A rotor pump body structure and compressor

Abstract

The application discloses a rotor pump body structure and a compressor. The rotor pump body structure comprises an upper flange, a lower flange, a crankshaft, a cylinder and two sliding vane assemblies. The cylinder is arranged between the upper flange and the lower flange. The crankshaft is rotatably arranged in the upper flange, the cylinder and the lower flange. The cylinder is provided with a compression chamber. The crankshaft and the cylinder are both provided with sliding vane grooves in communication with the compression chamber. One end of each of the two sliding vane assemblies is reciprocally movably arranged in the sliding vane grooves. The other end of each of the two sliding vane assemblies extends out of the sliding vane groove and can contact or separate from the crankshaft. The crankshaft is a concentric shaft. The crankshaft is a concentric shaft, the influence of the eccentric structure on the dynamic and static balance of the pump body is reduced, and the stability of the pump body is enhanced. Meanwhile, the double sliding vane structure is used, the movement stroke of the sliding vane is reduced, and the lubrication effect is improved. In addition, the roller is cancelled, one relative movement pair of the pump body is reduced, and the effects of reducing the power of the compressor and the processing cost are achieved.

Description

Technical Field

[0001] This invention relates to the field of compressor technology, and in particular to a rotary pump body structure and compressor. Background Technology

[0002] In the refrigeration and air conditioning field, the rotary compressor, as a highly efficient and compact compression device, has been widely used. Its basic principle is that an eccentric crankshaft drives rollers to rotate within a cylinder, while vanes divide the cylinder into a high-pressure chamber and a low-pressure chamber. As the rollers rotate, the gas is compressed in the high-pressure chamber and then discharged, realizing the compression process in the refrigeration cycle. However, this traditional design faces a series of technical challenges in practical applications.

[0003] Firstly, while the eccentric structure effectively compresses gas, it also makes it difficult to maintain the dynamic and static balance of the pump body. Due to the eccentric configuration of the crankshaft, significant vibration and noise are generated during high-speed operation, which not only affects the stable operation of the equipment but may also shorten its service life.

[0004] Secondly, the support and lubrication mechanism of the vanes is also a key factor restricting the performance improvement of rolling rotor compressors. In traditional designs, the vane stroke is relatively long, resulting in insufficient lubrication. In addition, during crankshaft rotation, the rollers and the eccentric part of the crankshaft wear continuously, leading to a significant reduction in the service life of both the rollers and the crankshaft. Summary of the Invention

[0005] The purpose of this invention is to provide a rotor pump body structure and compressor, which aims to solve the problems of difficulty in maintaining the dynamic and static balance of existing compressor pump bodies and the long stroke of the sliding vanes.

[0006] This invention provides a rotor pump body structure, including: an upper flange, a lower flange, a crankshaft, a cylinder, and two vane assemblies. The cylinder is disposed between the upper flange and the lower flange. The crankshaft is rotatably mounted within the upper flange, the cylinder, and the lower flange. A compression chamber is provided within the cylinder. Both the crankshaft and the cylinder are provided with vane grooves communicating with the compression chamber. One end of each of the two vane assemblies is reciprocally mounted within the two vane grooves, and the other end of each vane assembly extends outside the vane grooves and can contact or separate with the rotation of the crankshaft. The crankshaft is a concentric shaft.

[0007] Furthermore, the crankshaft is located on the centerline of the compression chamber.

[0008] Furthermore, each of the slider assemblies includes a slider and an elastic member, one end of the elastic member abutting against one end of the slider, the other end of the elastic member abutting against the slider groove, and the other end of the slider extending out of the slider groove.

[0009] Furthermore, each of the slide assembly includes a plurality of elastic elements, which are distributed along the axial direction of the crankshaft.

[0010] Furthermore, the bottom of the slide groove is provided with a first limiting hole, the slide is provided with a second limiting hole, one end of the elastic member abuts in the second limiting hole, and the other end of the elastic member abuts in the first limiting hole.

[0011] Furthermore, the other end of the slider is provided with an outwardly convex arc-shaped portion.

