Pump body assembly, compressor and air conditioner

Abstract

The application provides a pump body assembly, a compressor and an air conditioner. The pump body assembly comprises: a cylinder, the cylinder is provided with suction holes and sliding vane grooves at intervals; an upper flange, the upper flange is arranged on the cylinder and is located above the cylinder, the upper flange is provided with a backflow channel, the backflow channel penetrates the upper flange along the axial direction of the upper flange and extends along the circumferential direction of the upper flange; wherein, along the circumferential direction of the upper flange, at least one of the suction holes and the sliding vane grooves is arranged in a staggered manner with the distribution interval of the backflow channel. Through the technical scheme provided by the application, the technical problem that liquid refrigeration oil cannot be smoothly backflowed into an oil pool in the prior art can be solved.

Description

Technical Field

[0001] This invention relates to the field of compressor technology, and more specifically, to a pump assembly, a compressor, and an air conditioner. Background Technology

[0002] Currently, existing compressors mainly consist of a pump body assembly, a motor assembly, a distributor component, and a housing assembly. The housing assembly forms a sealed cavity structure, inside which the pump body assembly and motor assembly are housed. The pump body assembly mainly includes key components such as an upper flange, cylinder, crankshaft, rollers, a lower flange, and vanes. These components work together to form a high-pressure exhaust chamber and a low-pressure intake chamber. The motor assembly mainly includes a rotor assembly and a stator assembly. The lower part of the housing is an oil sump, which contains a certain amount of refrigerant oil.

[0003] For rotary compressors, the motor drives the pump crankshaft. Driven by the crankshaft's rotation, the eccentric structure causes the vanes to reciprocate within their slots, resulting in a periodic change in the compressor's suction and discharge chamber volume. This achieves the compressor's periodic suction, compression, and discharge processes. Gas discharged from the pump chamber enters the lower motor chamber, primarily flowing through the rotor's flow holes to the upper motor chamber, and then exits the compressor into the air conditioning system. The gas discharged from the pump is typically a mixture of refrigerant and refrigeration oil. During the discharge process, the gaseous lubricating oil mixed with the refrigerant impacts motor components or the oil baffle structure, causing it to liquefy and separate. The separated liquid refrigeration oil flows back to the lower motor chamber through the tangential gap between the inner wall of the casing and the outer circumference of the motor stator, and further flows back to the compressor oil sump through the perforated flow channel of the upper flange.

[0004] However, during the reflux process of liquid refrigerant oil, some liquid refrigerant oil often flows back to the intake port of the cylinder and the vane groove of the cylinder. This will result in ineffective reflux of liquid refrigerant oil, which in turn will prevent some liquid refrigerant oil from returning to the oil sump in time. This will cause the compressor oil sump to be short of oil, which will lead to insufficient oil supply to the pump body and reliability problems such as wear of friction pair parts. Summary of the Invention

[0005] The main objective of this invention 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 be smoothly returned to the oil sump.

[0006] To achieve the above objectives, according to one aspect of the present invention, a pump body assembly is provided, comprising:

[0007] The cylinder has air intake holes and sliding vane grooves spaced apart on it.

[0008] The upper flange is mounted on the cylinder and is located above the cylinder. The upper flange has a return channel that runs through the upper flange along its axial direction and extends along its circumference.

[0009] Along the circumference of the upper flange, at least one of the suction port and the sliding vane groove is offset from the distribution range of the return channel.

[0010] Furthermore, the intake port and the vane groove are spaced apart along the circumference of the cylinder;

[0011] Along the circumference of the upper flange, the distribution areas of the suction holes and sliding vane grooves are staggered with the distribution areas of the return channel.

[0012] Furthermore, the cylinder includes a cylinder body and a connecting part that are connected to each other. The connecting part protrudes from the side of the cylinder body and is provided with an intake port and a sliding vane groove. The connecting part extends circumferentially along the cylinder body.

