Rotary compressor pump assembly, rotary compressor and refrigeration equipment

Abstract

The present invention discloses a pump body assembly of a rotary compressor, a rotary compressor, and a refrigeration device. The pump body assembly of the rotary compressor includes a cylinder, an upper flange, a lower flange, and a vane. The cylinder has a working chamber and a vane groove connected to the working chamber. The upper flange and the lower flange are sealed and arranged on the upper and lower sides of the cylinder, respectively. The vane is movably arranged in the vane groove. The upper flange and the lower flange are each provided with a flange groove. The flange groove includes a pressure-bearing side and a non-pressure-bearing side. A tail restraint connected to the tail of the vane is provided in the flange groove. The side of the tail restraint close to the pressure-bearing side forms an angle with the pressure-bearing side, and the angle gradually decreases inward from the entrance of the flange groove. The cooperation between the tail restraint and the vane groove increases the constraint on the tail of the vane, thereby reducing the tilt of the vane head, ensuring the thickness of the oil film on both sides of the vane, and avoiding the problem of dry friction.

Description

Technical Field

[0001] The present invention relates to the technical field of compressors, and in particular to a pump body assembly of a rotary compressor, a rotary compressor and a refrigeration device. Background Art

[0002] The vane in a rotary compressor is a component installed in the vane groove of the cylinder. It can slide freely and always keep in contact with the rolling rotor under the action of spring force, thereby separating the closed cavity formed by the cylinder and the rolling rotor into an intake cavity and an exhaust cavity.

[0003] During operation, the vanes of a rotary compressor are subject to friction on both sides, gas pressure at both ends, their own inertia, spring forces, and rolling rotor contact forces. With the advancement of inverter technology and the continuous improvement of the energy efficiency of variable-frequency air conditioners, the demand for compressor performance is increasing. This, in turn, results in increasing suction and exhaust pressure differentials during compressor operation under certain operating conditions. This increases the reliability requirements for the friction pairs formed by the vanes and vane slots, and the vane and roller friction pairs. As the vanes reciprocate in the slots, the gas pressure differential on both sides of the vanes causes the vanes to deflect toward the suction side at the vane head. The friction force exerted by the rollers on the vanes also tends to do the same, causing the entire vane to tilt toward the suction side within the slots. Furthermore, the longer the vane protrudes from the slots, the shorter the vane remains within the slots, resulting in greater vane deflection and a larger vane tilt angle. This tilt reduces the oil film thickness between the vane and the slots, increasing the risk of direct contact between the vane and the slots, leading to greater wear and loss of reliability.

[0004] In the prior art, although the inclination of the sliding vane in the sliding vane groove can be reduced by increasing the length of the sliding vane while keeping the gap unchanged, the length of the sliding vane will affect the outer diameter of the cylinder. Summary of the Invention

[0005] The purpose of the present invention is to overcome the deficiencies of the prior art and provide a pump body assembly of a rotary compressor, a rotary compressor and a refrigeration device, aiming to solve the problem of the sliding vane tilting in the sliding vane groove.

[0006] To achieve the above object, the present invention adopts the following technical solutions:

[0007] In a first aspect, the present invention provides a pump assembly for a rotary compressor, comprising:

[0008] A cylinder having a working chamber and a sliding vane groove communicating with the working chamber;

[0009] An upper flange and a lower flange are respectively sealed and arranged on the upper side and the lower side of the cylinder;

[0010] a slide, movably disposed in the slide slot;

[0011] Among them, the upper flange and the lower flange are both provided with a flange slide groove, the flange slide groove includes a pressure-bearing side and a non-pressure-bearing side, and a tail restraint connected to the tail of the slide is provided in the flange slide groove, and an angle is formed between the side of the tail restraint close to the pressure-bearing side and the pressure-bearing side, and the angle gradually decreases from the entrance of the flange slide groove inward.

[0012] Furthermore, the pressure-bearing side is tilted relative to the central axis of the flange slot so that an angle is formed between the side of the tail restraint member close to the pressure-bearing side and the pressure-bearing side. Furthermore, the angle is less than 1°.