[0012] Furthermore, the diameter of the compression chamber is D, the maximum outer diameter of the crankshaft is d, the arc angle of the arc portion of the slider is A, the radius of the arc portion of the slider is R, and satisfies: (Dd) / 2<2*(RR*cos(A / 2)).

[0013] Furthermore, the crankshaft is provided with at least one balance hole to ensure that the center of gravity of the crankshaft is located on the central axis of the crankshaft.

[0014] Furthermore, the crankshaft is provided with an oil outlet channel, and the sliding vane groove is connected to the oil outlet channel.

[0015] Furthermore, it also includes an oil guide plate, which is installed in the oil outlet channel of the crankshaft.

[0016] This invention also provides a compressor, including the above-described rotor pump body structure.

[0017] This invention discloses a rotor-type pump body structure and compressor. The rotor-type pump body structure includes: an upper flange, a lower flange, a crankshaft, a cylinder, and two vane assemblies. The cylinder is disposed between the upper and lower flanges. The crankshaft is rotatably mounted within the upper flange, cylinder, and lower flange. A compression chamber is provided within the cylinder. Both the crankshaft and the cylinder are provided with vane grooves communicating with the compression chamber. One end of each of the two vane assemblies is reciprocally mounted within its respective vane groove, while the other end extends beyond the groove and can contact or separate with the rotation of the crankshaft. The crankshaft is concentric. The concentric crankshaft of this invention reduces the impact of the eccentric structure on the dynamic and static balance of the pump body, enhancing its stability. Simultaneously, the use of a double vane structure reduces the vane travel distance, improving lubrication. Furthermore, the elimination of rollers reduces one relative moving pair within the pump body, lowering compressor power and manufacturing costs, and preventing continuous wear between the rollers and the eccentric portion of the crankshaft, thereby extending the crankshaft's service life. Attached Figure Description

[0018] To more clearly illustrate the technical solutions of the embodiments of the present invention, the drawings used in the following description of the embodiments will be briefly introduced. Obviously, the drawings described below are some embodiments of the present invention. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0019] Figure 1 This is a structural diagram of a rotor pump body.

[0020] Figure 2 A cross-sectional schematic diagram of the rotor pump body structure;

[0021] Figure 3 This is a schematic diagram of the cylinder structure;

[0022] Figure 4 This is a cross-sectional view of the cylinder;

[0023] Figure 5 This is a schematic diagram of the crankshaft structure;

[0024] Figure 6 This is a schematic diagram of the first process of slider contact;

[0025] Figure 7 This is a schematic diagram of the second process of slider contact;

[0026] Figure 8 This is a schematic diagram of the third process of slider contact;

[0027] Figure 9 This is a schematic diagram of the fourth process of slider contact;

[0028] Figure 10 This is a schematic diagram of the slider from a first-person perspective.

[0029] Figure 11 A schematic diagram of the slider from a second perspective;

[0030] Figure 12 A schematic diagram showing the crankshaft and cylinders;

[0031] Figure 13 This is a diagram showing the markings on the slider;

[0032] Figure 14 This is a schematic diagram of the structure of the axle platform;

[0033] Figure 15 Schematic diagrams of other shaped axle platforms;

[0034] Figure 16 This is a cross-sectional view of the crankshaft;

[0035] Figure 17 This is a structural schematic diagram of the lower flange;

[0036] Figure 18 This is a schematic diagram of the upper flange structure;

[0037] Explanation of markings in the diagram:

[0038] 1. Upper flange; 2. Lower flange; 3. Crankshaft; 4. Cylinder; 5. Sliding vane assembly; 6. Compression chamber; 7. Sliding vane groove; 8. Sliding vane; 9. Elastic element; 10. First limiting hole; 11. Second limiting hole; 12. Arc-shaped part; 13. Balance hole; 14. Rotating shaft; 15. Shaft platform; 16. Oil outlet channel; 17. Oil reservoir; 18. Oil outlet; 19. Oil guide plate; 20. First boss; 21. Second boss; 22. Third boss; 23. Air intake port; 24. Cylinder exhaust port; 25. Positioning hole; 26. Flange oil guide groove; 27. Support part. Detailed Implementation

[0039] The technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some, not all, of the embodiments of the present invention. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.