[0013] Along the circumference of the upper flange, the distribution intervals of the connection and the return channel are staggered.

[0014] Furthermore, the upper flange includes an interconnected flange body and an exhaust valve seat; along the circumference of the upper flange, the exhaust valve seat and the distribution area of ​​the return channel are staggered.

[0015] Furthermore, the discharge volume of the pump body assembly is V, the operating frequency of the pump body assembly is f, and the flow area of ​​the return channel is S.

[0016] Wherein, 0.1≤S / (0.001Vf)≤0.6.

[0017] Furthermore, the radius of the center circle corresponding to the reflux channel is r0, the outer radius of the upper flange is R, and the maximum radial width of the reflux channel is w;

[0018] Wherein, 1-(r0+0.5w) / R≥0.05.

[0019] Furthermore, the upper flange is welded to the component to be connected; along the circumference of the upper flange, the weld joint between the upper flange and the component to be connected is staggered with the distribution area of ​​the return channel.

[0020] Furthermore, the end of the sliding vane groove is provided with a tail hole, which is a round hole with a diameter of d; the upper flange is provided with a first clearance hole corresponding to the tail hole, which is opposite to the tail hole, and is a round hole with a diameter of D.

[0021] Where d≤D≤d+0.5mm.

[0022] Furthermore, the cylinder is provided with process holes; along the circumference of the cylinder, the distribution range of the process holes and the return channel is staggered.

[0023] Furthermore, the upper flange is provided with a second clearance hole that is opposite to the process hole. Both the process hole and the second clearance hole are circular holes. The diameter of the process hole is d1, and the diameter of the second clearance hole is D1.

[0024] Where d1≤D1≤d1+0.5mm.

[0025] Furthermore, the reflux channel includes a plurality of reflux holes spaced circumferentially along the upper flange, and the distance between two reflux holes at both ends of the plurality of reflux holes forms the distribution range of the reflux channel.

[0026] According to another aspect of the present invention, a compressor is provided, comprising the pump assembly described above.

[0027] According to another aspect of the present invention, an air conditioner is provided, comprising the compressor described above.

[0028] By applying the technical solution of this invention, at least one of the suction port and the sliding vane groove is staggered with the distribution range of the return channel, the possibility of oil flowing out of the return channel entering at least one of the suction port and the sliding vane groove can be effectively reduced. This effectively reduces the ineffective return of the refrigeration oil, allowing it to smoothly return to the oil tank and ensuring that the oil tank contains reconstituted oil. Therefore, the technical solution provided by this invention solves the technical problem in the prior art where liquid refrigeration oil cannot smoothly return to the oil tank. Attached Figure Description

[0029] The accompanying drawings, which form part of this application, are used to provide a further understanding of the invention. The illustrative embodiments of the invention and their descriptions are used to explain the invention and do not constitute an undue limitation of the invention. In the drawings:

[0030] Figure 1 A schematic diagram of the upper flange provided according to an embodiment of the present invention is shown;

[0031] Figure 2 A schematic diagram of the pump body assembly provided according to an embodiment of the present invention is shown;

[0032] Figure 3 A schematic diagram of the structure of an upper flange having a first clearance hole according to an embodiment of the present invention is shown;

[0033] Figure 4 A schematic diagram of an upper flange having a first clearance hole and a second clearance hole according to an embodiment of the present invention is shown.

[0034] Figure 5A schematic diagram of the structure of an upper flange having a plurality of second clearance holes according to an embodiment of the present invention is shown;

[0035] Figure 6 A schematic diagram of the fit between the upper flange and the cylinder according to an embodiment of the present invention is shown;

[0036] Figure 7 A schematic diagram of the structural stiffness simulation of the upper flange provided according to an embodiment of the present invention is shown.

