Rotor type pump body structure and compressor

Abstract

The rotor type pump body structure comprises an upper flange, a lower flange, a crankshaft, an air cylinder and two sliding piece assemblies, the air cylinder is arranged between the upper flange and the lower flange, the crankshaft is rotationally installed in the upper flange, the air cylinder and the lower flange, a compression cavity is formed in the air cylinder, and the two sliding piece assemblies are arranged in the compression cavity. The crankshaft and the air cylinder are both provided with sliding piece grooves communicated with the compression cavity, one ends of the two sliding piece assemblies are installed in the two sliding piece grooves in a reciprocating motion mode respectively, the other ends of the two sliding piece assemblies extend out of the sliding piece grooves and can make contact with or be separated from the sliding piece grooves along with rotation of the crankshaft, and the crankshaft is a concentric shaft. The crankshaft is a concentric shaft, so that the influence of an eccentric structure on dynamic and static balance of the pump body is reduced, and the stability of the pump body is enhanced. Meanwhile, a double-sliding-piece structure is used, the movement stroke of the sliding pieces is reduced, and the lubricating effect is improved. In addition, a roller is omitted, a relative kinematic pair of the pump body is reduced, and the power and the machining cost of the compressor are reduced.

Description

Technical Field

[0001] The present invention relates to the technical field of compressors, and in particular to a rotor type pump body structure and a compressor. Background Art

[0002] In the field of refrigeration and air conditioning, rolling rotor compressors have been widely used as efficient and compact compression equipment. The basic principle is that the eccentric crankshaft drives the roller to make circular motion in the cylinder, and the sliding vane is used to divide the cylinder into a high-pressure chamber and a low-pressure chamber. As the roller rotates, the gas is compressed and discharged in the high-pressure chamber, realizing the compression process in the refrigeration cycle. However, this traditional design faces a series of technical challenges in practical applications.

[0003] First, although the adoption of the eccentric structure can effectively achieve gas compression, it also brings about the problem of difficulty in maintaining the dynamic and static balance of the pump body. Due to the eccentric configuration of the crankshaft, it will produce greater vibration and noise when running at high speed, which will not only affect the stable operation of the equipment, but also shorten its service life.

[0004] Secondly, the support and lubrication mechanism of the vane is also one of the key factors that restrict the performance improvement of the rolling rotor compressor. In the traditional design, the vane movement stroke is long, resulting in insufficient lubrication. In addition, during the rotation of the crankshaft, the roller and the eccentric part of the crankshaft are constantly worn, resulting in a significant reduction in the service life of the roller and the crankshaft. Summary of the invention

[0005] The object of the present invention is to provide a rotor type pump body structure and a compressor, aiming to solve the problems of the existing compressor pump body being difficult to maintain dynamic and static balance and the long movement stroke of the sliding vane.

[0006] An embodiment of the present invention provides a rotor pump body structure, comprising: an upper flange, a lower flange, a crankshaft, a cylinder and two vane assemblies, wherein the cylinder is arranged between the upper flange and the lower flange, the crankshaft is rotatably installed in the upper flange, the cylinder and the lower flange, a compression chamber is arranged in the cylinder, and vane grooves connected to the compression chamber are arranged on the crankshaft and the cylinder, one ends of the two vane assemblies are respectively reciprocatingly installed in the two vane grooves, and the other ends of the two vane assemblies extend out of the vane grooves and can be contacted or separated with the rotation of the crankshaft, wherein the crankshaft is a concentric shaft.

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

[0008] Furthermore, each of the slide assemblies includes: a slide and an elastic member, one end of the elastic member abuts against one end of the slide, the other end of the elastic member abuts against the slide groove, and the other end of the slide extends out of the slide groove.

[0009] Furthermore, each of the sliding vane assemblies includes a plurality of the elastic members, and the plurality of the elastic members are distributed along the axial direction of the crankshaft.

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

[0011] Furthermore, an outwardly convex arc portion is provided at the other end of the slide.

[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-shaped portion of the slide is A, the radius of the arc-shaped portion of the slide is R, and it satisfies: (Dd) / 2<2*(RR*cos(A / 2)).

