A pump body oil circuit structure, a pump body, a compressor, and an air conditioner

Abstract

The present invention provides a pump body oil circuit structure, a pump body, a compressor and an air conditioner. The pump body oil circuit structure includes: an upper flange, on the inner wall of the shaft hole of the upper flange, there are an upper oil groove, an oil storage groove and a lower oil groove. The upper oil groove extends upward until its upper end communicates with the oil storage groove. The oil storage groove extends along the horizontal direction on the inner wall of the upper flange. The upper end of the lower oil groove communicates with the oil storage groove to be able to suck oil from the oil storage groove. The lower oil groove extends downward. Inside the upper flange, there is also an oil return inclined hole which extends obliquely downward, and the upper end of the oil return inclined hole communicates with the lower end of the lower oil groove. The lower end of the oil return inclined hole extends to the lower end face of the upper flange to be able to lead the oil to an oil pool below the upper flange. The minimum distance between the oil return inclined hole and the annular flexible groove is a, and a ≥ 1 mm. According to the present invention, the oil spitting rate can be minimized to the greatest extent, and the problem that the setting of the oil return flow passage destroys the load-bearing oil film between the crankshaft and the flange friction pair can also be solved.

Description

Technical Field

[0001] The present invention relates to the technical field of compressors, and particularly relates to a pump body oil circuit structure, a pump body, a compressor and an air conditioner. Background Art

[0002] Conventional rolling rotor compressors mainly consist of a pump body assembly, a motor assembly, a liquid distributor component, a housing assembly, an upper cover, a lower cover, etc. The housing assembly and the upper and lower covers cooperate to form a closed structure. The interior of the housing mainly consists of two major parts: a pump body assembly and a motor assembly. The pump body assembly includes main components such as an upper flange, a cylinder, a crankshaft, a roller, a lower flange, etc. Each component cooperates with each other to form a closed cavity. The motor assembly includes a stator assembly and a rotor assembly. The rotary compressor generates a driving force on the pump body crankshaft through the electromagnetic force generated between the motor rotor assembly and the stator assembly. Under the driving action of the rotating crankshaft, the volume of the pump body cavity changes continuously, and it sucks, compresses, and discharges gas periodically. The oil-gas mixture discharged from the pump body cavity enters the lower cavity space of the motor, then passes through the motor flow channel holes to the upper cavity of the motor, and then is discharged from the compressor into the air conditioning system.

[0003] The lubrication between the friction pairs of the compressor pump body mainly relies on the oil circuit in the pump body to pump lubricating oil to the contact surfaces of the moving parts, so as to achieve the effects of lubrication, cooling, and heat dissipation. The oil circuit structure of the main and auxiliary bearings of a conventional rolling rotor compressor is as follows: The crankshaft is provided with a central oil hole. The roots of the long and short axes of the crankshaft are respectively designed with side oil holes that communicate with the central oil hole of the crankshaft. A pump oil device is assembled in the central oil hole of the crankshaft. The inner circular surfaces of the upper flange and the lower flange are respectively provided with spiral oil grooves. A certain amount of lubricating oil is filled in the lower part of the housing. When the compressor operates, under the action of the pump oil device in the central oil hole of the crankshaft, the lubricating oil in the bottom oil sump is pumped into the central oil hole, and is respectively pumped to the ends of the inner circular surfaces of the lower flange and the upper flange through the side oil holes at the roots of the long and short axes of the crankshaft, and then is respectively pumped to the surfaces of the friction pairs (main and auxiliary bearings) between the upper and lower flanges and the long and short axes of the crankshaft through the spiral oil grooves on the upper and lower flanges, thereby realizing the oil circuit lubrication of the main and auxiliary bearings.

[0004] When the compressor operates at high frequency, a large amount of heat energy is generated by the friction of the moving parts. If the amount of pumped oil is insufficient, it will lead to insufficient heat dissipation, rapid temperature rise of the pump body, heating of the working cavity of the cylinder, and a decrease in volumetric efficiency. At the same time, the exhaust temperature rises rapidly, resulting in a decrease in motor efficiency, and ultimately leading to a decline in compressor performance. At the same time, at high frequency, the requirements for lubrication between the contact surfaces of the moving parts are higher, especially between the crankshaft and the upper flange, and sufficient lubricating oil needs to be provided for lubrication.

[0005] In addition, when the compressor is running, the cavity is filled with oil droplets. One of the main sources of these oil droplets is that the lubricating oil path of the pump body is directly connected to the lower cavity of the motor. Under the action of centrifugal force and gas force, the oil in the lubricating oil path enters the upper cavity of the motor and then is discharged into the system, resulting in a high oil spitting rate during high-frequency operation of the compressor. While the performance of the compressor is reduced, the reliability risk of oil shortage inside the compressor is increased.

[0006] Due to the technical problems in the compressors in the prior art, such as a large amount of lubricating oil pumped out from the spiral oil groove on the upper flange of the pump body lubricating oil path entering the lower cavity of the motor, and only relying on gravity to flow back, most of it is carried into the upper cavity of the motor by the impact of high-speed air flow and discharged from the compressor housing, resulting in an excessively high oil spitting rate of the compressor. Therefore, the present invention researches and designs a pump body oil path structure, a pump body, a compressor and an air conditioner. Summary of the Invention

[0007] Therefore, the technical problem to be solved by the present invention is to overcome the defect that the lubricating oil in the compressors in the prior art is easily carried into the upper cavity of the motor by the impact of high-speed air flow and discharged from the compressor housing, resulting in an excessively high oil spitting rate of the compressor, so as to provide a pump body oil path structure, a pump body, a compressor and an air conditioner.