[0037] The above figures include the following reference numerals:

[0038] 10. Pump body assembly;

[0039] 11. Cylinder; 111. Intake port; 112. Sliding vane groove; 1121. Tail port; 113. Cylinder body; 114. Connecting part; 115. Process hole; 116. Exhaust port; 117. Protrusion;

[0040] 12. Upper flange; 121. Return channel; 1211. Return hole; 122. Flange body; 123. Exhaust valve seat; 1231. Flange exhaust port; 124. First clearance hole; 125. Second clearance hole; 126. Weld point. Detailed Implementation

[0041] It should be noted that, unless otherwise specified, the embodiments and features described in this application can be combined with each other. The present invention will now be described in detail with reference to the accompanying drawings and embodiments.

[0042] like Figures 1 to 6 As shown, an embodiment of the present invention provides a pump body assembly 10, which includes a cylinder 11 and an upper flange 12. The cylinder 11 is provided with a suction port 111 and a vane groove 112 spaced apart. The upper flange 12 is disposed on the cylinder 11 and is located above the cylinder 11. A return channel 121 is provided on the upper flange 12, extending axially through the upper flange 12 and circumferentially along the upper flange 12. Specifically, along the circumferential direction of the upper flange 12, at least one of the suction port 111 and the vane groove 112 is offset from the distribution area of ​​the return channel 121.

[0043] It should be noted that "at least one of the suction port 111 and the sliding vane groove 112 is misaligned with the distribution area of ​​the return channel 121 along the circumferential direction of the upper flange 12" means that at least one of the suction port and the sliding vane groove 112 is not correspondingly arranged with the return channel 121 in the circumferential direction of the upper flange 12, and there are no overlapping or intersecting sections. The definitions of the remaining misaligned arrangements in this application are all based on the above explanation.

[0044] By employing the pump assembly 10 provided in this embodiment, and by misaligning at least one of the suction port 111 and the vane groove 112 with the distribution interval of the return channel 121, the possibility of oil flowing out of the return channel 121 entering at least one of the suction port 111 and the vane groove 112 can be effectively reduced. This effectively reduces the ineffective backflow of the refrigeration oil, allowing the refrigeration oil to smoothly return to the oil tank, ensuring that the oil tank contains reconstituted oil. Therefore, the pump assembly 10 provided in this embodiment can solve the technical problem in the prior art where liquid refrigeration oil cannot smoothly return to the oil tank.

[0045] Furthermore, by adopting the above structural configuration, since both the suction port 111 and the vane groove 112 are hollow structures, and the return channel 121 is also a hollow structure, this avoids the situation where the hollow structures are relatively arranged, resulting in weaker structural strength or even increased vibration and noise. Through the optimized design of the upper flange 12 structure, the ineffective design of the upper flange 12 return channel 121 is avoided, while ensuring the rigidity of the upper flange 12 and the flow area of ​​its return channel 121. This optimizes the structural rigidity of the compressor oil return channel and the pump body assembly 10, improves the reliability of the compressor, and avoids compressor vibration and noise problems caused by insufficient rigidity.

[0046] In this embodiment, the suction port 111 and the vane groove 112 are spaced apart along the circumference of the cylinder 11. Along the circumference of the upper flange 12, the distribution areas of the suction port 111 and the vane groove 112 are staggered with the distribution area of ​​the return channel 121. This structural arrangement helps to better prevent the possibility of refrigerant oil entering the suction port 111 and the vane groove 112, avoiding ineffective oil return, and thus better ensuring that the refrigerant oil can smoothly return to the oil sump, avoiding a lack of oil in the oil sump.

[0047] Specifically, the cylinder 11 includes a cylinder body portion 113 and a connecting portion 114 connected to each other. The connecting portion 114 protrudes from the side of the cylinder body portion 113 and is provided with an air intake port 111 and a vane groove 112. The connecting portion 114 extends circumferentially along the cylinder body portion 113. Along the circumferential direction of the upper flange 12, the distribution intervals of the connecting portion 114 and the return channel 121 are staggered. This structural arrangement ensures that the solid structure containing the air intake port 111 and the vane groove 112 is the entire connecting portion 114, which is staggered from the return channel 121. This effectively prevents oil from flowing into the connecting portion 114 from the return channel 121, and further prevents refrigerant oil from flowing into the air intake port 111 and the vane groove 112 via the connecting portion 114, thus further ensuring the smooth return of refrigerant oil to the oil sump.