[0040] It should be understood that, when used in this specification and the appended claims, the terms "comprising" and "including" indicate the presence of the described features, integrals, steps, operations, elements and / or components, but do not exclude the presence or addition of one or more other features, integrals, steps, operations, elements, components and / or collections thereof.

[0041] It should also be understood that the terminology used in this specification is for the purpose of describing particular embodiments only and is not intended to limit the invention. As used in this specification and the appended claims, the singular forms “a,” “an,” and “the” are intended to include the plural forms unless the context clearly indicates otherwise.

[0042] It should also be further understood that the term "and / or" as used in this specification and the appended claims refers to any combination of one or more of the associated listed items and all possible combinations, and includes such combinations.

[0043] Please see Figure 1-5This embodiment provides a rotor pump body structure, including: an upper flange 1, a lower flange 2, a crankshaft 3, a cylinder 4, and two vane assemblies 5. The cylinder 4 is disposed between the upper flange 1 and the lower flange 2. The crankshaft 3 is rotatably mounted in the upper flange 1, the cylinder 4, and the lower flange 2. A compression chamber 6 is provided in the cylinder 4. Both the crankshaft 3 and the cylinder 4 are provided with vane grooves 7 that communicate with the compression chamber 6. One end of each of the two vane assemblies 5 is reciprocated and mounted in the two vane grooves 7. The other end of each vane assembly 5 extends out of the vane grooves 7 and can contact or separate with the rotation of the crankshaft 3. The crankshaft 3 is a concentric shaft.

[0044] In this embodiment, the crankshaft 3 is a concentric shaft, which reduces the impact of the eccentric structure on the dynamic and static balance of the pump body and enhances the stability of the pump body. Simultaneously, the use of a double-vane structure reduces the travel of the vanes and improves lubrication. Furthermore, the rollers are eliminated, reducing one relative moving pair in the pump body, thus lowering compressor power and manufacturing costs, and preventing continuous wear between the rollers and the eccentric portion of the crankshaft 3, thereby extending the service life of the crankshaft 3.

[0045] in, Figure 6-9 Part b in the diagram is a partial schematic diagram corresponding to part a in the attached diagram.

[0046] In this embodiment, the cylinder 4 is connected to the upper flange 1 by screws, and the cylinder 4 is also connected to the lower flange 2 by screws; alternatively, the upper flange 1, cylinder 4, and lower flange 2 are connected by screws that pass through the upper flange 1, cylinder 4, and lower flange 2. Screw connection is a high-strength mechanical connection method. By tightening the screws, sufficient preload can be generated, forming a tight and secure connection between the cylinder 4 and the upper and lower flanges 2. This connection method can withstand large working loads and vibrations, ensuring the stability of the cylinder 4 during operation.

[0047] Furthermore, crankshaft 3 is located on the center line of compression chamber 6.

[0048] The centerline design of crankshaft 3 helps to better balance inertial forces and torque fluctuations during rotation, thereby reducing vibration and noise during compressor operation. Placing crankshaft 3 on the centerline of compression chamber 6 allows for a more compact compressor structure, contributing to a reduction in equipment size and weight.

[0049] In this embodiment, please refer to Figure 2 Each slider assembly 5 includes a slider 8 and an elastic member 9. One end of the elastic member 9 abuts against one end of the slider 8, and the other end of the elastic member 9 abuts against the slider groove 7. The other end of the slider 8 extends out of the slider groove 7.

[0050] One end of the elastic element 9 (such as a spring) abuts against the slider 8, and the other end abuts against the slider groove 7. This design allows the slider 8 to automatically return to its original position after being displaced by an external force, thanks to the elastic force of the elastic element 9. Because the elastic element 9 has a certain degree of elasticity and compressibility, the slider assembly 5 can adapt to a certain degree of dimensional changes and installation errors, reducing the requirements for installation accuracy and improving the flexibility and versatility of the design.