[0013] Furthermore, the crankshaft is provided with at least one balancing hole for ensuring that the center of gravity of the crankshaft is located on the central axis of the crankshaft.

[0014] Furthermore, an oil outlet channel is provided on the crankshaft, and the vane groove is communicated with 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] An embodiment of the present invention further provides a compressor, comprising: the above-mentioned rotor type pump body structure.

[0017] The present invention 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 vane assemblies. The cylinder is arranged between the upper flange and the lower flange. The crankshaft is rotatably installed in the upper flange, the cylinder and the lower flange. A compression chamber is arranged in the cylinder. The crankshaft and the cylinder are both provided with vane grooves connected with the compression chamber. One end of the two vane assemblies is respectively reciprocated and installed in the two vane grooves. The other ends of the two vane assemblies extend out of the vane grooves and can contact or separate with the rotation of the crankshaft, wherein the crankshaft is a concentric shaft. The crankshaft of the present invention is a concentric shaft, which reduces the influence of the eccentric structure on the dynamic and static balance of the pump body and enhances the stability of the pump body. At the same time, the use of a double vane structure reduces the movement stroke of the vane and improves the lubrication effect. In addition, the roller is cancelled, a relative motion pair of the pump body is reduced, the compressor power and processing cost are reduced, and the continuous wear between the roller and the eccentric part of the crankshaft is avoided, thereby improving the service life of the crankshaft. BRIEF DESCRIPTION OF THE DRAWINGS

[0018] In order to more clearly illustrate the technical solutions of the embodiments of the present invention, the accompanying drawings required for use in the description of the embodiments will be briefly introduced below. Obviously, the accompanying drawings described below are some embodiments of the present invention. For ordinary technicians in this field, other accompanying drawings can be obtained based on these accompanying drawings without paying any creative work.

[0019] Figure 1 It is a structural schematic diagram of a rotor type pump body structure;

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

[0021] Figure 3 It is the structural schematic diagram of the cylinder;

[0022] Figure 4 is a cross-sectional schematic diagram of a cylinder;

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

[0024] Figure 6 is a schematic diagram of the first process of the sliding plate contact;

[0025] Figure 7 is a schematic diagram of the second process of the sliding plate contact;

[0026] Figure 8 is a schematic diagram of the third process of the sliding plate contact;

[0027] Fig. 9 is a schematic diagram of the fourth process of the sliding plate contact;

[0028] Fig.10 It is a structural schematic diagram of the slide from the first perspective;

[0029] Fig.11 is a structural schematic diagram of the slide from a second viewing angle;

[0030] Fig.12 It is a labeled schematic diagram of the crankshaft and cylinder;

[0031] Fig.13 is a labeled schematic diagram of a slide;

[0032] Fig.14 It is the structural schematic diagram of the pillow block;

[0033] Fig.15 It is a structural schematic diagram of a pillow block of other shapes;

[0034] Fig.16 is a cross-sectional schematic diagram of a crankshaft;

[0035] Fig.17 It is the structural schematic diagram of the lower flange;

[0036] Fig.18 It is the structural schematic diagram of the upper flange;

[0037] Description of the markings in the figure:

[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 member; 10. First limiting hole; 11. Second limiting hole; 12. Arc-shaped portion; 13. Balance hole; 14. Rotating shaft; 15. Pillow block; 16. Oil outlet channel; 17. Oil storage tank; 18. Oil outlet; 19. Oil guide plate; 20. First boss; 21. Second boss; 22. Third boss; 23. Air intake; 24. Cylinder exhaust port; 25. Positioning hole; 26. Flange oil guide groove; 27. Support portion. DETAILED DESCRIPTION

[0039] The following will be combined with the drawings in the embodiments of the present invention to clearly and completely describe the technical solutions in the embodiments of the present invention. Obviously, the described embodiments are part of the embodiments of the present invention, not all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without creative work 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 "include" and "comprises" indicate the presence of described features, integers, steps, operations, elements and / or components, but do not exclude the presence or addition of one or more other features, integers, steps, operations, elements, components and / or combinations thereof.