[0013] Furthermore, a side of the tail restraint close to the non-pressure-bearing side is arranged parallel to and spaced from the non-pressure-bearing side.

[0014] Furthermore, a distance between a side of the tail restraint close to the non-pressure-bearing side and the non-pressure-bearing side is 0.001 mm to 0.05 mm.

[0015] Furthermore, the tail restraint comprises a slider and a connector. The slider is slidably arranged relative to the flange slot, and the slider is connected to the tail of the slide through the connector.

[0016] Furthermore, the head of the slider is provided with a chamfered surface.

[0017] Furthermore, the tail restraint comprises a circular rolling body and a connecting piece. The circular rolling body is arranged to roll relative to the flange sliding groove. The circular rolling body is connected to the tail of the sliding piece through the connecting piece.

[0018] In a second aspect, the present invention further provides a rotary compressor comprising the above-mentioned pump body assembly of the rotary compressor.

[0019] In a third aspect, the present invention further provides a refrigeration device comprising the above-mentioned rotary compressor.

[0020] The present invention has the following advantages over the prior art: a pump body assembly for a rotary compressor includes a cylinder, an upper flange, a lower flange, and a vane; the cylinder has a working chamber and a vane groove connected to the working chamber; the upper flange and the lower flange are sealed on the upper and lower sides of the cylinder, respectively; the vane is movably arranged in the vane groove; both the upper and lower flanges are provided with flange grooves, the flange grooves including a pressure-bearing side and a non-pressure-bearing side; a tail restraint connected to the tail of the vane is provided in the flange grooves; a side of the tail restraint close to the pressure-bearing side forms an angle with the pressure-bearing side, and the angle gradually decreases inward from the entrance of the flange grooves. The cooperation between the tail restraint and the vane groove increases the constraint on the tail of the vane, thereby reducing the tilt of the vane head, ensuring the thickness of the oil film on both sides of the vane, and avoiding the problem of dry friction.

[0021] The above description is only an overview of the technical solution of the present invention. In order to more clearly understand the technical means of the present invention, it can be implemented in accordance with the contents of the specification. In order to make the above and other purposes, features and advantages of the present invention more obvious and easy to understand, the following preferred embodiments are specifically cited and described in detail as follows. BRIEF DESCRIPTION OF THE DRAWINGS

[0022] In order to more clearly illustrate the technical solutions of the embodiments of the present invention, the following briefly introduces the drawings required for use in the description of the embodiments. Obviously, the drawings described below are some embodiments of the present invention. For ordinary technicians in this field, other drawings can be obtained based on these drawings without paying any creative work.

[0023] Figure 1 It is a structural schematic diagram of a pump body assembly of a rotary compressor in the prior art;

[0024] Figure 2 for Figure 1 A partial enlarged view of point A in the middle;

[0025] Figure 3 A schematic diagram of the structure of the pump assembly of the rotary compressor provided in a specific embodiment of the present invention Figure 1 ;

[0026] Figure 4 A schematic diagram of the structure of the pump assembly of the rotary compressor provided in a specific embodiment of the present invention Figure 2 ;

[0027] Figure 5 A schematic diagram of the relationship between a slider and a flange slot in a pump assembly of a rotary compressor provided by a specific embodiment of the present invention;

[0028] Figure 6 for Figure 5 A partial enlarged view of point A in the middle;

[0029] Figure 7 A schematic diagram of the installation of a sliding vane and a sliding block in a pump assembly of a rotary compressor provided by a specific embodiment of the present invention;

[0030] Figure 8 A schematic structural diagram of a slider in a pump assembly of a rotary compressor provided by a specific embodiment of the present invention;

[0031] Figure 9 A schematic diagram of the relationship between the circular rolling element and the flange groove in the pump assembly of the rotary compressor provided by a specific embodiment of the present invention;

[0032] Figure 10 for Figure 9 A partial enlarged view of point A in the middle;

[0033] Figure 11 A schematic structural diagram of a circular rolling element in a pump assembly of a rotary compressor provided by a specific embodiment of the present invention;

