Pump body assembly, compressor and air conditioner

Abstract

A pump body assembly, a compressor and an air conditioner. The pump body assembly comprises: a cylinder (11), on which an air suction hole (111) and a sliding vane groove (112) are provided spaced apart; an upper flange (12), which is arranged on the cylinder (11) and is located above the cylinder (11), a return channel (121) being provided in the upper flange (12), running through the upper flange (12) in the axial direction of the upper flange (12), and extending along the circumference of the upper flange (12), wherein along the circumference of the upper flange (12), at least one of the air suction hole (111) and the sliding vane groove (112) is arranged staggered with respect to the distribution zone of the return channel (121). The pump body assembly can solve the technical problem in the prior art whereby liquid refrigerant oil cannot smoothly flow back into an oil sump.

Description

Pump assemblies, compressors and air conditioners

[0001] This application claims priority to the patent application filed with the State Intellectual Property Office of China on September 25, 2023, with application number 202311249295.1 and application name “Pump body assembly, compressor and air conditioner”. Technical Field

[0002] The present application relates to the technical field of compressors, and in particular to a pump assembly, a compressor, and an air conditioner. Background Art

[0003] Currently, compressors in the prior art primarily consist of a pump assembly, a motor assembly, a liquid distributor, and a housing assembly. The housing assembly forms a sealed cavity structure, within which the pump and motor assemblies are located. The pump assembly primarily includes an upper flange, cylinder, crankshaft, rollers, a lower flange, and vanes, forming a high-pressure exhaust chamber and a low-pressure intake chamber. The motor assembly primarily comprises a rotor assembly and a stator assembly. The lower portion of the housing contains an oil reservoir, which holds a certain amount of refrigerant oil.

[0004] For rotary compressors, the motor generates driving force on the pump crankshaft. Under the driving action of the crankshaft's rotation, the eccentric structure of the crankshaft causes the vanes to reciprocate within the vane slots, causing the volume of the compressor's suction and exhaust chambers to change periodically, thus achieving the compressor's periodic suction, compression, and exhaust processes. The gas discharged from the pump cavity enters the motor's lower chamber and primarily flows through the rotor's circulation holes to the motor's upper chamber, where it is then discharged from the compressor and enters the air conditioning system. The gas discharged from the pump body is typically a mixture of refrigerant and refrigeration oil. During the exhaust circulation process, the gaseous lubricating oil mixed in the refrigerant impacts motor components or oil retaining structures, causing it to liquefy and separate. The separated liquid refrigeration oil primarily flows back to the motor's lower chamber through the cut-edge gap between the inner wall of the housing and the outer circumference of the motor stator, and further flows back to the compressor oil pool through the hollowed-out circulation channel of the upper flange.

[0005] However, during the reflux process of the liquid refrigerant oil, some of the liquid refrigerant oil often flows back to the suction hole and the slide groove of the cylinder, which will lead to ineffective reflux of the liquid refrigerant oil, and then some of the liquid refrigerant oil cannot be returned to the oil pool in time, resulting in oil shortage in the compressor oil pool, and then causing insufficient oil supply to the pump body and reliability problems such as wear of friction pair components.

[0006] Summary of the Invention

[0007] The main purpose of the present application is to provide a pump assembly, a compressor and an air conditioner to solve the technical problem in the prior art that liquid refrigeration oil cannot smoothly flow back into the oil pool.

[0008] In order to achieve the above object, according to one aspect of the present application, a pump body assembly is provided, comprising:

[0009] Cylinder, with air suction holes and sliding vane grooves arranged at intervals on the cylinder;

[0010] An upper flange is provided on the cylinder, the upper flange is located above the cylinder, and a return channel is provided on the upper flange. The return channel penetrates the upper flange along the axial direction of the upper flange and extends along the circumference of the upper flange.

[0011] Wherein, along the circumference of the upper flange, at least one of the air suction hole and the sliding vane groove is staggered with respect to the distribution interval of the return channel.

[0012] Furthermore, the air suction holes and the sliding vane grooves are arranged at intervals along the circumference of the cylinder;

[0013] Along the circumference of the upper flange, the distribution intervals of the air suction holes and the sliding vane grooves are staggered with the distribution intervals of the return channels.