[0008] To solve the above problems, the present invention provides a pump body oil path structure, which includes:

[0009] An upper flange, on the inner wall of the shaft hole of the upper flange, there are an upper oil groove, an oil storage groove and a lower oil groove. The lower end of the upper oil groove can be used to suck oil, the upper oil groove extends upward until its upper end communicates with the oil storage groove, the oil storage groove extends horizontally on the inner wall of the upper flange, the upper end of the lower oil groove communicates with the oil storage groove to suck oil from the oil storage groove, the lower oil groove extends downward, and there is also an oil return inclined hole inside the upper flange. The oil return inclined hole extends obliquely downward, and the upper end of the oil return inclined hole communicates with the lower end of the lower oil groove. The lower end of the oil return inclined hole extends to the lower end face of the upper flange to export the oil to the oil pool below the upper flange;

[0010] There is also an annular flexible groove on the upper flange. The annular flexible groove is located on the outer periphery of the inner wall of the shaft hole and is spaced from the inner wall of the shaft hole by a preset distance. The connection end of the oil return inclined hole and the lower oil groove is above the upper end of the annular flexible groove; and the minimum distance between the oil return inclined hole and the annular flexible groove is a, and a≥1mm; the upper flange includes a flange disc and a shaft diameter part. The shaft diameter part is located on the upper end face of the flange disc and extends upward, and the outer peripheral surface of the shaft diameter part intersects with the upper end face of the flange disc at a bending part. The minimum distance between the outer peripheral surface of the shaft diameter part, the bending part and the upper end face of the flange disc and the oil return inclined hole is b, and b≥1mm.

[0011] In some embodiments, it further includes a crankshaft which penetrates into the shaft hole of the upper flange;

[0012] A central oil hole and side oil holes are provided inside the crankshaft. The central oil hole extends along the axial direction of the crankshaft, and the side oil holes extend along the radial direction of the crankshaft. One end of the side oil hole communicates with the central oil hole, and the other end extends to communicate with the radial outside of the crankshaft. And the side oil holes face the inner wall of the upper flange so as to be able to convey oil into the upper oil groove;

[0013] The distance between the lower end of the lower oil groove and the lower end face of the flange is c. The lower end of the lower oil groove is higher than the upper end of the annular flexible groove, and the lower end of the lower oil groove is higher than the upper end of the side oil hole.

[0014] In some embodiments, the circumferential arrangement position of the oil storage groove is in the non-bearing area of the pump body. In the projection plane of the axial end face of the upper flange, the projection point of the central axis of the upper flange is O, and the projection point of the central axis of the exhaust hole of the upper flange is M1. The connection line of O and M1 is L1. The projection point of the starting edge end of the oil storage groove along the rotation direction of the pump body is M2, and the projection point of the terminating edge end is M3. The connection lines of the projection point O with M2 and M3 are L2 and L3 respectively. And along the rotation direction of the pump body, the included angle between L2 and L1 is set as α, and the included angle between L3 and L1 is set as β. The parameters α and β satisfy: 80°≤β≤150°, 0°≤α≤60°.

[0015] In some embodiments, it further includes an oil return groove and a cylinder. The axial upper end face of the cylinder is connected to the axial lower end face of the flange of the upper flange. The oil return groove is opened on the upper flange and / or the cylinder. An upper flange hollow cavity is axially opened on the flange. The upper flange hollow cavity penetrates from the upper end face of the flange to its lower end face. One end of the oil return groove communicates with the oil return inclined hole, and the other end communicates with the upper flange hollow cavity.

[0016] In some embodiments, the oil return groove is arranged on the lower end face of the upper flange and extends along the radial direction; the minimum distance between the lower end of the oil return inclined hole and the inner circular surface of the cylinder is d, and the minimum distance between the end of the oil return groove communicating with the oil return inclined hole and the inner circular surface of the cylinder is e. And d≥1.5mm, e≥1.5mm, and d = e.

[0017] In some embodiments, the oil return groove is arranged on the axial upper end face of the cylinder and extends along the radial direction, and the lower end of the oil return inclined hole extends to the lower end face of the flange.

[0018] In some embodiments, the oil return groove is provided inside the upper flange. The oil return groove is located between the upper end face and the lower end face of the flange plate, and the oil return groove extends in the radial direction. The lower end of the oil return inclined hole extends to the lower end face of the flange plate.

[0019] In some embodiments, part of the oil return groove is formed on the lower end face of the upper flange, and part of it is formed on the upper axial end face of the cylinder. The part of the oil return groove formed on the upper flange and the part of the oil return groove formed on the cylinder are opposite and communicated with each other, splicing to form a complete oil return groove.

[0020] In some embodiments, the oil return inclined hole is a straight hole, which is inclined with respect to both the horizontal direction and the vertical direction. The extending direction of the oil return inclined hole forms an angle between (0, 90°) with the axial direction of the upper flange, and the extending direction of the oil return inclined hole forms an angle between (0, 90°) with the horizontal direction. The axial direction of the upper flange is along the vertical direction, and the axial end face of the upper flange is along the horizontal direction.