[0034] Reference numerals:

[0035] 1. Cylinder; 11. Intake side; 12. Exhaust side; 13. Vane groove; 2. Vane; 21. Vane head; 3. Upper flange; 31. Flange groove; 311. Pressure side; 312. Non-pressure side; 4. Lower flange; 5. Roller; 6. Slider; 61. Chamfered surface; 7. Connector; 8. Circular rolling element; 100. High-risk wear area. DETAILED DESCRIPTION

[0036] The following will clearly and completely describe the technical solutions of the present invention in conjunction with specific embodiments of the present invention. Obviously, the embodiments described are only part of the embodiments of the present invention, not all of them. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without making creative efforts are within the scope of protection of the present invention.

[0037] In the description of the present invention, it should be understood that the terms "center", "longitudinal", "lateral", "length", "width", "thickness", "up", "down", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inside", "outside", "clockwise", "counterclockwise", "axial", "radial", "circumferential" and the like to indicate orientations or positional relationships based on the orientations or positional relationships shown in the accompanying drawings, and are only for the convenience of describing the present invention and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore should not be understood as limiting the present invention.

[0038] Furthermore, the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of the technical features being referred to. Thus, a feature defined as "first" or "second" may explicitly or implicitly include at least one such feature. In the description of the present invention, "plurality" means at least two, such as two, three, etc., unless otherwise specifically defined.

[0039] In the present invention, unless otherwise specified or limited, the terms "installed," "connected," "connect," "fixed," etc. should be understood in a broad sense. For example, they can refer to fixed connection, detachable connection, or integration; mechanical connection, electrical connection; direct connection, or indirect connection through an intermediate medium; internal communication between two components, or interaction between two components, unless otherwise specified. Those skilled in the art will understand the specific meanings of the above terms in the present invention based on specific circumstances.

[0040] In the present invention, unless otherwise expressly specified or limited, when a first feature is "above" or "below" a second feature, it may mean that the first and second features are in direct contact, or that the first and second features are in indirect contact through an intermediary. Furthermore, when a first feature is "above," "above," or "above" a second feature, it may mean that the first feature is directly above or diagonally above the second feature, or simply means that the first feature is at a higher level than the second feature. When a first feature is "below," "below," or "below" a second feature, it may mean that the first feature is directly below or diagonally below the second feature, or simply means that the first feature is at a lower level than the second feature.

[0041] It should be noted that when an element is referred to as being "fixed to" or "disposed on" another element, it may be directly on the other element or there may be an intermediate element. When an element is considered to be "connected to" another element, it may be directly connected to the other element or there may be an intermediate element. The terms "vertical," "horizontal," "upper," "lower," "left," "right," and similar expressions used herein are for illustrative purposes only and do not represent the only implementation methods.

[0042] In the traditional air conditioner industry, the compressor has always been a core component. As the most important component, the compressor's energy efficiency, noise, and reliability have always been key industry indicators. However, with the continuous improvement of energy efficiency levels, operating conditions such as liquid inhalation and high pressure ratios are occurring more frequently, placing even stricter demands on compressor reliability.