[0014] Furthermore, the cylinder includes a cylinder body portion and a connecting portion connected to each other, the connecting portion protruding from the side of the cylinder body portion, the connecting portion is provided with an air suction hole and a sliding vane groove, and the connecting portion extends along the circumference of the cylinder body portion;

[0015] Wherein, along the circumference of the upper flange, the connection portion and the distribution interval of the return channel are staggered.

[0016] Furthermore, the upper flange includes a flange body and an exhaust valve seat that are connected to each other; along the circumference of the upper flange, the exhaust valve seat and the distribution interval of the return channel are staggered.

[0017] Furthermore, the exhaust volume of the pump assembly is V, the operating frequency of the pump assembly is f, and the flow area of ​​the return channel is S;

[0018] Among them, 0.1≤S / (0.001Vf)≤0.6.

[0019] Furthermore, the radius of the center circle corresponding to the return channel is r0, the outer radius of the upper flange is R, and the radial maximum width of the return channel is w;

[0020] Among them, 1-(r0+0.5w) / R≥0.05.

[0021] Furthermore, the upper flange is welded to the part to be connected; along the circumference of the upper flange, the welding point where the upper flange and the part to be connected are welded is staggered with the distribution interval of the return channel.

[0022] Furthermore, a tail hole is provided at the end of the sliding vane groove, the tail hole is a circular hole, and the diameter of the tail hole is d; a first avoidance hole corresponding to the tail hole is provided on the upper flange, the first avoidance hole is arranged opposite to the tail hole, the first avoidance hole is a circular hole, and the diameter of the first avoidance hole is D;

[0023] Among them, d≤D≤d+0.5mm.

[0024] Furthermore, a process hole is provided on the cylinder; along the circumference of the cylinder, the distribution intervals of the process hole and the reflux channel are staggered.

[0025] Furthermore, a second avoidance hole is provided on the upper flange and is arranged opposite to the process hole. Both the process hole and the second avoidance hole are circular holes. The diameter of the process hole is d1, and the diameter of the second avoidance hole is D1.

[0026] Among them, d1≤D1≤d1+0.5mm.

[0027] Furthermore, the reflux channel includes a plurality of reflux holes spaced apart along the circumference of the upper flange, and the distance between two reflux holes at both ends of the plurality of reflux holes forms a distribution interval of the reflux channel.

[0028] According to another aspect of the present application, a compressor is provided, comprising the pump body assembly provided above.

[0029] According to another aspect of the present application, an air conditioner is provided, comprising the compressor provided above.

[0030] By applying the technical solution of this application, by staggering at least one of the air intake holes and the vane slots relative to the distribution interval of the return channel, the possibility of oil flowing out of the return channel entering at least one of the air intake holes and the vane slots can be effectively reduced, thereby effectively reducing the ineffective refrigeration oil backflow, allowing the refrigeration oil to be smoothly returned to the oil pool, ensuring that the oil pool has sufficient oil. Therefore, the technical solution provided by this application can solve the technical problem in the prior art that liquid refrigeration oil cannot smoothly return to the oil pool. BRIEF DESCRIPTION OF THE DRAWINGS

[0031] The drawings that constitute part of this application are used to provide a further understanding of this application. The illustrative embodiments of this application and their descriptions are used to explain this application and do not constitute an improper limitation on this application. In the drawings:

[0032] FIG1 shows a schematic structural diagram of an upper flange provided according to an embodiment of the present application;

[0033] FIG2 shows a schematic structural diagram of a pump assembly according to an embodiment of the present application;

[0034] FIG3 shows a schematic structural diagram of an upper flange with a first avoidance hole provided according to an embodiment of the present application;

[0035] FIG4 shows a schematic structural diagram of an upper flange having a first avoidance hole and a second avoidance hole according to an embodiment of the present application;

[0036] FIG5 shows a schematic structural diagram of an upper flange with a plurality of second avoidance holes provided according to an embodiment of the present application;

[0037] FIG6 shows a schematic structural diagram of the cooperation between the upper flange and the cylinder according to an embodiment of the present application;

[0038] FIG7 shows a schematic diagram of structural stiffness simulation of an upper flange provided according to an embodiment of the present application.