[0048] Specifically, the cylinder 11 is also provided with an exhaust port 116.

[0049] In this embodiment, the upper flange 12 includes a flange body 122 and an exhaust valve seat 123 connected to each other. Along the circumference of the upper flange 12, the exhaust valve seat 123 and the return channel 121 are offset in their distribution areas. With this structural arrangement, since the exhaust valve seat 123 is a recessed groove structure, it becomes a weak point in the rigidity of the upper flange 12. The return channel 121 is also a hollow structure, meaning it is also weak in rigidity. When the distribution areas of the exhaust valve seat 123 and the return channel 121 are concentrated in one area, the rigidity of that area will be weak, which is detrimental to the overall structural strength and stability of the upper flange 12. By offsetting the exhaust valve seat 123 and the upper flange 12 along the circumference of the upper flange 12, the two weak points in rigidity can be avoided from being concentrated, preventing a weak overall strength of the upper flange 12 and facilitating the improvement of the overall strength of the upper flange 12.

[0050] Specifically, a flange vent 1231 is provided on the vent valve seat 123.

[0051] Specifically, the angular 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 connecting structure at the intake port 111 and the vane groove 112 of the cylinder 11 is β. 2π-θ and α, and 2π-θ and β, do not overlap. This ensures that the return channel 121 of the upper flange 12 and the solid structure of the outer edge of the cylinder 11 (i.e., the connecting structure) do not interfere with each other, avoiding ineffective return flow while improving flange rigidity and enhancing the timely and smooth return of refrigeration lubricating oil. This ensures the oil level in the oil sump and the lubrication of the pump body, reducing the reliability risk of the compressor due to insufficient lubrication, and optimizing vibration and noise. Furthermore, the return channel 121 of the upper flange 12 reasonably avoids the weak area of ​​the upper flange 12 (near the exhaust valve seat 123), greatly improving flange rigidity and further optimizing compressor vibration and noise.

[0052] Specifically, the pump body assembly has a discharge capacity of V, an operating frequency of f, and a flow area of ​​S in the return channel 121. Where 0.1 ≤ S / (0.001Vf) ≤ 0.6. This structural design ensures that the compressor, operating at high frequencies, has a matching oil return flow area in the upper flange 12. Furthermore, it ensures that the refrigerant oil mixed in the gas, after liquefaction and separation, can return smoothly and promptly to the oil sump at the bottom of the compressor. This reduces the reliability issues caused by insufficient oil return during high-frequency operation, which could lead to oil shortage at the bottom of the oil sump and consequently insufficient lubrication of the pump body, resulting in wear of pump body parts.

[0053] Preferably, 0.24≤S / (0.001Vf)≤0.39, which can more effectively ensure that the return oil flow area of ​​the upper flange 12 is better adapted to the corresponding high-frequency operation mode.

[0054] 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 this invention is above 120Hz or much greater than 120Hz, and the maximum gas delivery volume (Vf) is greatly increased. Since the gas contains a large amount of refrigeration oil, the amount of refrigeration oil flowing with the gas delivery will inevitably increase significantly. This evaluation index S / (0.001Vf) can be simply understood as: the flow area per unit gas delivery volume. Compared with conventional compressors in the prior art, this evaluation index of the high-speed compressor will be greatly reduced (it will inevitably be smaller than the prior art and cannot achieve the same level as the prior art). If it is too small, it will cause insufficient flow area per unit, resulting in a large amount of refrigeration oil not being able to flow back smoothly. Preferably, the evaluation index should be as large as possible. However, due to the limitations of design space, the hollow area S cannot be increased indefinitely, and increasing S will inevitably lead to a decrease in flange strength, 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, resulting in poor flow return. At the same time, the design space limitations and structural strength are considered, and an optimal upper limit value is proposed to optimize the flow return problem of high-speed compressors.