[0043] Rotary compressors have the highest installation rate among air-conditioning compressor products due to their simple structure. Figure 1 and Figure 2The diagram below shows the structure of the pump assembly of a conventional rotary compressor. Upper and lower flanges 3 and 4 are mounted on either side of cylinder 1, forming a sealed working chamber. The crankshaft's major and minor axes are mounted on upper and lower flanges 3 and 4, respectively, forming two sets of sliding bearings. Roller 5 is mounted on the eccentric portion of the crankshaft. Vane slots 13 are defined in cylinder 1. Vane 2 is mounted within these slots, with its head 21 contacting the outer circumference of roller 5. Vane 2, roller 5, and the inner wall of cylinder 1 divide the working chamber into two sections: intake side 11 and exhaust side 12. Rotation of the crankshaft drives roller 5, causing the pressures of both intake and exhaust sides 11 and 12 to fluctuate periodically. The slide 2 performs periodic reciprocating motion in the slide slot 13. When the middle surface of the slide slot 13 is at an angle of 0°, the slide 2 extension length is 0. When the slide slot 13 is at an angle of 180°, the maximum extension length of the slide 2 is A. The total length of the slide 2 is D. The extension rate of the slide 2 is defined as γ = A / D and γ ≤ 0.5. Figure 2 As shown, when the vane 2 extends out of the vane slot 13, a pressure difference is formed between the exhaust side 12 and the intake side 11. The friction between the roller 5 and the vane 2 causes the head 21 of the vane to tilt toward the intake side 11, and the vane 2 tilts in the vane slot 13. Figure 2 The pressure-bearing position of the vane slot 13 is a high-risk wear area 100. The vane 2 extending out of the vane slot 13 can be regarded as an overhanging beam model, and the longer the vane 2 extends out of the vane slot 13, the shorter the vane 2 in the vane slot 13, the greater the deflection of the vane 2, the greater the inclination angle of the vane 2, and the greater the wear risk. Although there is currently a method of reducing the inclination of the vane 2 in the vane slot 13 by increasing the length of the vane 2 while keeping the gap unchanged, the length of the vane 2 will affect the outer diameter of the cylinder 1. Based on the above problems, the present invention is proposed, and the present invention is described below through specific embodiments.

[0044] like Figures 3 to 11 As shown, an embodiment of the present invention provides a pump body assembly of a rotary compressor, including a cylinder 1, an upper flange 3, a lower flange 4 and a vane 2. The cylinder 1 has a working chamber and a vane groove 13 connected to the working chamber. The upper flange 3 and the lower flange 4 are sealed on the upper and lower sides of the cylinder 1, respectively, and the vane 2 is movably arranged in the vane groove 13; the upper flange 3 and the lower flange 4 are both provided with a flange groove 31, the flange groove 31 includes a pressure-bearing side 311 and a non-pressure-bearing side 312, and a tail constraint connected to the tail of the vane 2 is provided in the flange groove 31, and an angle is formed between the side of the tail constraint close to the pressure-bearing side 311 and the pressure-bearing side 311, and the angle gradually decreases from the entrance of the flange groove 31 inward.

[0045] Specifically, the cylinder 1 is an annular structure, and a working chamber for compressing the refrigerant is formed inside it. A vane groove 13 extending radially is provided on the side wall of the cylinder 1. The vane groove 13 is connected to the working chamber. The cross-sectional shape of the vane groove 13 is adapted to the cross-sectional shape of the vane 2 to allow the vane 2 to slide back and forth radially in the vane groove 13.

[0046] Upper flange 3 and lower flange 4 are bolted to the upper and lower end faces of cylinder 1, respectively. Together, they form a sealed compression space, the aforementioned working chamber. Bearing holes are located in the center of each flange for mounting the crankshaft's major and minor axes, forming a sliding bearing pair to ensure stable crankshaft rotation.

[0047] The vane 2 is movably arranged in the vane groove 13. The head 21 of the vane can extend out of the vane groove 13 and contact the outer circle of the roller 5 installed on the eccentric part of the crankshaft. Driven by the crankshaft, as the roller 5 rotates, the vane 2 reciprocates in the vane groove 13, thereby realizing the compression of the refrigerant in the working chamber.

[0048] To strengthen the circumferential restraint of the vane 2 in the vane slot 13 and reduce vane 2 tilt, flange slots 31 are provided on both the upper flange 3 and the lower flange 4 near the vane slot 13. The flange slot 31 extends axially along the cylinder 1, with a converging cross-section that gradually narrows from the entrance of the flange slot 31 toward the interior. The flange slot 31 includes a pressure-bearing side 311 and a non-pressure-bearing side 312. The pressure-bearing side 311 is closer to the exhaust side 12, while the non-pressure-bearing side 312 is closer to the intake side 11.