[0021] In some embodiments, an annular flexible groove is further provided on the upper flange. The annular flexible groove is located on the outer periphery of the inner wall of the shaft hole and is spaced from the inner wall of the shaft hole by a preset distance. The connection end of the oil return inclined hole and the lower oil groove is located above the upper end of the annular flexible groove.

[0022] In some embodiments, the upper oil groove is a spiral oil groove structure formed on the inner wall of the upper flange. The upper oil groove extends spirally upward from its lower end to its upper end, and the rotation direction of the upper oil groove from its lower end to its upper end is the same as the rotation direction of the crankshaft. The upper flange is sleeved on the outer periphery of the crankshaft; the lower oil groove is a spiral oil groove structure formed on the inner wall of the upper flange. The lower oil groove extends spirally downward from its upper end to its lower end, and the rotation direction of the lower oil groove from its upper end to its lower end is the same as the rotation direction of the crankshaft.

[0023] In some embodiments, the upper end of the upper oil groove is communicated with the first position of the oil storage groove, the upper end of the lower oil groove is communicated with the second position of the oil storage groove, and the first position and the second position are located at different positions.

[0024] In some embodiments, the oil storage groove includes a first end and a second end along the horizontal direction. The first position is arranged closer to the first end relative to the second end or the first position coincides with the first end. The second position is arranged closer to the second end relative to the first end or the second position coincides with the second end.

[0025] In some embodiments, it further includes a cylinder, and a first oil return hole and a second oil return hole are arranged inside the cylinder. The first oil return hole extends along the axial direction of the cylinder, and the upper end of the first oil return hole is opposite to and communicated with the lower end of the oil return inclined hole. The second oil return hole extends along the radial direction of the cylinder, and one end of the second oil return hole is communicated with the lower end of the first oil return hole, and the other end is communicated to the outside of the cylinder in the radial direction.

[0026] In some embodiments, it further includes a cylinder and a lower flange. A first oil return hole is arranged inside the cylinder. The first oil return hole extends along the axial direction of the cylinder, and the upper end of the first oil return hole is opposite to and communicated with the lower end of the oil return inclined hole. The first oil return hole axially penetrates the cylinder, so that the lower end of the first oil return hole extends to the lower end face of the cylinder;

[0027] A third oil return hole and a fourth oil return hole are arranged inside the lower flange. The third oil return hole extends along the axial direction of the lower flange, and the upper end of the third oil return hole is opposite to and communicated with the lower end of the first oil return hole. The fourth oil return hole extends along the radial direction of the lower flange, and one end of the fourth oil return hole is communicated with the lower end of the third oil return hole, and the other end is communicated to the outside of the lower flange in the radial direction.

[0028] The present invention also provides a pump body, which includes the pump body oil circuit structure described in any one of the previous items.

[0029] The present invention also provides a compressor, which includes the aforementioned pump body.

[0030] The present invention also provides an air conditioner, which includes the aforementioned compressor.

[0031] The pump body oil circuit structure, pump body, compressor and air conditioner provided by the present invention have the following beneficial effects:

[0032] By providing the structures of an oiling groove, an oil storage groove, and a lower oil groove, the present invention can effectively lubricate between the crankshaft and the upper flange through the oiling groove, store lubricating oil by using the oil storage groove, and export the lubrication downward below the upper flange through the lower oil groove, thus effectively solving the problem of excessive oil spitting rate of the compressor caused by lubricating oil entering the lower cavity of the motor upward, enabling the lubricating oil to return to below the upper flange as much as possible without being discharged, and reducing the oil spitting rate. Moreover, through the provision of the oil return inclined holes, the lubricating oil flowing back from the upper flange can be diverted to a position closer to the bottom of the oil sump, enabling the returned lubricating oil to directly enter below the oil level in the oil sump via the diversion channel, thereby optimizing the circulation of the lubricating oil path in the pump body inside the pump body, preventing the lubricating oil pumped out from the oil return flow channel from directly radially spraying onto the flange wall surface or the housing wall surface, causing the sprayed hollow cavity wall surface to splash some lubricating oil into the lower cavity of the motor and flowing out with the exhaust gas. For example, spraying radially onto the hollow cavity to avoid some lubricating oil entering the lower cavity of the motor, further improving the compressor oil spitting rate and radial vibration problems caused thereby. Therefore, it can further prevent oil discharge and minimize the oil spitting rate to the greatest extent. The present invention also sets the position of the oil return inclined holes to satisfy the minimum distances a≥1mm and b≥1mm with the outer peripheral surface of the annular flexible groove and the shaft diameter part and the upper end surface of the flange disk, which can effectively ensure that there is sufficient safety and sealing distance between the lower side of the inclined surface of the oil return inclined hole and the annular flexible groove, and sufficient safety and sealing distance between the upper side of the inclined surface of the oil return inclined hole and the outer peripheral surface of the shaft diameter part, the upper end surface of the flange disk, and the bent part, enabling both to form a sealing effect that meets the requirements for the oil return inclined holes, without affecting the structural strength of the flange entity part between the oil return inclined holes and the annular flexible groove, and without affecting the structural strength of the entity parts between the oil return inclined holes and the outer peripheral surface of the shaft diameter part and the upper end surface of the flange disk respectively, and further realizing that the oil return flow path structure avoids the oil film heavy load area of the crankshaft flange friction pair on the premise of not affecting the flexible deformation effect of the flexible groove, thereby enhancing the performance and reliability of the compressor. It solves the reliability problem in the prior art that the setting of the oil return flow path of the upper flange destroys the bearing oil film between the crankshaft and the flange friction pair, especially in the area where the contact stress between the root of the crankshaft and the flange is relatively large, resulting in wear of the root of the crankshaft due to oil film damage. BRIEF DESCRIPTION OF THE DRAWINGS