[0055] In this embodiment, the radius of the central 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; wherein, 1 - (r0 + 0.5w) / R ≥ 0.05. Specifically, the upper flange 12 is used to connect to the inner wall of the housing. This arrangement ensures that there is sufficient connection width between the upper flange 12 and the part to be connected, thereby ensuring sufficient connection rigidity and thus achieving the effect of optimizing compressor vibration and noise.

[0056] Specifically, 1 - (r0 + 0.5w) / R = [R - (r0 + 0.5w)] / R = (R - R1) / R = W1 / R ≥ 0.05, where W1 is the connection between the flange and the inner wall of the casing, which is the main transmission path for compressor vibration and noise. For the high-speed compressor of this invention, the perforated area S needs to be as large as possible, but due to design space limitations, it cannot be increased indefinitely. Furthermore, increasing S would inevitably lead to a decrease in flange strength, thereby affecting the connection strength and vibration transmission of the compressor, causing vibration problems in the high-speed compressor. Here, by further constraining the W1 / R value, the lower limit of the connection stiffness between the flange and the inner wall of the casing is limited to avoid abnormal vibration and noise in the high-speed compressor due to insufficient connection stiffness.

[0057] Preferably, 1-(r0+0.5w) / R≥0.07, so as to better ensure the connection strength and rigidity of the compressor.

[0058] Specifically, the upper flange 12 is welded to the component to be connected; along the circumference of the upper flange 12, the weld joint between the upper flange 12 and the component to be connected is offset from the distribution area of ​​the return channel 121. This scheme can also be understood as the weld point 126 of the upper flange 12 being located on the solid part 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 the vibration noise of the compressor.

[0059] In this embodiment, the end of the sliding vane groove 112 is provided with a tail hole 1121, which is a circular hole with a diameter of d. The upper flange 12 is provided with a first clearance hole 124 corresponding to the tail hole 1121. The first clearance hole 124 is opposite to the tail hole 1121 and is a circular hole with a diameter of D; wherein d≤D≤d+0.5mm. This structural arrangement can maximize the effective oil return flow area of ​​the upper flange 12 while ensuring the rigidity of the upper flange 12.

[0060] Specifically, the first clearance hole 124 is axially inserted through the upper flange 12.

[0061] Preferably, in this embodiment, the axis of symmetry of the tail hole is coaxial with the axis of symmetry of the first clearance hole 124.

[0062] In this embodiment, 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 return channel 121 are staggered. This structural arrangement effectively avoids the situation where the process hole 115 and the return channel 121 overlap in the circumference, resulting in a weaker cylinder 11. It should be noted that the above arrangement can also be understood as meaning that there is no overlapping area between the return channel 121 and the corresponding cylinder 11 body parts of the process hole 115.

[0063] Specifically, the upper flange 12 is provided with a second clearance hole 125 opposite to the process hole 115. Both the process hole 115 and the clearance hole 125 are circular holes. The diameter of the process hole 115 is d1, and the diameter of the second clearance hole 125 is D1. Wherein, d1≤D1≤d1+0.5mm. With this structural arrangement, the cylinder 11 has a protrusion 117, and the process hole 115 is located on the protrusion 117. This avoids interference between the open flow channel of the upper flange 12 and the protrusion 117 where the process hole 115 of the cylinder 11 is located, thus preventing an ineffective backflow structure. This maximizes the effective oil return flow area of ​​the upper flange 12 while ensuring the rigidity of the upper flange 12.

[0064] Specifically, the second clearance hole 125 is axially inserted through the upper flange 12.