[0049] A tail restraint is provided within the flange chute 31. This tail restraint is fixedly connected to the tail of the vane 2 and moves within the flange chute 31 along with the vane 2. The side of the tail restraint near the pressure-bearing side 311 forms an angle with the pressure-bearing side 311. This angle gradually decreases inward from the entrance of the flange chute 31. For example, the angle at the entrance can be 0.8°, gradually decreasing inward to 0.2°. With this structural design, as the length of the vane 2 extending out of the vane slot 13 increases, the tail restraint extends further into the flange chute 31, creating a tighter fit between the tail restraint and the pressure-bearing side 311. This strengthens the circumferential restraint on the tail of the vane 2, effectively suppresses the tilting of the vane 2 head toward the suction side 11, ensures a thick oil film on both sides of the vane 2, and avoids dry friction.

[0050] In one embodiment, the pressure-bearing side 311 is tilted relative to the central axis of the flange slot 31 , so that an angle is formed between the side of the tail restraint member close to the pressure-bearing side 311 and the pressure-bearing side 311 .

[0051] The central axis of the flange chute 31 is the geometric center line along its length. The pressure-bearing side 311 is the side wall of the flange chute 31 close to the exhaust side 12, and is inclined relative to the above-mentioned central axis. Specifically, a fixed inclination angle is formed between the pressure-bearing side 311 and the central axis. The setting of this angle needs to be determined in combination with the contraction trend of the flange chute 31 and the movement requirements of the tail restraint. For example, if the central axis of the flange chute 31 is a plumb line, the pressure-bearing side 311 can be tilted toward the central axis, so that from the entrance to the inside of the flange chute 31, the distance between the pressure-bearing side 311 and the central axis gradually decreases, that is, the cross-section of the flange chute 31 presents a contraction feature.

[0052] The side of the tail restraint near the pressure-bearing side 311 is designed as a flat surface, parallel to the direction of movement of the tail restraint (i.e., parallel to the central axis of the flange chute 31). Assuming that when the tail restraint is located at the entrance of the flange chute 31, the initial angle between the side of the tail restraint near the pressure-bearing side 311 and the pressure-bearing side 311 is 0.5°. As the tail restraint moves along the central axis toward the interior of the flange chute 31, the angle between the two gradually decreases due to the continued inclination of the pressure-bearing side 311 toward the central axis. By the time the tail restraint reaches the innermost side of the flange chute 31, the angle has decreased to 0.1°.

[0053] The tilting of the pressure-bearing side 311 causes the clearance between the tail restraint and the pressure-bearing side 311 to dynamically change. When the vane 2 extends a short distance from the vane slot 13, the tail restraint is located near the entrance of the flange slot 31. At this point, the angle between the two is relatively large (e.g., 0.5°), resulting in a relatively loose clearance. This reduces resistance to the tail restraint's movement and prevents excessive interference with the reciprocating motion of the vane 2. As the vane 2 extends further (i.e., the risk of vane 2 tilting increases), the tail restraint extends deeper into the flange slot 31, reducing the angle. This improves the fit between the tail restraint and the pressure-bearing side 311, strengthening the restraining effect on the tail of the vane 2 and effectively preventing the vane 2 from tilting toward the suction side 11.

[0054] like Figure 6 As shown, the angle β is less than 1°, and generally ranges from 0.1° to 1°. The setting of this angle range is based on a comprehensive consideration of the constraint effect and movement resistance of the slide 2, and is verified by a large number of experiments. Specifically, if the angle is too large (such as equal to or greater than 1°), then when the tail constraint member penetrates deep into the flange slot 31, the fitting clearance between it and the pressure-bearing side 311 is still relatively loose, and it is impossible to effectively enhance the constraint on the tail of the slide 2, and it is difficult to suppress the tilt of the slide 2; if the angle is too small (such as less than 0.1°), then during the movement of the tail constraint member, it is easy for the two to get stuck due to processing errors, affecting the normal reciprocating motion of the slide 2. Therefore, setting the angle to less than 1° can not only ensure that sufficient constraint is provided when the risk of slide 2 tilting is high, but also avoid adverse effects on the movement of slide 2.

[0055] Furthermore, a side of the tail restraint member close to the non-pressure-bearing side 312 is arranged parallel to and spaced from the non-pressure-bearing side 312 .