[0033] Figure 1 is a sectional view of the pump body assembly and the oil path structure of the optimal embodiment of the pump body oil path structure of the present invention;

[0034] Figure 1-1 is Figure 1 the top view structure diagram of the upper flange of the pump body assembly oil path structure in

[0035] Figure 1-2 is Figure 1 the partial enlarged view of part K in

[0036] Figure 1-3 is Figure 1 the B-B cross-sectional view;

[0037] Figure 2 is the cross-sectional view of the pump body assembly and the oil circuit structure of the alternative embodiment 1 of the pump body oil circuit structure of the present invention;

[0038] Figure 3 is the cross-sectional view of the pump body assembly and the oil circuit structure of the alternative embodiment 2 of the pump body oil circuit structure of the present invention;

[0039] Figure 4 is the cross-sectional view of the pump body assembly and the oil circuit structure of the alternative embodiment 3 of the pump body oil circuit structure of the present invention.

[0040] The reference numerals are shown as:

[0041] 1, pump body assembly; 11, upper flange; 111, flange plate; 112, shaft diameter part; 113, bent part; 114, exhaust hole; 12, cylinder; 13, crankshaft; 14, roller; 15, lower flange; 7, oil sump; 100, upper oil flow path; 1101, upper oil groove; 1301, central oil hole; 1302, side oil hole; 200, oil return channel; 1102, oil storage tank; 1103, lower oil groove; 1109, oil return inclined hole; 1105, upper flange hollow cavity; 1106, annular flexible groove; 1110, oil return groove. Detailed implementation manners

[0042] As Figure 1-4 shown, the present invention provides a pump body oil circuit structure, which includes:

[0043] An upper flange 11, on the inner wall of the shaft hole of the upper flange, there are provided an upper oil groove 1101, an oil storage tank 1102 and a lower oil groove 1103. The lower end of the upper oil groove 1101 can be used to suck oil. The upper oil groove 1101 extends upward until its upper end communicates with the oil storage tank 1102. The oil storage tank 1102 extends horizontally on the inner wall of the upper flange 11. The upper end of the lower oil groove 1103 communicates with the oil storage tank 1102 to be able to suck oil from the oil storage tank 1102. The lower oil groove 1103 extends downward. Inside the upper flange 11, there is also provided an oil return inclined hole 1109. The oil return inclined hole 1109 extends obliquely downward, and the upper end of the oil return inclined hole 1109 communicates with the lower end of the lower oil groove 1103. The lower end of the oil return inclined hole 1109 can extend to lead the oil out to the oil sump below the upper flange 11;

[0044] An annular flexible groove 1106 is further provided on the upper flange 11. The annular flexible groove 1106 is located on the outer periphery of the inner wall of the shaft hole and is spaced from the inner wall of the shaft hole by a preset distance. The connecting end of the oil return inclined hole 1109 and the lower oil groove 1103 is located above the upper end of the annular flexible groove 1106; and the minimum distance between the oil return inclined hole 1109 and the annular flexible groove 1106 is a, and a≥1mm. The upper flange 11 includes a flange plate 111 and a shaft diameter portion 112. The shaft diameter portion 112 is located on the upper end surface of the flange plate 111 and extends upward. The outer peripheral surface of the shaft diameter portion 112 intersects with the upper end surface of the flange plate 111 at a bending portion 113. The minimum distance between the outer peripheral surface of the shaft diameter portion 112, the bending portion 113 and the upper end surface of the flange plate 111 and the oil return inclined hole 1109 is b, and b≥1mm.

[0045] By setting up the structures of the oiling groove, oil storage tank and lower oil groove, the present invention can effectively lubricate between the crankshaft and the upper flange through the oiling groove, store lubricating oil by using the oil storage tank, and export the lubrication downward below the upper flange through the lower oil groove, thus effectively solving the problem of too high oil spitting rate of the compressor caused by the lubricating oil entering the lower cavity of the motor upward, enabling the lubricating oil to return to below the upper flange as much as possible without being discharged, and reducing the oil spitting rate. And through the setting of the oil return inclined hole, the lubricating oil flowing back from the upper flange can be diverted to a position closer to the bottom of the oil sump, so that the flowing-back lubricating oil directly enters below the oil level in the oil sump through the diversion channel, thereby optimizing the circulation of the lubricating oil path in the pump body inside the pump body, avoiding the lubricating oil pumped out from the oil return flow channel being directly radially sprayed onto the flange wall surface or the housing wall surface, which causes the sprayed hollow cavity wall surface and makes part of the lubricating oil sputter into the lower cavity of the motor and flow out with the exhaust gas. For example, spraying radially onto the hollow cavity to avoid part of the lubricating oil entering the lower cavity of the motor, further improving the compressor oil spitting rate and radial vibration problems caused thereby. Therefore, it can further prevent oil discharge and minimize the oil spitting rate to the greatest extent. The present invention also sets the position of the oil return inclined hole to satisfy the minimum distances a≥1mm and b≥1mm from the annular flexible groove, the outer peripheral surface of the shaft diameter part and the upper end surface of the flange plate, which can effectively ensure that there is enough safety and sealing distance between the lower side of the inclined surface of the oil return inclined hole and the annular flexible groove, and enough safety and sealing distance between the upper side of the inclined surface of the oil return inclined hole and the outer peripheral surface of the shaft diameter part, the upper end surface of the flange plate and the bending part, which can not only form a sealing effect that meets the requirements for the oil return inclined hole, but also does not affect the structural strength of the flange entity part between the oil return inclined hole and the annular flexible groove, and does not affect the structural strength of the entity parts between the oil return inclined hole and the outer peripheral surface of the shaft diameter part and the upper end surface of the flange plate respectively, and can further realize that the oil return flow path structure avoids the heavy load area of the oil film of the crankshaft flange friction pair without affecting the flexible deformation effect of the flexible groove, thereby improving the performance and reliability of the compressor. It solves the reliability problem in the prior art that the setting of the oil return flow channel of the upper flange destroys the bearing oil film between the crankshaft and the flange friction pair, especially in the area where the contact stress between the root of the crankshaft and the flange is relatively large, and the root of the crankshaft wears due to the destruction of the oil film.