[0065] In this embodiment, the reflux channel 121 includes a plurality of reflux holes 1211 spaced circumferentially along the upper flange 12. The distance between two reflux holes 1211 at both ends of the plurality of reflux holes 1211 forms the distribution range of the reflux channel 121. When the reflux channel 121 includes a plurality of reflux holes 1211, the flow cross-section of the reflux channel 121 is the sum of the flow cross-sectional areas of the plurality of reflux holes 1211.

[0066] like Figure 7 The diagram shown is a simulation diagram of the structural stiffness of the upper flange 12 in this embodiment. The upper flange 12 in this embodiment and the upper flange in the prior art are respectively applied to specific compressor models and corresponding compressor operating conditions. According to the comparison, 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. It effectively optimizes the oil return effect while ensuring that the flange stiffness is basically the same (slightly reduced by 0.41%).

[0067]

[0068] Specifically, using the aforementioned specific model as a carrier, the experimental effects on compressor oil circulation rate, noise, and casing vibration near the upper flange under high-frequency specific operating conditions were verified. The results show that the pump body assembly of the present invention and the compressor using it can effectively optimize compressor oil circulation rate, noise, and casing vibration.

[0069]

[0070] Embodiment 2 of the present invention provides a compressor, including the pump assembly 10 provided in Embodiment 1 above. The compressor is a rolling rotor compressor, which can be a single-cylinder, double-cylinder, or multi-cylinder rotor compressor.

[0071] Embodiment 3 of the present invention provides an air conditioner, including the compressor provided in Embodiment 2 above.

[0072] As can be seen from the above description, the above embodiments of the present invention achieve the following technical effects: by optimizing the design of the upper flange structure, the ineffective design of the upper flange return channel is avoided, while ensuring the rigidity of the upper flange and the flow area of ​​its return channel, thereby optimizing the compressor oil return channel and ensuring that the return refrigerant oil can flow back to the oil sump in a timely and smooth manner. This avoids the reliability problem of insufficient oil supply to the pump body and wear of friction pair parts due to insufficient oil supply to the compressor oil sump. At the same time, it ensures the rigidity of the upper flange and avoids compressor vibration and noise problems caused by insufficient upper flange rigidity.

[0073] It should be noted that the terminology used herein is for the purpose of describing particular embodiments only and is not intended to limit the exemplary embodiments according to this application. As used herein, the singular form is intended to include the plural form as well, unless the context clearly indicates otherwise. Furthermore, it should be understood that when the terms "comprising" and / or "including" are used in this specification, they indicate the presence of features, steps, operations, devices, components, and / or combinations thereof.

[0074] Unless otherwise specifically stated, the relative arrangement, numerical expressions, and values ​​of the components and steps described in these embodiments do not limit the scope of this application. It should also be understood that, for ease of description, the dimensions of the various parts shown in the drawings are not drawn to actual scale. Techniques, methods, and devices known to those skilled in the art may not be discussed in detail, but where appropriate, such techniques, methods, and devices should be considered part of the specification. In all examples shown and discussed herein, any specific values ​​should be interpreted as merely exemplary and not as limitations. Therefore, other examples of exemplary embodiments may have different values. It should be noted that similar reference numerals and letters in the following drawings denote similar items; therefore, once an item is defined in one drawing, it need not be further discussed in subsequent drawings.

[0075] In the description of this application, it should be understood that the orientation or positional relationship indicated by directional terms such as "front, back, up, down, left, right", "horizontal, vertical, horizontal" and "top, bottom" is usually based on the orientation or positional relationship shown in the accompanying drawings, and is only for the convenience of describing this application and simplifying the description. Unless otherwise stated, these directional terms do not indicate or imply that the device or element referred to must have a specific orientation or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation on the scope of protection of this application; the directional terms "inner" and "outer" refer to the inner and outer contours relative to the outline of each component itself.