[0056] The non-pressure side 312 is the side wall of the flange chute 31 close to the air intake side 11. It extends linearly along the length of the flange chute 31 (i.e., the reciprocating motion direction of the slide 2) and remains parallel to the central axis of the flange chute 31. The side of the tail restraint close to the non-pressure side 312 is also configured as a planar structure. This plane is parallel to the plane of the non-pressure side 312, and a uniform distance is formed between the two. Figure 6 As shown, the distance d between the side of the tail restraint close to the non-pressure side 312 and the non-pressure side 312 is 0.001 mm to 0.05 mm, and the specific value can be 0.02 mm or 0.05 mm.

[0057] In one embodiment, if Figures 5 to 8 As shown, the tail restraint member includes a slider 6 and a connector 7 . The slider 6 is slidably arranged relative to the flange slot 31 . The slider 6 is connected to the tail of the slide 2 via the connector 7 .

[0058] The overall shape of the slider 6 matches the cross-sectional shape of the flange chute 31, forming a rectangular parallelepiped structure. The side of the slider 6 closest to the pressure-bearing side 311 is flat, forming a dynamically changing angle with the pressure-bearing side 311 of the flange chute 31. The side closest to the non-pressure-bearing side 312 is also flat, maintaining a parallel and spaced relationship with the non-pressure-bearing side 312.

[0059] Connector 7 securely connects slider 6 to the rear end of slide 2. In this embodiment, connector 7 utilizes a hexagon socket head bolt. Correspondingly, two threaded holes matching the bolts are defined in the center of slider 6. Threaded holes of the same specification are also defined on the upper and lower sides of the rear end of slide 2, ensuring that the bolts can be screwed into both threaded holes simultaneously, achieving a secure connection.

[0060] When the compressor is running, the crankshaft drives the roller 5 to rotate, causing the vane 2 to reciprocate within the vane slot 13. At this time, the slider 6, driven by the connector 7, slides along with the vane 2 within the flange slot 31. When the vane 2 is extended to a short length, the slider 6 is located near the entrance of the flange slot 31, with a large angle between the slider 6 and the pressure-bearing side 311, resulting in low sliding resistance. When the vane 2 is extended to a longer length, the slider 6 penetrates deeper into the flange slot 31, reducing the angle between the slider 6 and the pressure-bearing side 311 and creating a tighter fit. This strengthens the restraining effect on the tail of the vane 2 and effectively prevents the vane 2 from tilting.

[0061] In one embodiment, if Figure 8 As shown, the head of the slider 6 is provided with a chamfered surface 61 .

[0062] Specifically, the head of the slider 6 is the end closest to the entrance of the flange slot 31 along the direction of movement. This end is the first to enter the flange slot 31 when the slider 6 moves into the flange slot 31 along with the slide 2. To prevent rigid collision or jamming between the head of the slider 6 and the edge of the entrance of the flange slot 31, a chamfered surface 61 is provided on the edge of the slider 6 head. This chamfered surface 61 is a transitional slope connecting the end face and side face of the slider 6 head, allowing the slider 6 to smoothly enter the flange slot 31. The slider 6 carries lubricating oil into the flange slot 31, thus achieving sliding lubrication.

[0063] like Figures 9 to 11 As shown, the tail restraint member includes a circular rolling body 8 and a connecting member 7 . The circular rolling body 8 is arranged to roll relative to the flange sliding groove 31 . The circular rolling body 8 is connected to the tail of the sliding plate 2 through the connecting member 7 .

[0064] The circular rolling element 8 can be a wheel, a roller, or a ball bearing, and the connecting member 7 is used to connect the circular rolling element 8 to the rear end of the slide 2 while ensuring that the circular rolling element 8 can rotate freely. In this embodiment, the connecting member 7 is a pin structure, one end of which is connected to the rear end of the slide 2 by an interference fit or adhesive connection, and the other end is fixedly connected to the connecting hole defined in the circular rolling element 8.