[0051] Among them, the elastic component 9 includes, but is not limited to, springs, rubber, air cushions, etc. These materials have good elasticity and resilience, and can deform when subjected to external force, and can return to their original shape and size after the external force is removed.

[0052] Furthermore, each slider assembly 5 includes multiple elastic elements 9, which are distributed along the axial direction of the crankshaft 3. For example, each slider assembly 5 includes three elastic elements 9, which are distributed along the axial direction of the crankshaft 3.

[0053] Multiple elastic elements 9 distributed axially provide more uniform support force, helping to reduce the swaying and offset of the slider 8 during movement, thereby enhancing the stability of the entire assembly and making the slider 8 more stable during reciprocating motion. By distributing the stress points of the elastic elements 9, the load on individual elastic elements 9 can be reduced, lowering the risk of fatigue damage and extending the service life of the entire slider assembly 5. Simultaneously, the multiple elastic elements 9 also act as mutual backups; even if one fails, the others can continue to operate, ensuring the normal operation of the machinery.

[0054] In this embodiment, please refer to Figure 4 and Figure 10 The bottom of the sliding groove 7 is provided with a first limiting hole 10, and the sliding plate 8 is provided with a second limiting hole 11. One end of the elastic member 9 abuts in the second limiting hole 11, and the other end of the elastic member 9 abuts in the first limiting hole 10.

[0055] The slider 8 is stably connected to the slider groove 7 by the elastic element 9, and precise positioning is achieved through two limiting holes. This design effectively prevents the slider 8 from shifting or shaking during sliding, ensuring its stability and accuracy at the designated position. The first limiting hole 10 and the second limiting hole 11 ensure the correct installation of the elastic element 9 and improve the installation efficiency of the elastic element 9.

[0056] In this embodiment, the other end of the slider 8 is provided with an outwardly protruding arc-shaped portion 12 (e.g., Figure 11 (As shown).

[0057] The convex arc-shaped portion 12 forms a line contact with the corresponding contact surface (such as the cylinder wall 4 or the sliding vane 8), which significantly reduces the contact area. This helps reduce wear between the convex arc-shaped portion 12 and the corresponding contact surface, thereby improving the service life of the sliding vane 8 and the cylinder 4.

[0058] For further details, please refer to Figure 12 and Figure 13 When the slide vane 8 rotates to a specific position, the slide vane 8 on the crankshaft 3 and the slide vane 8 on the cylinder 4 may come into direct contact with each other, which will cause the crankshaft 3 to jam and become unable to continue working normally. To ensure that the slide vane 8 on the crankshaft 3 and the slide vane 8 on the cylinder 4 do not come into direct contact with each other, the height H of the arc-shaped part 12 needs to be limited. Specifically, the diameter of the compression chamber 6 is D, the maximum outer diameter of the crankshaft 3 is d; the arc angle of the arc-shaped part 12 of the slide vane 8 is A, the radius of the arc-shaped part 12 of the slide vane 8 is R, and the following conditions must be met: (Dd) / 2 < 2*(RR*cos(A / 2)).

[0059] By limiting (Dd) / 2 < 2*(RR*cos(A / 2)), when both the slide vane 8 on the crankshaft 3 and the slide vane 8 on the cylinder 4 are at their highest points, the extension distance of the slide vane 8 on the cylinder 4 is very small. The slide vane 8 on the crankshaft 3 and the slide vane 8 on the cylinder 4 will not have direct contact between their surfaces and edges. When the arc-shaped part 12 on the two slide vanes 8 is squeezed, it can smoothly transition under the action of the spring, thereby ensuring the normal operation of the pump body.

[0060] In this embodiment, the crankshaft 3 is provided with at least one balance hole 13 (e.g., ...) to ensure that the center of gravity of the crankshaft 3 is located on the central axis of the crankshaft 3. Figure 14 (As shown). The material removal volume of the balance hole 13 and the material removal volume of the sliding groove 7 on the crankshaft 3 can be the same or different, as long as the center of gravity of the crankshaft 3 is located on the central axis of the crankshaft 3.