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

[0042] It should be further understood that the term "and / or" used in the present description and the appended claims refers to any and all possible combinations of one or more of the associated listed items, and includes these combinations.

[0043] See also Figure 1-5The present 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, wherein the cylinder 4 is arranged between the upper flange 1 and the lower flange 2, the crankshaft 3 is rotatably installed in the upper flange 1, the cylinder 4 and the lower flange 2, a compression chamber 6 is arranged in the cylinder 4, and vane grooves 7 communicating with the compression chamber 6 are arranged on the crankshaft 3 and the cylinder 4, one ends of the two vane assemblies 5 are respectively reciprocated and installed in the two vane grooves 7, and the other ends of the two vane assemblies 5 extend out of the vane grooves 7 and can be contacted or separated with the rotation of the crankshaft 3, wherein the crankshaft 3 is a concentric shaft.

[0044] The crankshaft 3 of this embodiment is a concentric shaft, which reduces the influence of the eccentric structure on the dynamic and static balance of the pump body and enhances the stability of the pump body. At the same time, the double vane structure is used to reduce the movement stroke of the vane and improve the lubrication effect. In addition, the roller is eliminated, reducing a relative motion pair of the pump body, reducing the compressor power and processing cost, and avoiding continuous wear between the roller and the eccentric part of the crankshaft 3, thereby improving the service life of the crankshaft 3.

[0045] in, Figure 6-9 Part b in the figure is a partial schematic diagram of the corresponding part a in the accompanying drawing.

[0046] In this embodiment, the cylinder 4 is connected to the upper flange 1 by screws, and the cylinder 4 is connected to the lower flange 2 by screws; or, the upper flange 1, the cylinder 4 and the lower flange 2 are connected by screws that penetrate the upper flange 1, the cylinder 4 and the lower flange 2. Screw connection is a high-strength mechanical connection method. By tightening the screws, sufficient pre-tightening force can be generated to form a tight and firm 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, the crankshaft 3 is located on the center line of the compression chamber 6 .

[0048] The design of the crankshaft 3 being located on the centerline helps to better balance the inertial force and torque fluctuation during the rotation process, thereby reducing the vibration and noise during the operation of the compressor. Designing the crankshaft 3 on the centerline of the compression chamber 6 can make the structure of the entire compressor more compact, which is conducive to reducing the volume and weight of the equipment.

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

[0050] One end of the elastic member 9 (such as a spring) abuts against the slide 8, and the other end abuts against the slide slot 7. This design enables the slide 8 to automatically return to its original position with the elastic force of the elastic member 9 after being displaced by an external force. Since the elastic member 9 has a certain elasticity and compressibility, the slide assembly 5 can adapt to a certain degree of dimensional change and installation error, reduce the requirements for installation accuracy, and improve the flexibility and versatility of the design.

[0051] The elastic member 9 includes but is not limited to springs, rubber, air cushions, etc. These materials have good elasticity and recovery, can be deformed when subjected to external force, and can return to the original shape and size after the external force disappears.

[0052] Further, each vane assembly 5 includes a plurality of elastic members 9, and the plurality of elastic members 9 are distributed along the axial direction of the crankshaft 3. For example, each vane assembly 5 includes three elastic members 9, and the three elastic members 9 are distributed along the axial direction of the crankshaft 3.

[0053] Multiple elastic members 9 distributed along the axial direction can provide a more uniform support force, which helps to reduce the shaking and deviation of the slide 8 during movement, thereby enhancing the stability of the entire assembly and making the slide 8 more stable when performing reciprocating motion. By dispersing the stress points of the elastic members 9, the load of a single elastic member 9 can be reduced, reducing the risk of fatigue damage, thereby extending the service life of the entire slide assembly 5. At the same time, multiple elastic members 9 can also play a role in mutual backup. Even if one of them fails, the other elastic members 9 can continue to work to ensure the normal operation of the machine.