[0039] Among them, the above-mentioned drawings include the following figure marks: 10. Pump body assembly; 11. Cylinder; 111. Intake hole; 112. Slide groove; 1121. Tail hole; 113. Cylinder body; 114. Connecting part; 115. Process hole; 116. Exhaust hole; 117. Protrusion; 12. Upper flange; 121. Return channel; 1211. Return hole; 122. Flange body; 123. Exhaust valve seat; 1231. Flange exhaust port; 124. First avoidance hole; 125. Second avoidance hole; 126. Welding point. DETAILED DESCRIPTION

[0040] It should be noted that, in the absence of conflict, the embodiments and features of the embodiments in this application can be combined with each other. The present application will be described in detail below with reference to the accompanying drawings and in combination with the embodiments.

[0041] As shown in Figures 1 to 6, an embodiment of the present application provides a pump body assembly 10, which includes a cylinder 11 and an upper flange 12. Cylinder 11 is provided with air intake holes 111 and vane slots 112 at intervals. Upper flange 12 is disposed on cylinder 11 and is located above cylinder 11. Upper flange 12 is provided with a return channel 121, which extends axially through upper flange 12 and circumferentially along the upper flange 12. Along the circumference of upper flange 12, at least one of air intake holes 111 and vane slots 112 is offset from the distribution interval of return channel 121.

[0042] It should be noted that "along the circumference of the upper flange 12, at least one of the air intake holes 111 and the vane slots 112 is staggered with respect to the distribution interval of the return channel 121" means that at least one of the air intake holes 111 and the vane slots 112 is not arranged in a corresponding manner with respect to the return channel 121 in the circumferential direction of the upper flange 12, and there is no overlapping or interleaving interval. The remaining definitions of staggered arrangements in this application refer to the above explanation.

[0043] The pump body assembly 10 provided in this embodiment can effectively reduce the possibility of oil flowing out of the reflux channel 121 entering at least one of the air intake hole 111 and the vane groove 112 by staggering the distribution interval of the reflux channel 121, thereby effectively reducing the ineffective reflux of the refrigerated oil, so that the refrigerated oil can be smoothly returned to the oil pool to ensure that there is sufficient oil in the oil pool. Therefore, the pump body assembly 10 provided in this embodiment can solve the technical problem in the prior art that liquid refrigerated oil cannot smoothly return to the oil pool.

[0044] In addition, with the above-mentioned structural arrangement, since the air intake hole 111 and the vane slot 112 are both hollow structures, the return channel 121 is also a hollow structure. This can avoid the situation where the hollow structures are arranged relative to each other, resulting in a weak structural strength due to the hollow structures, or even causing increased vibration and noise. By optimizing the design of the upper flange 12 structure, while avoiding the ineffective design of the return channel 121 of the upper flange 12, the rigidity of the upper flange 12 and the flow area of ​​the return channel 121 are ensured, thereby optimizing the structural rigidity of the compressor oil return channel and the pump body assembly 10, improving the reliability of the compressor, and avoiding the vibration and noise problems of the compressor caused by insufficient rigidity.

[0045] In this embodiment, the air intake holes 111 and the vane slots 112 are spaced apart along the circumference of the cylinder 11. Along the circumference of the upper flange 12, the air intake holes 111 and the vane slots 112 are staggered relative to the return channel 121. This structural arrangement effectively prevents the refrigerant oil from entering the air intake holes 111 and the vane slots 112, thus preventing ineffective oil return and ensuring smooth return of the refrigerant oil to the oil sump, thereby preventing oil shortages within the sump.

[0046] Specifically, the cylinder 11 includes a cylinder body portion 113 and a connecting portion 114 that are interconnected. The connecting portion 114 is arranged to protrude from the side of the cylinder body portion 113. The connecting portion 114 is provided with an air intake hole 111 and a vane groove 112. The connecting portion 114 extends circumferentially along the cylinder body portion 113. The connecting portion 114 is staggered with the distribution interval of the return channel 121 along the circumference of the upper flange 12. With such a structural arrangement, the physical structure where the air intake hole 111 and the vane groove 112 are located, i.e., the connecting portion 114 as a whole, is staggered with the return channel 121. This can effectively prevent the oil in the return channel 121 from flowing into the connecting portion 114, thereby better preventing the refrigerated oil from flowing into the air intake hole 111 and the vane groove 112 through the connecting portion 114, thereby further ensuring the smooth return of the refrigerated oil to the oil pool.

[0047] Specifically, the cylinder 11 is further provided with an exhaust hole 116 .