[0061] For details, please refer to Figure 5 The crankshaft 3 is provided with a rotating shaft 14 and a shaft seat 15, which are connected. The rotating shaft 14 is rotatably installed in the upper flange 1, the cylinder 4 and the lower flange 2. The shaft seat 15 is located in the compression chamber 6, and at least one balance hole 13 is located on the shaft seat 15.

[0062] The design of the balance hole 13 can significantly reduce the vibration generated by the crankshaft 3 during rotation. Since the crankshaft 3 is a key component in the engine, its rotational stability directly affects the overall performance of the engine. By ensuring that the center of gravity of the crankshaft 3 is located on the central axis, the balance hole 13 can effectively balance the centrifugal force generated by the crankshaft 3 during rotation, thereby reducing vibration and noise.

[0063] It should be noted that the shaft support 15 in this embodiment can be provided with one balance hole 13, or two balance holes 13 (e.g., Figure 15 As shown in b), three balance holes 13 can also be set (as shown in b). Figure 14 As shown), four balance holes 13 can also be set (as shown). Figure 15 (as shown in a). In addition to the above examples, the number of balance holes 13 in this embodiment may vary depending on the situation, and the shape of the corresponding shaft platform 15 may also vary depending on the situation. This embodiment does not limit this.

[0064] In this embodiment, an oil outlet channel 16 is provided on the crankshaft 3 (e.g., Figure 16 As shown in the figure, the sliding vane groove 7 is connected to the oil outlet channel 16.

[0065] The connection between the oil outlet channel 16 and the vane groove 7 allows lubricating oil to be delivered directly and efficiently to the vane groove 7 and the compression chamber 6. This design ensures a continuous supply of a limited amount of refrigerant oil to the compression chamber 6 during the reciprocating motion of the vane 8. This benefits the pump body lubrication, reducing friction and wear caused by insufficient lubrication, and also reduces the impact of excessive refrigerant oil on the compression process. Simultaneously, sufficient lubricating oil forms a thicker lubricating film, which helps to further reduce the coefficient of friction, improve the wear resistance of moving parts, and thus extend the service life of the vane 8 and related components.

[0066] Furthermore, an oil reservoir 17 is provided on the bearing platform 15 (e.g., Figure 14 As shown), the side of the rotating shaft 14 is provided with an oil outlet 18 (as shown). Figure 16 As shown in the figure, the oil outlet 18 is connected to the oil outlet channel 16.

[0067] The oil reservoir 17 on the shaft support 15 can store a certain amount of lubricating oil, ensuring a sufficient supply of lubricating oil during equipment operation. This design reduces lubrication problems caused by insufficient lubricating oil. The connection between the oil outlet 18 and the oil outlet channel 16 allows the lubricating oil to flow to the parts that need lubrication along a predetermined path. This directional oil supply method improves the utilization rate of lubricating oil and reduces lubricating oil waste.

[0068] In this embodiment, please refer to Figure 2 It also includes: an oil guide plate 19, which is installed in the oil outlet channel 16.

[0069] The oil guide plate 19 effectively guides the refrigerant oil in the compressor oil sump into the pump body through a spiral principle. This design not only ensures smooth oil flow but also provides necessary lubrication for the pump body, thereby guaranteeing the pump's efficient operation and long-term stability.

[0070] Furthermore, an interference fit can be used between the oil guide plate 19 and the oil outlet channel 16.

[0071] The interference fit, by making the outer diameter of the oil guide plate 19 slightly larger than the inner diameter of the oil outlet channel 16, generates a certain amount of extrusion deformation during assembly, thereby ensuring a tight seal between the oil guide plate 19 and the oil outlet channel 16. This tight fit effectively prevents lubricating oil leakage and ensures the normal operation of the lubrication system. Due to the preload generated by the interference fit, the connection between the oil guide plate 19 and the oil outlet channel 16 is more stable and reliable. This stable connection can resist vibration and impact during equipment operation, preventing the oil guide plate 19 from loosening or falling off, and ensuring the long-term stable operation of the lubrication system.