[0054] In this embodiment, please refer to Figure 4 and Fig.10 A first limiting hole 10 is provided at the bottom of the slide groove 7 , a second limiting hole 11 is provided on the slide 8 , one end of the elastic member 9 abuts against the second limiting hole 11 , and the other end of the elastic member 9 abuts against the first limiting hole 10 .

[0055] The slide 8 is stably connected to the slide slot 7 by the elastic member 9, and accurate positioning is achieved by the two limiting holes. This design can effectively prevent the slide 8 from deflecting or shaking during the sliding process, and ensure its stability and accuracy at the specified position. The provision of the first limiting hole 10 and the second limiting hole 11 can ensure the correct installation of the elastic member 9 and improve the installation efficiency of the elastic member 9.

[0056] In this embodiment, the other end of the slide 8 is provided with a convex arc portion 12 (such as Fig.11 shown).

[0057] Linear contact is formed between the convex arc-shaped portion 12 and the corresponding contact surface (such as the cylinder 4 wall or the sliding vane 8), which can significantly reduce the contact area. This helps to reduce the wear of the convex arc-shaped portion 12 and the corresponding contact surface, thereby increasing the service life of the sliding vane 8 and the cylinder 4.

[0058] For further information, see Fig.12 and Fig.13 When the vane 8 rotates to a specific position, the vane 8 on the crankshaft 3 and the vane 8 on the cylinder 4 may have direct surface-to-edge contact, which will cause the crankshaft 3 to be directly stuck and unable to continue to work normally. In order to ensure that the vane 8 on the crankshaft 3 and the vane 8 on the cylinder 4 do not have direct surface-to-edge contact, it is necessary to limit the height H of the arc portion 12. Specifically, the diameter of the compression chamber 6 is D, and the maximum outer diameter of the crankshaft 3 is d; the arc angle of the arc portion 12 of the vane 8 is A, and the radius of the arc portion 12 of the vane 8 is R, and it satisfies: (Dd) / 2<2*(RR*cos(A / 2)).

[0059] By limiting (Dd) / 2<2*(RR*cos(A / 2)), when the vane 8 on the crankshaft 3 and the vane 8 on the cylinder 4 are both at the highest point, the extension distance of the vane 8 on the cylinder 4 is very small, and there will be no direct surface-to-edge contact between the vane 8 on the crankshaft 3 and the vane 8 on the cylinder 4. When the arc-shaped portions 12 on the two vanes 8 are squeezed, a smooth transition can be achieved 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 balancing hole 13 (such as Fig.14 The volume of material removed from the balancing hole 13 and the volume of material removed from the vane groove 7 on the crankshaft 3 may 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 A rotating shaft 14 and a pillow block 15 are provided on the crankshaft 3. The rotating shaft 14 and the pillow block 15 are connected. The rotating shaft 14 is rotatably installed in the upper flange 1, the cylinder 4 and the lower flange 2. The pillow block 15 is arranged in the compression chamber 6, and at least one balancing hole 13 is arranged on the pillow block 15.

[0062] The design of the balancing 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 rotation 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 balancing 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 pillow block 15 of this embodiment may be provided with one balancing hole 13 or two balancing holes 13 (eg Fig.15 As shown in b), three balancing holes 13 can also be provided (as shown in Fig.14 As shown), four balancing holes 13 can also be provided (as shown Fig.15 In addition to the above examples, the number of the balancing holes 13 of this embodiment can be determined according to the situation, and the shape of the corresponding pillow block 15 can also be determined according to the situation, which is not limited in this embodiment.

[0064] In this embodiment, the crankshaft 3 is provided with an oil outlet passage 16 (such as Fig.16 As shown), the vane groove 7 is connected to the oil outlet channel 16.

[0065] The design of connecting the oil outlet channel 16 with the vane groove 7 enables the lubricating oil to be directly and efficiently delivered to the vane groove 7 and the compression chamber 6 area. This design ensures that the vane 8 can continuously provide a limited amount of refrigeration oil to the compression chamber 6 when it reciprocates, which is beneficial to the lubrication of the pump body, reduces the friction and wear caused by insufficient lubrication, and reduces the impact of excessive refrigeration oil on the compression process. At the same time, sufficient lubricating oil can form a thicker lubricating film, which helps to further reduce the friction coefficient and improve the wear resistance of the moving parts, thereby extending the service life of the vane 8 and related parts.