[0048] In this embodiment, the upper flange 12 includes a flange body 122 and an exhaust valve seat 123 that are interconnected. Along the circumference of the upper flange 12, the exhaust valve seat 123 and the return channel 121 are staggered. With this structural arrangement, since the exhaust valve seat 123 is a sunken groove structure, it becomes a weak rigidity area of ​​the upper flange 12. Furthermore, the return channel 121 is also a hollow structure, which means it has weak rigidity. If the exhaust valve seat 123 and the return channel 121 are concentrated in one area, the rigidity in that area will be weak, which is detrimental to the overall structural strength and stability of the upper flange 12. By staggering the exhaust valve seat 123 and the upper flange 12 along the circumference of the upper flange 12, the concentrated distribution of the two weak rigidity areas can be avoided, thus preventing the overall weak strength of the upper flange 12 and improving the overall strength of the upper flange 12.

[0049] Specifically, a flange exhaust port 1231 is provided on the exhaust valve seat 123 .

[0050] Specifically, the angle range of the return channel 121 is 2π-θ, the position span angle of the exhaust valve seat 123 is α, and the position span angle of the connection structure at the intake port 111 and the vane slot 112 of the cylinder 11 is β. 2π-θ and α, and 2π-θ and β do not have overlapping areas. This ensures that the return channel 121 of the upper flange 12 and the physical structure of the outer edge of the cylinder 11, i.e., the connection structure, do not interfere with or overlap, avoiding invalid reflux while improving flange stiffness, improving the timely and smooth return of the refrigeration lubricating oil, and ensuring the oil level in the oil pool and the oil supply and lubrication of the pump body. This reduces the reliability risk of the compressor due to insufficient lubrication while optimizing vibration and noise. Furthermore, the return channel 121 of the upper flange 12 reasonably avoids the weak stiffness area of ​​the upper flange 12 (near the exhaust valve seat 123), greatly improving flange stiffness and further optimizing compressor vibration and noise.

[0051] Specifically, the exhaust volume of the pump assembly is V, the operating frequency of the pump assembly is f, and the flow area of ​​the return channel 121 is S. Here, 0.1≤S / (0.001Vf)≤0.6. This structural arrangement enables the compressor to have a matching oil return flow area of ​​the upper flange 12 when operating at a high frequency. Furthermore, it ensures that the refrigerant oil mixed in the gas can be promptly and smoothly returned to the oil pool at the bottom of the compressor after liquefaction and separation, thereby reducing reliability issues such as oil shortage at the bottom of the oil pool due to poor oil return during high-frequency operation of the compressor, which in turn leads to insufficient oil supply and lubrication of the pump body and causes wear of pump body parts.

[0052] Preferably, 0.24≤S / (0.001Vf)≤0.39, which can more effectively ensure that the oil return flow area of ​​the upper flange 12 is more compatible with the corresponding high-frequency operation mode.

[0053] It should be noted that the maximum operating frequency of conventional compressors in the prior art is basically around 120Hz, while the maximum operating frequency of the high-speed compressor of the present application is above 120Hz or much greater than 120Hz, and the maximum gas output (Vf) is greatly improved. Since the gas contains a large amount of refrigerant oil, the refrigerant oil flowing with the gas output must increase significantly. The evaluation index S / (0.001Vf) can be briefly understood as: the flow area per unit gas output. Compared with the conventional compressors in the prior art, the evaluation index of the high-speed compressor will be greatly reduced (it must be smaller than the prior art and cannot be at the same level as the prior art). If it is too small, it will cause insufficient unit flow area, resulting in a large amount of refrigerant oil unable to flow back smoothly. Preferably, the evaluation index should be as large as possible. However, due to the limitation of design space, the hollow area S cannot be increased indefinitely, and increasing S will inevitably cause the flange strength to deteriorate, which in turn affects the connection strength and vibration transmission of the compressor, causing vibration problems in high-speed compressors. Here, an optimal range is given to limit the lower limit of the evaluation index so that the unit flow area is not too small to cause poor circulation and oil return. The design space limitation and structural strength are simultaneously considered to propose an optimal upper limit value, thereby optimizing the circulation and reflux problem of high-speed compressors.