[0046] Aiming at the technical problems existing in the conventional rolling rotor compressor, the present invention proposes an innovative oil path structure. Without affecting the flexible deformation effect of the existing conventional annular flexible groove, while realizing the single-path circulation of the lubricating oil path inside the pump body, it avoids the centrifugal force and gas force generated by the rotation of the crankshaft from carrying the lubricating oil into the upper and lower cavities of the motor, greatly reducing the oil content rate in the upper and lower cavities of the motor, thereby reducing the oil spitting rate of the compressor, increasing the oil pumping volume between the upper flange and the crankshaft friction pair and the overall oil path, and thus improving the performance and reliability of the compressor.

[0047] The pump body assembly of the rolling rotor compressor of the present invention includes an upper flange, a cylinder, a crankshaft, a roller, and a lower flange. A central oil hole is provided on the crankshaft, and a side oil hole is provided at the lower root of the shaft end where the crankshaft mates with the upper flange. The upper flange is provided with an upper spiral oil groove, an oil storage groove, a lower oil groove, an oil return inclined hole, an oil return groove, and an upper flange hollow cavity. The central oil hole of the crankshaft and the upper flange hollow cavity are respectively communicated with the oil sump, and the central oil hole of the crankshaft, the side oil hole, and the upper spiral oil groove, the oil storage groove, the lower oil groove, the oil return inclined hole, the oil return groove, and the upper flange hollow cavity of the upper flange are sequentially communicated to jointly form an oil pumping and oil return circulation flow path of the pump body assembly. Among them, the central oil hole of the crankshaft, the side oil hole, and the upper spiral oil groove on the upper flange jointly constitute an upper oil or oil pumping flow path, and the oil storage groove, the lower oil groove, the oil return inclined hole, the oil return groove, and the upper flange hollow cavity on the upper flange jointly constitute an oil return flow path.

[0048] For the oil pumping and oil return circulation flow path of the present invention, the oil return inclined hole of the oil return flow path is arranged inside the flange of the upper flange, penetrates the lower end face and the inner circular surface of the flange, and is respectively communicated with the lower oil groove and the oil return groove at both ends. The center line of the oil return inclined hole has a certain inclination angle with the lower end face of the upper flange and is not communicated with the upper flange annular flexible groove. The minimum wall thicknesses between the oil return inclined hole and the flange annular flexible groove and the upper end face of the flange are set as a and b respectively, and the preferred ranges of the parameters a and b are: a≥1mm, b≥1mm.

[0049] Both ends of the lower oil groove as described above are respectively communicated with the oil storage groove and the oil return inclined hole. The lower end side of the lower oil groove has a certain distance c from the lower end face of the flange, and the lower end side of the lower oil groove is not communicated with the side oil hole of the crankshaft and the annular flexible groove.

[0050] The present invention also solves the following technical problems:

[0051] 1. A large amount of lubricating oil pumped out from the upper spiral oil groove on the upper flange of the pump body lubricating oil path is pumped into the lower cavity of the motor and only relies on gravity to flow back. Most of it is carried into the upper cavity of the motor by the impact of the high-speed air flow and discharged from the compressor housing, resulting in too high an oil spitting rate of the compressor, thus affecting the performance and reliability of the compressor;

[0052] 2. The setting of the oil return flow path on the upper flange in the prior art destroys the load-bearing oil film between the friction pairs of the crankshaft and the flange. Especially in the area where the contact stress between the root of the crankshaft and the flange is relatively large, there is a reliability problem of wear at the root of the crankshaft due to the destruction of the oil film.