[0072] In this embodiment, please refer to Figure 3 The cylinder 4 is provided with a first boss 20, a second boss 21 and a third boss 22. The first boss 20 and the second boss 21 are connected. The first boss 20 and the second boss 21 are not flush. The second boss 21 and the third boss 22 are flush. The third boss 22 is provided with an air intake 23 that communicates with the compression chamber 6.

[0073] The first boss 20 and the second boss 21 are connected, and the end face of the first boss 20 is slightly lower than the end face of the second boss 21. This reduces the machining area for finishing, lowers machining costs, and improves machining efficiency. The second boss 21 and the third boss 22 are flush. The first boss 20 and the second boss 21 are not flush to ensure the longitudinal safety distance of the air intake 23, and also to reduce the weight of the component.

[0074] Furthermore, the inner wall of the compression chamber 6 of the cylinder 4 is provided with a cylinder exhaust port 24, which is connected to the flange exhaust port.

[0075] The cylinder exhaust port 24 is directly located on the inner wall of the compression chamber 6, ensuring that the high-pressure gas generated during compression can be smoothly discharged. This design reduces airflow resistance and turbulence during the discharge process, thus improving exhaust efficiency.

[0076] The first boss 20 and / or the third boss 22 are each provided with positioning holes 25 for assembling and positioning the cylinder 4.

[0077] The locating hole 25 provides a precise positional reference for the assembly of cylinder 4, enabling cylinder 4 to be accurately aligned and fixed when assembled with other components. This helps reduce errors during the assembly process and improves the assembly accuracy of the entire system.

[0078] In this embodiment, please refer to Figure 17 The lower flange 2 is provided with a flange oil guide groove 26 to lubricate the rotating shaft 14.

[0079] In this embodiment, please refer to Figure 17 and Figure 18Both the upper flange 1 and the lower flange 2 are provided with support parts 27, and the rotating shaft 14 is rotatably mounted in the support parts 27. The design of the support parts 27 allows the load borne by the rotating shaft 14 to be evenly distributed on the upper flange 1 and the lower flange 2, thereby improving the load-bearing capacity and stability of the overall structure.

[0080] The components in this embodiment are all simple parts that can be easily manufactured; as long as the manufacturing accuracy is guaranteed as required, it is sufficient.

[0081] The working principle of the rotor pump body structure in this embodiment is as follows: The refrigerant of the compressor enters through the suction port 23, is compressed by the cylinder 4 and crankshaft 3, forming high-pressure gas, which is then discharged through the exhaust port on the side of the cylinder 4. During the compression process, the motor drives the rotor to rotate the crankshaft 3. During the rotation of the crankshaft 3, the sliding vanes 8 on the crankshaft 3 rotate from the lowest point to the highest point, and then smoothly pass through the two arc-shaped portions 12 within a small gap with the sliding vanes 8 on the cylinder 4. Please refer to [link / reference]. Figure 6-9 Specifically, when the sliding vane 8 on the crankshaft 3 contacts the sliding vane 8 on the cylinder 4 (e.g. Figure 6 As shown), with the rotation of crankshaft 3, the sliding vane 8 on crankshaft 3 and the sliding vane 8 on cylinder 4 will compress the elastic element 9. When the lowest point of the arc-shaped portion 12 on the sliding vane 8 on crankshaft 3 abuts against the highest point of the arc-shaped portion 12 on the sliding vane 8 on cylinder 4 (as shown), Figure 9 As shown in the figure, at this time the elastic element 9 is compressed to the maximum compression state, and then the rotation of the crankshaft 3 will cause the two sliding plates 8 to disengage.

[0082] The assembly process of the rotor pump body structure in this embodiment is as follows:

[0083] Place the upper flange 1 on the cylinder 4, and then tighten it with screws;

[0084] Place the elastic element 9 and the sliding plate 8 into the sliding plate groove 7 of the crankshaft 3, and lubricate to fit the rotating shaft 14 of the crankshaft 3 into the inner hole of the upper flange 1.