[0066] Furthermore, an oil storage tank 17 (such as Fig.14 The side of the rotating shaft 14 is provided with an oil outlet 18 (as shown in Fig.16 As shown), the oil outlet 18 is communicated with the oil outlet channel 16.

[0067] The oil storage tank 17 on the pillow block 15 can store a certain amount of lubricating oil to ensure that there is sufficient supply of lubricating oil during the operation of the equipment. This design reduces the problem of poor lubrication caused by insufficient lubricating oil. The connection design 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 the lubricating oil and reduces the waste of the lubricating oil.

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

[0069] The oil guide plate 19 can effectively guide the refrigeration oil in the compressor oil pool into the pump body through the spiral principle. This design not only ensures the smooth flow of oil, but also provides the necessary lubrication for the pump body, thereby ensuring the efficient operation and long-term stability of the pump body.

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

[0071] The interference fit makes the outer diameter of the oil guide plate 19 slightly larger than the inner diameter of the oil outlet channel 16, which generates a certain amount of extrusion deformation during assembly, thereby ensuring that a tightly fitting sealing surface is formed between the oil guide plate 19 and the oil outlet channel 16. This tight fit can effectively prevent lubricating oil leakage and ensure the normal operation of the lubrication system. Due to the preload force 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 the operation of the equipment, prevent the oil guide plate 19 from loosening or falling off, and ensure 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, and the third boss 22 is provided with an air intake port 23 connected to the compression chamber 6.

[0073] The first boss 20 is connected to the second boss 21, and the end face of the first boss 20 is shorter than the end face of the second boss 21, so that the processing area of ​​fine processing can be reduced, the processing cost can be reduced, and the processing efficiency can be improved. The second boss 21 is flush with the third boss 22, and the first boss 20 and the second boss 21 are not flush in order to ensure the longitudinal safety distance of the air intake port 23, and at the same time, the weight of the component can be reduced.

[0074] Furthermore, a cylinder exhaust port 24 is provided on the inner wall of the compression chamber 6 of the cylinder 4 and is communicated with the flange exhaust port.

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

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

[0077] The positioning hole 25 provides an accurate position reference for the assembly of the cylinder 4, so that the cylinder 4 can be accurately aligned and fixed when assembled with other components. This helps to reduce errors in the assembly process and improve the assembly accuracy of the entire system.

[0078] In this embodiment, please refer to Fig.17 A flange oil guide groove 26 is provided on the lower flange 2 to lubricate the rotating shaft 14.

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

[0080] The components of this embodiment are all simple to process, and the processing accuracy can be ensured as required.

[0081] The working principle of the rotor pump structure of this embodiment is as follows: the refrigerant of the compressor enters from the air inlet 23, is compressed by the cylinder 4 and the crankshaft 3, forms high-pressure gas and is discharged from the exhaust port on the side of the cylinder 4. During the compression process, the motor drives the rotor to drive the crankshaft 3 to rotate. During the rotation of the crankshaft 3, the vane 8 on the crankshaft 3 rotates from the low point of the crankshaft 3 to the high point, and then abuts against the vane 8 on the cylinder 4 through the two arc-shaped parts 12 in a small gap and passes smoothly. Please refer to Figure 6-9 Specifically, when the sliding vane 8 on the crankshaft 3 contacts the sliding vane 8 on the cylinder 4 (such as Figure 6 As shown in FIG. 1 , as the crankshaft 3 rotates, the slide vane 8 on the crankshaft 3 and the slide vane 8 on the cylinder 4 will compress the elastic member 9. When the lowest point of the arc-shaped portion 12 on the slide vane 8 on the crankshaft 3 abuts against the highest point of the arc-shaped portion 12 on the slide vane 8 on the cylinder 4 (as shown in FIG. 1 ), the elastic member 9 will be compressed by the slide vane 8 on the crankshaft 3 and the slide vane 8 on the cylinder 4. Fig. 9 As shown), at this time, the elastic member 9 is compressed to the maximum compression state, and then the rotation of the crankshaft 3 causes the two slides 8 to break contact.