[0053] Beneficial effects:

[0054] 1. The present invention proposes an innovative internal circulation oil return structure for the pump body lubricating oil path, avoiding a large amount of lubricating oil pumped out from the upper spiral oil groove on the upper flange of the pump body lubricating oil path being pumped into the lower cavity of the motor and being carried to the upper cavity of the motor by the disturbance and impact of the high-speed air flow and discharged from the compressor housing, greatly reducing the oil spitting rate of the compressor and improving the performance and reliability of the compressor;

[0055] 2. The present invention provides an innovative single-flow-path internal circulation lubricating oil return structure for a pump body, which, without affecting the flexible deformation effect of the flexible groove, further enables the oil return flow path structure to avoid the oil film heavy load area of the crankshaft flange friction pair, thereby achieving excellent effects of improving the performance and reliability of the compressor. By setting the oil return inclined hole 1109, the present invention can, on the basis of the existing structure, move the position where the oil return inclined hole 1109 is connected to the lower oil groove 1103 upwards as much as possible to avoid the heavy load area as much as possible, so as to realize both guiding the oil back and preventing the oil film in the stress-bearing area at the root of the crankshaft from being damaged, resulting in large wear.

[0056] In some embodiments, it further includes a crankshaft 13, and the crankshaft 13 passes through the shaft hole of the upper flange 11;

[0057] A central oil hole 1301 and a side oil hole 1302 are arranged inside the crankshaft 13. The central oil hole 1301 extends along the axial direction of the crankshaft 13, the side oil hole 1302 extends along the radial direction of the crankshaft 13. One end of the side oil hole 1302 is communicated with the central oil hole 1301, and the other end extends to be communicated with the radial outside of the crankshaft 13, and the side oil hole 1302 faces the inner wall of the upper flange 11 to be able to transport oil into the upper oil groove 1101;

[0058] The distance between the lower end of the lower oil groove 1103 and the lower end face of the flange plate 111 is c. The lower end of the lower oil groove 1103 is higher than the upper end of the annular flexible groove 1106, and the lower end of the lower oil groove 1103 is higher than the upper end of the side oil hole 1302.

[0059] The present invention also sets the position of the lower oil groove to be located at the upper end of the annular flexible groove and the upper end of the side oil hole, which can effectively ensure that there is enough safety and sealing distance between the lower end of the lower oil groove and the annular flexible groove and between the lower end of the lower oil groove and the upper end of the side oil hole, so that both a sealing effect that meets the requirements can be formed for the lower oil groove, and the structural strength of the flange entity part between the lower oil groove and the annular flexible groove and the structural strength of the entity part between the lower oil groove and the side oil hole are not affected. Without affecting the flexible deformation effect of the flexible groove, the oil return flow path structure can further avoid the oil film heavy load area of the crankshaft flange friction pair, thereby achieving excellent effects of improving the performance and reliability of the compressor. Further solve the reliability problem in the prior art that the setting of the oil return flow path of the upper flange destroys the bearing oil film between the crankshaft and the flange friction pair, especially in the area where the contact stress between the root of the crankshaft and the flange is large, and the root of the crankshaft is worn due to the destruction of the oil film.

[0060] As Figure 1-1As shown, the oil return circulation flow path of the pump body assembly with an innovative structure of the present invention has an oil return inclined hole 1109 in the oil return flow path disposed inside the flange of the upper flange, and penetrates the lower end face and the inner circular face of the flange. The center line of the oil return inclined hole 1109 has a certain inclination angle with the lower end face of the upper flange, and its two ends are respectively connected to the lower oil groove 1103 and the oil return groove 1110, and are not connected to the annular flexible groove 1106 of the upper flange. As Figure 1-2 shown, let the minimum wall thicknesses between the oil return inclined hole 1109 and the annular flexible groove 1106 and the upper end face of the flange be a and b respectively. The preferred ranges of the parameters a and b are: a ≥ 1 mm, b ≥ 1 mm to ensure the local structural strength of the upper flange. Further, there is a certain distance c between the lower end side of the lower oil groove 1103 of the innovative structure of the present invention and the lower end face of the flange, and the lower end side of the lower oil groove 1103 is not connected to the side oil hole 1302 of the crankshaft and the annular flexible groove 1106. This avoids a large amount of lubricating oil directly entering the oil outlet of the oil return flow path from the short-circuit flow path before the lubricating oil pumped out from the side oil hole 1302 at the root of the long axis of the crankshaft enters the upper spiral oil groove (upper oil groove 1101) on the upper flange, and returning to the oil sump 7 through the hollow cavity 1105 of the upper flange, which in turn causes a significant reduction in the oil pumping volume of the upper oil groove 1101 on the upper flange, increasing the reliability risk of insufficient lubrication and wear between the contact surfaces of the friction pair of the upper flange and the long axis of the crankshaft. In addition, since the area with a relatively large contact stress between the crankshaft and the flange generally occurs at the root of the crankshaft, the innovative structure of the proposed solution of the present invention can, without affecting the deformation effect of the annular flexible groove 1106, simultaneously increase the distance c between the lower end side of the lower oil groove 1103 and the lower end face of the flange to the greatest extent, thereby avoiding the reliability problem of wear of the crankshaft and flange parts caused by the downward extension of the lower oil groove 1103 being too long and damaging the oil film in the maximum contact stress area, resulting in a significant decrease in its bearing capacity.

[0061] In some embodiments, the circumferential arrangement position of the oil storage groove 1102 is a non-bearing area of the pump body. It is set that in the projection plane of the axial end face of the upper flange 11, the projection point of the central axis of the upper flange 11 is O, the projection point of the central axis of the exhaust hole 114 of the upper flange 11 is M1, and the connection line between O and M1 is L1. The projection point of the starting edge end of the oil storage groove 1102 along the rotation direction of the pump body is M2, and the projection point of the terminating edge end is M3. The connection lines between the projection point O and M2, M3 are L2 and L3 respectively. And along the rotation direction of the pump body, let the included angle between L2 and L1 be α, and the included angle between L3 and L1 be β. The parameters α and β satisfy: 80° ≤ β ≤ 150°, 0° ≤ α ≤ 60°.