[0054] In this embodiment, the radius of the center circle corresponding to the return channel 121 is r0, the outer radius of the upper flange 12 is R, and the maximum radial width of the return channel 121 is w; where 1-(r0 + 0.5w) / R ≥ 0.05. Specifically, the upper flange 12 is used to connect to the inner wall of the housing. This configuration effectively optimizes the connection width between the upper flange 12 and the connected component, thereby ensuring sufficient connection rigidity and thereby optimizing compressor vibration and noise.

[0055] Specifically, 1-(r0+0.5w) / R=[R-(r0+0.5w)] / R=(R-R1) / R=W1 / R≥0.05, W1 is the connection entity between the flange and the inner wall of the shell, and is the main transmission path of the compressor vibration noise. For the high-speed compressor of this application, the hollow area S needs to be as large as possible, but it cannot be increased indefinitely due to design space limitations, and increasing S will inevitably cause the flange strength to deteriorate, thereby affecting the connection strength and vibration transmission of the compressor, causing high-speed compressor vibration problems. Here, by further constraining the W1 / R value, the lower limit of the connection stiffness between the flange and the inner wall of the shell is limited to avoid the problem of abnormal vibration noise of the high-speed compressor due to insufficient connection stiffness.

[0056] Preferably, 1-(r0+0.5w) / R≥0.07, so as to better ensure the connection strength and rigidity of the compressor.

[0057] Specifically, the upper flange 12 is welded to the component to be connected; along the circumference of the upper flange 12, the welds are offset from the distribution interval of the return channel 121. This solution can also be understood as the weld points 126 of the upper flange 12 being located on the solid portion of the upper flange 12, with the component to be connected being the housing. This effectively improves the connection rigidity between the flange and the housing, thereby reducing vibration and noise in the compressor.

[0058] In this embodiment, a tail hole 1121 is provided at the end of the sliding vane slot 112. Tail hole 1121 is a circular hole with a diameter of d. A first avoidance hole 124 is provided on the upper flange 12, corresponding to tail hole 1121. The first avoidance hole 124 is arranged opposite to tail hole 1121 and is a circular hole with a diameter of D. Where d ≤ D ≤ d + 0.5 mm. This structural arrangement maximizes the effective oil return flow area of ​​the upper flange 12 while ensuring its rigidity.

[0059] Specifically, the first avoidance hole 124 is provided axially through the upper flange 12 .

[0060] Preferably, the symmetry axis of the tail hole in this embodiment is coaxial with the symmetry axis of the first avoidance hole 124 .

[0061] In this embodiment, the cylinder 11 is provided with a process hole 115. Along the circumference of the cylinder 11, the process hole 115 and the return channel 121 are staggered in their distribution intervals. This structural arrangement effectively avoids circumferential overlap between the process hole 115 and the return channel 121, which could weaken the cylinder 11. It should be noted that this arrangement can also be understood as meaning that there is no overlap between the return channel 121 and the solid portion of the cylinder 11 corresponding to the process hole 115.

[0062] Specifically, the upper flange 12 is provided with a second avoidance hole 125, which is arranged opposite the process hole 115. Both the process hole 115 and the second avoidance hole 125 are circular holes, with the diameter of the process hole 115 being d1 and the diameter of the second avoidance hole 125 being D1. Where d1≤D1≤d1+0.5mm. With this structural arrangement, the cylinder 11 has a raised portion 117, and the process hole 115 is arranged on the raised portion 117. This prevents interference between the hollowed-out flow channel of the upper flange 12 and the raised portion 117 where the process hole 115 of the cylinder 11 is located, which could result in an ineffective return flow structure. This maximizes the effective oil return flow area of ​​the upper flange 12 while ensuring the rigidity of the upper flange 12.

[0063] Specifically, the second avoidance hole 125 is provided axially through the upper flange 12 .

[0064] In this embodiment, the return channel 121 includes a plurality of return holes 1211 spaced apart along the circumference of the upper flange 12. The distance between two return holes 1211 at either end of the plurality of return holes 1211 defines the distribution range of the return channel 121. When the return channel 121 includes a plurality of return holes 1211, the flow cross-section of the return channel 121 is the sum of the flow cross-section areas of the plurality of return holes 1211.