[0065] Because the circular rolling element 8 and the flange chute 31 experience rolling friction, the friction coefficient is significantly lower than the sliding friction between the slider 6 and the flange chute 31, further reducing frictional resistance. Furthermore, the rolling motion of the circular rolling element 8 is smoother, effectively absorbing shock and vibration during motion and reducing noise during compressor operation.

[0066] The present invention also provides a rotary compressor including the above-mentioned pump assembly of the rotary compressor. Except for the above-mentioned pump assembly of the rotary compressor, the rest of the structure of the rotary compressor is the same as that in the prior art, and the rest of the structure is not described in detail here.

[0067] It should be noted that the rotary compressor provided in the embodiment of the present invention includes the above-mentioned pump body assembly of the rotary compressor. Therefore, the rotary compressor has all the beneficial effects of the above-mentioned pump body assembly of the rotary compressor, which will not be repeated here.

[0068] The embodiment of the present invention further provides a refrigeration device including the above-mentioned rotary compressor. Except for the above-mentioned rotary compressor, the rest of the structure of the refrigeration device can be the same as that in the prior art, and the rest of the structure is not described here in detail.

[0069] It should be noted that the refrigeration device provided in the embodiment of the present invention includes the above-mentioned rotary compressor, so the refrigeration device has all the beneficial effects of the above-mentioned rotary compressor, which will not be described in detail here.

[0070] The above description is merely a specific embodiment of the present invention, but the scope of protection of the present invention is not limited thereto. Any person skilled in the art can easily conceive of various equivalent modifications or substitutions within the technical scope disclosed in the present invention, and such modifications or substitutions are intended to be within the scope of protection of the present invention. Therefore, the scope of protection of the present invention shall be subject to the scope of protection of the claims.

Claims

1. A pump assembly for a rotary compressor, characterized in that: include: The cylinder comprises a working chamber and a sliding vane groove communicating with the working chamber, wherein the working chamber is divided into an intake side and an exhaust side; An upper flange and a lower flange are respectively sealed and arranged on the upper side and the lower side of the cylinder; a slide, movably disposed in the slide slot; In which, the upper flange and the lower flange are both provided with a flange slide groove, and the flange slide groove includes a pressure-bearing side and a non-pressure-bearing side, the pressure-bearing side is the side close to the exhaust side, and the non-pressure-bearing side is the side close to the intake side, and a tail restraint connected to the tail of the slide is provided in the flange slide groove, and an angle is formed between the side of the tail restraint close to the pressure side and the pressure side, and the angle gradually decreases from the entrance of the flange slide groove inward, and the pressure-bearing side is inclined relative to the central axis of the flange slide groove so that the angle is formed between the side of the tail restraint close to the pressure side and the pressure side, and the central axis of the flange slide groove is the geometric center line along its length direction.

2. The pump body assembly of the rotary compressor according to claim 1, characterized in that: The angle is less than 1°.

3. The pump body assembly of the rotary compressor according to claim 1 or 2, characterized in that: The side of the tail restraint close to the non-pressure-bearing side is arranged parallel to and spaced from the non-pressure-bearing side.

4. The pump body assembly of the rotary compressor according to claim 3, characterized in that: The distance between the side of the tail restraint close to the non-pressure-bearing side and the non-pressure-bearing side is 0.001 mm to 0.05 mm.

5. The pump body assembly of the rotary compressor according to claim 1, characterized in that: The tail restraint comprises a slider and a connector. The slider is slidably arranged relative to the flange slot. The slider is connected to the tail of the slide through the connector.

6. The pump body assembly of the rotary compressor according to claim 5, characterized in that: The head of the slider is provided with a chamfered surface.

7. The pump body assembly of the rotary compressor according to claim 1, characterized in that: The tail restraint comprises a circular rolling body and a connecting piece. The circular rolling body is arranged to roll relative to the flange sliding groove. The circular rolling body is connected to the tail of the sliding piece through the connecting piece.

8. A rotary compressor, characterized in that: A pump body assembly comprising a rotary compressor according to any one of claims 1 to 7.

9. A refrigeration device, characterized in that: Including the rotary compressor described in claim 8.

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