second limit boss is embedded in the second limit groove.

4. The pump body assembly for a compressor according to any one of claims 1 to 3, wherein A fitting gap is provided between the connection end and the inner wall surface of the limit accommodation space, so that the connection end can rotate in the limit accommodation space, thereby enabling the piston to swing relative to the sliding vane; Wherein, the fitting gap between the connection end and the inner wall surface of the limit accommodation space is greater than or equal to 0.03 mm and less than or equal to 0.06 mm.

5. The pump body assembly for a compressor according to any one of claims 1 to 3, wherein The outer peripheral wall of the first piston body is provided with a first opening, and the first opening is communicated with the limit accommodation space; The outer peripheral wall of the second piston body is provided with a second opening, and the second opening is communicated with the limit accommodation space. The first opening and the second opening are arranged opposite to each other along the axial direction of the piston, and the first opening and the second opening are correspondingly communicated to form an assembly opening; The sliding vane further includes a transition section, and the transition section is arranged at one end of the connection end far away from the piston. The transition section is connected to the connection end, and the transition section passes through the assembly opening.

6. The pump body assembly for a compressor according to claim 5, characterized in that, Further comprising: A cylinder, provided with a working cavity and a sliding vane groove which are communicated with each other. The piston is arranged in the working cavity and can move in the working cavity. The sliding vane is slidably arranged in the sliding vane groove. Along the axial direction of the piston, the cross-sectional shape of the connection end of the sliding vane is a first arc, and the cross-sectional shape of the limit accommodation space is a second arc. The centers of the first arc and the second arc coincide. Wherein, the half-width d of the assembly opening along the circumferential direction of the piston, the width t of the transition section along the circumferential direction of the piston, the eccentricity e of the piston, the distance L between the center of the second arc and the center of the piston along the radial direction of the cylinder, the length h of the assembly opening along the radial direction of the piston, and the radius r of the second arc satisfy the following formula:

7. The pump body assembly for a compressor according to claim 5, wherein, The sliding vane further includes: A sliding vane main body, arranged at one end of the transition section far away from the connection end. The sliding vane main body is connected to the transition section, and the dimension of the sliding vane main body along the axial direction of the piston is greater than the dimension of the assembly opening along the axial direction of the piston.

8. The pump body assembly for a compressor according to claim 7, characterized in that, The sliding vane further includes: The sealing part is arranged at one end of the sliding vane body facing the piston. The sealing part protrudes arcuately towards the piston, and the sealing part abuts against the outer wall surface of the piston.

9. The pump body assembly for a compressor according to claim 7, wherein the dimension of the first accommodation cavity along the axial direction of the piston is smaller than the dimension of the first piston body along the axial direction of the piston; and / or, the dimension of the second accommodation cavity along the axial direction of the piston is smaller than the dimension of the second piston body along the axial direction of the piston; and / or, the ratio of the dimension of the first opening along the axial direction of the piston to the dimension of the first accommodation cavity along the axial direction of the piston is greater than or equal to 0.5 and less than 1; and / or, the ratio of the dimension of the second opening along the axial direction of the piston to the dimension of the second accommodation cavity along the axial direction of the piston is greater than or equal to 0.5 and less than 1; and / or, the dimension of the connection end along the axial direction of the piston is greater than the dimension of the transition section along the axial direction of the piston; and / or, the ratio between the dimension of the connection end along the axial direction of the piston and the dimension of the sliding vane body along the axial direction of the piston is greater than or equal to 0.

5.

10. A compressor, characterized in that, It includes the pump body assembly for a compressor according to any one of claims 1 to 9.

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