[0085] Place the sliding vane 8 into the sliding vane groove 7 on the cylinder 4, then place the lower flange 2 on the cylinder 4, and finally tighten it with screws.

[0086] In this embodiment, the parts can be assembled according to their dimensions, eliminating the need for centering equipment and reducing the impact of pump body displacement on performance.

[0087] This embodiment also provides a compressor, including: the rotor pump body structure of the above embodiment.

[0088] The various embodiments in this specification are described in a progressive manner, with each embodiment focusing on its differences from other embodiments. Similar or identical parts between embodiments can be referred to interchangeably. For the apparatus disclosed in the embodiments, since it corresponds to the method disclosed in the embodiments, the description is relatively simple; relevant parts can be referred to in the method section. It should be noted that those skilled in the art can make various improvements and modifications to this invention without departing from its principles, and these improvements and modifications also fall within the protection scope of the claims of this invention.

[0089] It should also be noted that, in this specification, relational terms such as "first" and "second" are used only to distinguish one entity or operation from another, and do not necessarily require or imply any such actual relationship or order between these entities or operations. Furthermore, the terms "comprising," "including," or any other variations thereof are intended to cover non-exclusivity.

[0090] The term "comprises" implies that a process, method, article, or apparatus that comprises a list of elements includes not only those elements but also other elements not expressly listed, or elements inherent to such a process, method, article, or apparatus. Unless otherwise specified, an element defined by the phrase "comprises a..." does not exclude the presence of other identical elements in the process, method, article, or apparatus that includes said element.

Claims

1. A rotor pump body structure, characterized in that, include: The system comprises an upper flange, a lower flange, a crankshaft, a cylinder, and two vane assemblies. The cylinder is disposed between the upper flange and the lower flange. The crankshaft is rotatably mounted within the upper flange, the cylinder, and the lower flange. The cylinder contains a compression chamber. Both the crankshaft and the cylinder are provided with vane grooves communicating with the compression chambers. One end of each of the two vane assemblies is reciprocally mounted within the two vane grooves, and the other end of each vane assembly extends out of the vane grooves and can contact or separate with the rotation of the crankshaft. The crankshaft is a concentric shaft. Each of the aforementioned slider assemblies includes: a slider and an elastic member, one end of the elastic member abutting against one end of the slider, the other end of the elastic member abutting against the slider groove, and the other end of the slider extending out of the slider groove; The other end of the slider is provided with an outwardly convex arc-shaped portion; The diameter of the compression chamber is D, the maximum outer diameter of the crankshaft is d; the arc angle of the arc portion of the slider is A, the radius of the arc portion of the slider is R, and the following conditions are met: (Dd) / 2 < 2*(RR*cos(A / 2)).

2. The rotor pump body structure according to claim 1, characterized in that, The crankshaft is located on the center line of the compression chamber.

3. The rotor pump body structure according to claim 1, characterized in that, Each of the slide assembly includes a plurality of elastic elements, which are distributed along the axial direction of the crankshaft.

4. The rotor pump body structure according to claim 1, characterized in that, The bottom of the slide groove is provided with a first limiting hole, and the slide is provided with a second limiting hole. One end of the elastic element abuts in the second limiting hole, and the other end of the elastic element abuts in the first limiting hole.

5. The rotor pump body structure according to claim 1, characterized in that, The crankshaft is provided with at least one balance hole to ensure that the center of gravity of the crankshaft is located on the central axis of the crankshaft.

6. The rotor pump body structure according to claim 1, characterized in that, The crankshaft is provided with an oil outlet channel, and the sliding vane groove is connected to the oil outlet channel.

7. The rotor pump body structure according to claim 6, characterized in that, Also includes: An oil guide plate is installed in the oil outlet channel of the crankshaft.

8. A compressor, characterized in that, include: The rotor pump body structure as described in any one of claims 1-7.

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