[0065] Figure 7 shows a schematic diagram of the structural stiffness simulation of the upper flange 12 in this embodiment. The upper flange 12 in this embodiment and the upper flange in the prior art are applied to specific compressor models and corresponding to specific compressor operating conditions. The comparison shows that the upper flange 12 in this application can achieve a 39.67% increase in oil return flow area and a 31.51% increase in oil return volume compared to the upper flange in the prior art, effectively optimizing the oil return effect while ensuring that the flange stiffness is essentially the same (slightly reduced by 0.41%).

[0066] Specifically, using the aforementioned specific model as a testbed, we conducted tests to verify the compressor's oil circulation rate, noise, and housing vibration near the upper flange under specific high-frequency operating conditions. The results demonstrated that the pump assembly and the compressor using it can effectively optimize the compressor's oil circulation rate, noise, and housing vibration.

[0067] The second embodiment of the present application provides a compressor, including the pump assembly 10 provided in the first embodiment. The compressor is a rolling rotor compressor, which can be a single-cylinder, double-cylinder, or multi-cylinder rotor compressor.

[0068] A third embodiment of the present application provides an air conditioner, comprising the compressor provided in the second embodiment above.

[0069] From the above description, it can be seen that the above-mentioned embodiments of the present application achieve the following technical effects: through the optimized design of the upper flange structure, the invalid design of the upper flange return channel is avoided, while the upper flange stiffness and the flow area of ​​the return channel are ensured, thereby optimizing the compressor return oil channel, ensuring that the return refrigeration oil can flow back to the oil pool in a timely and smooth manner, avoiding the lack of oil in the compressor oil pool, and causing insufficient oil supply to the pump body and resulting in wear of friction pair components. Reliability problems, at the same time, ensure the stiffness of the upper flange, and avoid compressor vibration and noise problems caused by insufficient stiffness of the upper flange.

[0070] It should be noted that the terms used herein are only for describing specific embodiments and are not intended to limit the exemplary embodiments according to the present application. As used herein, unless the context clearly indicates otherwise, the singular form is also intended to include the plural form. In addition, it should be understood that when the terms "comprise" and / or "include" are used in this specification, they indicate the presence of features, steps, operations, devices, components and / or combinations thereof.

[0071] Unless otherwise specifically stated, the relative arrangement of the parts and steps, numerical expressions and numerical values ​​set forth in these embodiments do not limit the scope of the present application. At the same time, it should be understood that, for ease of description, the sizes of the various parts shown in the drawings are not drawn according to actual proportional relationships. The techniques, methods and equipment known to those of ordinary skill in the relevant art may not be discussed in detail, but where appropriate, the techniques, methods and equipment should be considered as part of the authorization specification. In all examples shown and discussed here, any specific values ​​should be interpreted as being merely exemplary and not as limitations. Therefore, other examples of the exemplary embodiments may have different values. It should be noted that similar numbers and letters represent similar items in the following figures, and therefore, once an item is defined in one figure, it does not need to be further discussed in subsequent figures.

[0072] In the description of this application, it should be understood that the directions or positional relationships indicated by directional words such as "front, back, up, down, left, right", "horizontal, vertical, vertical, horizontal" and "top, bottom" are usually based on the directions or positional relationships shown in the accompanying drawings. They are only for the convenience of describing this application and simplifying the description. Unless otherwise specified, these directional words do not indicate or imply that the device or element referred to must have a specific direction or be constructed and operated in a specific direction. Therefore, they cannot be understood as limiting the scope of protection of this application; the directional words "inside and outside" refer to the inside and outside relative to the outline of each component itself.

[0073] For ease of description, spatially relative terms such as "above", "above", "on the upper surface of", "above", etc. may be used herein to describe the spatial positional relationship of a device or feature to other devices or features as shown in the figures. It should be understood that spatially relative terms are intended to include different orientations of the device in use or operation in addition to the orientation described in the figures. For example, if the device in the drawings is inverted, the device described as "above other devices or structures" or "above other devices or structures" will be positioned as "below other devices or structures" or "below other devices or structures". Thus, the exemplary term "above" can include both "above" and "below". The device can also be positioned in other different ways (rotated 90 degrees or in other orientations), and the spatially relative descriptions used here are interpreted accordingly.

[0074] In addition, it should be noted that the use of terms such as "first" and "second" to limit components is only for the convenience of distinguishing the corresponding components. Unless otherwise stated, the above terms have no special meaning and therefore cannot be understood as limiting the scope of protection of this application.