[0062] By forming the above relationship between the installation position of the oil storage tank and the exhaust hole, since the position of the exhaust hole in the circumferential direction is the load-bearing area, in the present invention, 80° ≤ β ≤ 150° and 0° ≤ α ≤ 60° can make the oil storage tank of the present invention as far as possible from the area of the exhaust port in the circumferential direction, so that it is arranged in the non-load-bearing area in the circumferential direction, thus avoiding the range of the load-bearing area. This can ensure that the opening of the oil storage tank does not affect the normal load-bearing performance of the upper flange, does not affect the exhaust performance, etc., and can also play the role of oil storage and oil return, effectively reducing the oil spitting rate.

[0063] The innovative structure of the present invention proposes an innovative structure of a rolling rotor type compressor pump body assembly, including an upper flange 11, a cylinder 12, a crankshaft 13, a roller 14 and a lower flange 15. A central oil hole 1301 is provided on the crankshaft 13, and a side oil hole 1302 is provided at the lower root of the shaft end where the crankshaft is fitted with the upper flange. The upper flange 11 is provided with an upper spiral oil groove (upper oil groove 1101), an oil storage tank 1102, a lower oil groove 1103, an oil return inclined hole 1109, an oil return groove 1110 and an upper flange hollow cavity 1105. The central oil hole 1301 of the crankshaft and the upper flange hollow cavity 1105 are respectively communicated with the oil sump 7, and the central oil hole 1301 of the crankshaft, the side oil hole 1302, and the upper spiral oil groove (upper oil groove 1101), the oil storage tank 1102, the lower oil groove 1103, the oil return inclined hole 1109, the oil return groove 1110 and the upper flange hollow cavity 1105 of the upper flange are sequentially communicated, jointly forming the oil pumping and oil return circulation flow path of the pump body assembly 1. Among them, the central oil hole 1301 of the crankshaft, the side oil hole 1302 and the upper spiral oil groove 1101 of the upper flange jointly constitute the upper oil or oil pumping flow path (i.e., the upper oil flow path 100), and the oil storage tank 1102, the lower oil groove 1103, the oil return inclined hole 1109, the oil return groove 1110 and the upper flange hollow cavity 1105 of the upper flange jointly constitute the oil return flow path (i.e., the oil return channel 200).

[0064] The oil storage tank 1102 of the innovative structure of the present invention is a crescent-shaped groove structure along the radial direction arranged in the non-load-bearing area (here, the non-load-bearing area is different from the load-bearing area caused by the high-pressure gas force of the pump body, and the load-bearing area is the area within a certain angle range on the exhaust port side (the high-pressure cavity side of the pump body)). Figure 1-3As shown in the figure, it is set that the connecting line between the projection points O and M1 of the central axis of the upper flange and the central axis of the exhaust hole of the upper flange in the horizontal direction is L1. The projection points of the starting edge end and the ending edge end of the oil storage tank along the rotation direction of the pump body in the horizontal direction are M2 and M3 respectively. The connecting lines between the projection point O and M2, M3 are L2 and L3 respectively. Further, along the rotation direction of the pump body, it is set that the included angle between L2 and L1 is α, and the included angle between L3 and L1 is β. Preferably, the parameters α and β satisfy: 80° ≤ β ≤ 150°, 0° ≤ α ≤ 60°, which can minimize the influence on the flange support effect and the damage to the oil film continuity caused by the structure of the oil storage tank. The lower oil tank 1103 is a straight tank or a lower spiral oil tank structure with a spiral direction opposite to that of the upper spiral oil tank (upper oil tank 1101).

[0065] In some embodiments, it further includes an oil return groove 1110 and a cylinder 2. The axial upper end surface of the cylinder 2 is connected to the axial lower end surface of the flange of the upper flange 11. The oil return groove 1110 is opened on the upper flange 11 and / or the cylinder 2. An upper flange hollow cavity 1105 is axially opened on the flange 111. The upper flange hollow cavity 1105 penetrates from the upper end surface of the flange 111 to its lower end surface. One end of the oil return groove 1110 is communicated with the oil return inclined hole 1109, and the other end is communicated with the upper flange hollow cavity 1105. Through the setting of the oil return groove, the present invention can be communicated with the oil return inclined hole, so as to effectively guide the returned oil back to the oil pool below the upper flange through the upper flange hollow cavity, thereby reducing the situation that the upper flange discharges oil upward into the motor cavity, resulting in an increase in the oil spitting rate, and effectively reducing the oil spitting rate.

[0066] As Figure 1-2 shown, in some embodiments, the oil return groove 1110 is arranged on the lower end surface of the upper flange 11, and the oil return groove 1110 extends along the radial direction. The minimum distance between the lower end of the oil return inclined hole 1109 and the inner circular surface of the cylinder 2 is d, and the minimum distance between the end of the oil return groove 1110 communicated with the oil return inclined hole 1109 and the inner circular surface of the cylinder 2 is e, and d ≥ 1.5 mm, e ≥ 1.5 mm, and d = e. By arranging the oil return groove on the lower end surface of the flange of the upper flange and extending it along the radial direction, the present invention can effectively guide the oil to the upper flange hollow cavity and enter the oil pool below the flange. And by setting the minimum distance d ≥ 1.5 mm between the oil return inclined hole and the inner circular surface of the cylinder, and the minimum distance e ≥ 1.5 mm between the oil return groove and the inner circular surface of the cylinder, it can effectively seal the inside of the cylinder, prevent the leakage of compressed gas, and prevent the returned oil from entering the compression chamber again.