[0076] For ease of description, spatial relative terms such as "above," "on top of," "on the upper surface of," "above," etc., are used herein to describe the spatial positional relationship of a device or feature as shown in the figures to other devices or features. It should be understood that spatial relative terms are intended to encompass different orientations in use or operation beyond the orientation of the device as described in the figures. For example, if the device in the figures were inverted, a device described as "above" or "on top of" other devices or structures would subsequently be positioned as "below" or "under" other devices or structures. Thus, the exemplary term "above" can include both "above" and "below." The device may also be positioned in other different ways (rotated 90 degrees or in other orientations), and the spatial relative descriptions used herein will be interpreted accordingly.

[0077] Furthermore, it should be noted that the use of terms such as "first" and "second" to define components is merely for the purpose of distinguishing the corresponding components. Unless otherwise stated, the above terms have no special meaning and therefore cannot be construed as limiting the scope of protection of this application.

[0078] The above description is merely a preferred embodiment of the present invention and is not intended to limit the invention. Various modifications and variations can be made to the present invention by those skilled in the art. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of the present invention should be included within the scope of protection of the present invention.

Claims

1. A pump body assembly, characterized in that, include: The cylinder (11) is provided with an air intake hole (111) and a sliding plate groove (112) spaced apart. An upper flange (12) is provided on the cylinder (11). The upper flange (12) is located above the cylinder (11). A return channel (121) is provided on the upper flange (12). The return channel (121) passes through the upper flange (12) along the axial direction of the upper flange (12) and extends along the circumference of the upper flange (12). Along the circumference of the upper flange (12), at least one of the suction hole (111) and the sliding vane groove (112) is misaligned with the distribution range of the return channel (121); The pump body assembly has a discharge capacity of V, an operating frequency of f, and a flow area of ​​S in the return channel (121); wherein 0.1 ≤ S / (0.001Vf) ≤ 0.

6.

2. The pump body assembly according to claim 1, characterized in that, The air intake hole (111) and the sliding plate groove (112) are arranged at intervals along the circumference of the cylinder (11); Along the circumference of the upper flange (12), the distribution range of the suction hole (111) and the sliding groove (112) is offset from the distribution range of the return channel (121).

3. The pump body assembly according to claim 1, characterized in that, The cylinder (11) includes a cylinder body (113) and a connecting part (114) connected to each other. The connecting part (114) is provided on the side of the cylinder body (113). The connecting part (114) is provided with the air intake hole (111) and the slide groove (112). The connecting part (114) extends circumferentially along the cylinder body (113). Along the circumference of the upper flange (12), the distribution intervals of the connecting part (114) and the return channel (121) are staggered.

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

5. The pump body assembly according to claim 1, characterized in that, 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; Wherein, 1-(r0+0.5w) / R≥0.

05.

6. The pump body 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 weld joint of the upper flange (12) and the part to be connected is misaligned with the distribution range of the return channel (121).

7. The pump body assembly according to claim 1, characterized in that, The end of the sliding groove (112) is provided with a tail hole (1121), which is a round hole with a diameter of d; the upper flange (12) is provided with a first clearance hole (124) corresponding to the tail hole (1121), which is opposite to the tail hole (1121), and is a round hole with a diameter of D; Where d≤D≤d+0.5mm.

8. The pump body 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 process hole (115) and the distribution range of the return channel (121) are staggered.

9. The pump body assembly according to claim 8, characterized in that, The upper flange (12) is provided with a second clearance hole (125) opposite to the process hole (115). Both the process hole (115) and the second clearance hole (125) are round holes. The diameter of the process hole (115) is d1, and the diameter of the second clearance hole (125) is D1. Where d1≤D1≤d1+0.5mm.

10. The pump body assembly according to any one of claims 1 to 9, characterized in that, The return channel (121) includes a plurality of return holes (1211) arranged circumferentially along the upper flange (12), and the distance between two return holes (1211) at both ends of the plurality of return holes (1211) forms the distribution range of the return channel (121).

11. A compressor, characterized in that, Includes the pump body assembly according to any one of claims 1 to 10.

12. An air conditioner, characterized in that, Includes the compressor as described in claim 11.

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