[0075] The above description is merely a preferred embodiment of the present application and is not intended to limit the present application. Various modifications and variations are possible for those skilled in the art. Any modifications, equivalent substitutions, or improvements made within the spirit and principles of the present application shall be included within the scope of protection of the present application.

Claims

1. A pump assembly, characterized in that: include: A cylinder (11), wherein the cylinder (11) is provided with air suction holes (111) and sliding vane grooves (112) at intervals; an upper flange (12) disposed on the cylinder (11); the upper flange (12) is located above the cylinder (11); a return channel (121) is disposed on the upper flange (12); the return channel (121) penetrates the upper flange (12) along the axial direction of the upper flange (12); and the return channel (121) extends along the circumferential direction of the upper flange (12); Wherein, along the circumference of the upper flange (12), at least one of the air suction hole (111) and the sliding vane groove (112) is arranged in a staggered manner with respect to the distribution interval of the reflux channel (121).

2. The pump assembly according to claim 1, characterized in that: The air suction holes (111) and the vane grooves (112) are arranged at intervals along the circumference of the cylinder (11); Along the circumference of the upper flange (12), the distribution intervals of the air suction holes (111) and the sliding vane grooves (112) are staggered with the distribution interval of the return channel (121).

3. The pump assembly according to claim 1, characterized in that: The cylinder (11) comprises a cylinder body (113) and a connecting part (114) which are connected to each other, the connecting part (114) is arranged protruding from the side of the cylinder body (113), the connecting part (114) is provided with the air suction hole (111) and the sliding vane groove (112), and the connecting part (114) extends along the circumference of the cylinder body (113); Wherein, along the circumference of the upper flange (12), the connection portion (114) and the distribution interval of the reflux channel (121) are staggered.

4. The pump assembly according to claim 1, characterized in that: The upper flange (12) comprises a flange body (122) and an exhaust valve seat (123) which are connected to each other; along the circumference of the upper flange (12), the exhaust valve seat (123) and the distribution interval of the return channel (121) are staggered.

5. The pump assembly according to claim 1, characterized in that: The exhaust volume of the pump assembly is V, the operating frequency of the pump assembly is f, and the flow area of ​​the reflux channel (121) is S; Among them, 0.1≤S / (0.001Vf)≤0.

6.

6. The pump assembly according to claim 1, characterized in that: The radius of the center circle corresponding to the reflux channel (121) is r0, the outer radius of the upper flange (12) is R, and the maximum radial width of the reflux channel (121) is w; Among them, 1-(r0+0.5w) / R≥0.

05.

7. The pump assembly according to claim 1, characterized in that: The upper flange (12) is welded to the part to be connected; along the circumference of the upper flange (12), the welding point where the upper flange (12) is welded to the part to be connected is staggered with the distribution interval of the return channel (121).

8. The pump assembly according to claim 1, characterized in that: The end of the sliding plate groove (112) is provided with a tail hole (1121), the tail hole (1121) is a circular hole, and the diameter of the tail hole (1121) is d; the upper flange (12) is provided with a first avoidance hole (124) corresponding to the tail hole (1121), the first avoidance hole (124) is arranged opposite to the tail hole (1121), the first avoidance hole (124) is a circular hole, and the diameter of the first avoidance hole (124) is D; Among them, d≤D≤d+0.5mm.

9. The pump assembly according to claim 1, characterized in that: The cylinder (11) is provided with a process hole (115); along the circumference of the cylinder (11), the distribution intervals of the process hole (115) and the reflux channel (121) are staggered.

10. The pump assembly according to claim 9, characterized in that: The upper flange (12) is provided with a second avoidance hole (125) arranged opposite to the process hole (115); the process hole (115) and the second avoidance hole (125) are both circular holes; the diameter of the process hole (115) is d1, and the diameter of the second avoidance hole (125) is D1; Among them, d1≤D1≤d1+0.5mm.

11. The pump assembly according to any one of claims 1 to 10, characterized in that: The reflux channel (121) comprises a plurality of reflux holes (1211) arranged at intervals along the circumference of the upper flange (12), and the distance between two reflux holes (1211) at two ends of the plurality of reflux holes (1211) forms a distribution interval of the reflux channel (121).

12. A compressor, characterized in that: A pump body assembly comprising any one of claims 1 to 11.

13. An air conditioner, characterized in that: Comprising the compressor as claimed in claim 12.

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