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

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

[0084] Put the elastic member 9 and the sliding plate 8 into the sliding plate groove 7 of the crankshaft 3, lubricate and fit the rotating shaft 14 of the crankshaft 3 with the inner hole of the upper flange 1;

[0085] Place the slide 8 in the slide groove 7 on the cylinder 4, then place the lower flange 2 on the cylinder 4, and then tighten it with screws.

[0086] The parts of this embodiment can be assembled according to size, and no centering equipment is needed for centering, thereby reducing the impact of pump body displacement on performance.

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

[0088] The various embodiments in the specification are described in a progressive manner, and each embodiment focuses on the differences from other embodiments. The same and similar parts between the various embodiments can be referred to each other. For the device disclosed in the embodiment, since it corresponds to the method disclosed in the embodiment, the description is relatively simple, and the relevant parts can be referred to the method part description. It should be pointed out that for ordinary technicians in this technical field, without departing from the principle of the present invention, several improvements and modifications can be made to the present invention, and these improvements and modifications also fall within the scope of protection of the claims of the present invention.

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

[0090] Inclusion, so that the process, method, article or device including a series of elements includes not only those elements, but also includes other elements not explicitly listed, or also includes elements inherent to such process, method, article or device. In the absence of more restrictions, the elements defined by the sentence "including a..." do not exclude the existence of other identical elements in the process, method, article or device including the elements.

Claims

1. A rotor pump structure, characterized in that: include: An upper flange, a lower flange, a crankshaft, a cylinder and two vane assemblies, wherein the cylinder is arranged between the upper flange and the lower flange, the crankshaft is rotatably installed in the upper flange, the cylinder and the lower flange, a compression chamber is arranged in the cylinder, and vane grooves communicating with the compression chamber are arranged on the crankshaft and the cylinder, one end of the two vane assemblies are respectively reciprocated and installed in the two vane grooves, and the other ends of the two vane assemblies extend out of the vane grooves and can be contacted or separated with the rotation of the crankshaft, wherein the crankshaft is a concentric shaft.

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

3. The rotor pump structure according to claim 1, characterized in that: Each of the slide assemblies comprises: a slide and an elastic member, one end of the elastic member abuts against one end of the slide, the other end of the elastic member abuts against the slide slot, and the other end of the slide extends out of the slide slot.

4. The rotor pump structure according to claim 3, characterized in that: Each of the sliding vane assemblies includes a plurality of the elastic members, and the plurality of the elastic members are distributed along the axial direction of the crankshaft.

5. The rotor pump structure according to claim 3, characterized in that: A first limiting hole is arranged at the bottom of the slide groove, a second limiting hole is arranged on the slide, one end of the elastic member abuts against the second limiting hole, and the other end of the elastic member abuts against the first limiting hole.

6. The rotor pump structure according to claim 3, characterized in that: The other end of the slide is provided with an outwardly convex arc portion.

7. The rotor pump structure according to claim 6, characterized in that: The diameter of the compression chamber is D, and the maximum outer diameter of the crankshaft is d; the arc angle of the arc-shaped portion of the slide vane is A, and the radius of the arc-shaped portion of the slide vane is R, and it satisfies: (Dd) / 2<2*(RR*cos(A / 2)).

8. The rotor pump structure according to claim 1, characterized in that: The crankshaft is provided with at least one balancing hole for ensuring that the center of gravity of the crankshaft is located on the central axis of the crankshaft.

9. The rotor pump structure according to claim 1, characterized in that: The crankshaft is provided with an oil outlet passage, and the sliding vane groove is communicated with the oil outlet passage.

10. The rotor pump structure according to claim 9, characterized in that: Also includes: An oil guide plate is installed in the oil outlet channel of the crankshaft.

11. A compressor, characterized in that: include: A rotor pump body structure as described in any one of claims 1 to 10.

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