[0067] As Figure 1-2As shown, the oil return groove 1110 of the structure of the present invention is a groove structure provided on the lower end face of the upper flange and extending radially, and its two ends are respectively communicated with the oil return inclined hole 1109 and the upper flange hollow cavity 1105. It is set that the minimum distance from the flange end face side of the oil return inclined hole 1109 to the inner circular surface of the cylinder 12 is d, and the minimum distance from the end of the oil return groove 1110 close to the oil return inclined hole 1109 to the inner circular surface of the cylinder 12 is e. Preferably, d≥1.5mm, e≥1.5mm, and d = e, so as to ensure the seal between the cylinder cavity and the high-pressure cavity of the housing or the oil sump, and prevent performance problems caused by leakage of the cylinder cavity.

[0068] Alternative Embodiment 1, as Figure 2 , in some embodiments, the oil return groove 1110 is provided on the upper end face of the cylinder 2 in the axial direction and extends radially, and the lower end of the oil return inclined hole 1109 extends to the lower end face of the flange 111. This is the structural form of Alternative Embodiment 2 of the present invention, that is, the oil return groove is provided on the upper end face of the cylinder in the axial direction, and it can also effectively play the role of directly guiding the oil in the oil return inclined hole into the upper flange hollow cavity and then into the oil sump under the flange, effectively reducing the oil spitting rate. Alternatively, for the innovative pump body oil circuit structure of the present invention, its oil return groove 1110 can be a groove structure provided on the upper end face of the cylinder 12 that cooperates with the upper flange 11 and extends radially, and the two ends of the oil return groove are respectively communicated with the oil return inclined hole 1109 and the upper flange hollow cavity 1105.

[0069] Alternative Embodiment 2, as Figure 3 , in some embodiments, the oil return groove 1110 is provided inside the upper flange 11, the oil return groove 1110 is located between the upper end face and the lower end face of the flange 111, and the oil return groove 1110 extends in the radial direction, and the lower end of the oil return inclined hole 1109 extends to the lower end face of the flange. This is the structural form of Alternative Embodiment 3 of the present invention, that is, the oil return groove is provided inside the upper flange between the upper and lower end faces of the flange, and it can also effectively play the role of directly guiding the oil in the oil return inclined hole into the upper flange hollow cavity and then into the oil sump under the flange, effectively reducing the oil spitting rate. Alternatively, for the innovative pump body oil circuit structure of the present invention, its oil return groove 1110 can be an oil return hole structure provided inside the flange and extending radially, and the two ends of the oil return hole are respectively communicated with the oil return inclined hole 1109 and the upper flange hollow cavity 1105.

[0070] Alternative Embodiment 3, as Figure 4, in some embodiments, part of the oil return groove 1110 is formed on the lower end face of the upper flange 11, and part of it is formed on the upper axial end face of the cylinder 2. The part of the oil return groove formed on the upper flange 11 is opposite and communicated with the part of the oil return groove formed on the cylinder 2, and they are spliced to form a complete oil return groove. This is the structural form of the alternative embodiment 4 of the present invention, that is, part of the oil return groove is arranged on the lower end face of the flange, and the other part is arranged on the upper end face of the cylinder, so that the two are spliced to form a complete oil return groove, which can also effectively play the role of directly guiding the oil in the oil return inclined hole into the hollow cavity of the upper flange and then into the oil pool at the lower part of the flange, effectively reducing the oil spitting rate. Alternatively, the present invention innovatively designs the oil path structure of the pump body. A first oil groove structure is arranged on the end face of the upper flange 11, and a second oil groove structure is arranged at the corresponding position of the corresponding end face of the cylinder 12 cooperating with the upper flange 11. The first oil groove and the second oil groove cooperate to form the oil return groove 1110, and both ends of the oil return groove 1110 are respectively communicated with the oil return inclined hole 1109 and the hollow cavity 1105 of the upper flange.

[0071] In some embodiments, the oil return inclined hole 1109 is a straight hole, which is inclined with respect to both the horizontal direction and the vertical direction. The extending direction of the oil return inclined hole 1109 forms an angle between (0, 90°) with the axial direction of the upper flange 11, and the extending direction of the oil return inclined hole 1109 forms an angle between (0, 90°) with the horizontal direction. The axial direction of the upper flange 11 is along the vertical direction, and the axial end face of the upper flange 11 is along the horizontal direction. This is the preferred structural form of the oil return inclined hole of the present invention, that is, its extending direction is inclined with respect to the vertical direction and also with respect to the horizontal direction, which can guide the oil at the lower end of the lower oil groove to the lower end face of the upper flange through the oil return inclined hole, rather than flowing horizontally to the hollow cavity of the upper flange and being impacted into the lower cavity of the motor above the upper flange, thereby further reducing the oil spitting rate.

[0072] In some embodiments, the upper oil groove 1101 is a spiral oil groove structure formed on the inner wall of the upper flange 11. The upper oil groove 1101 extends spirally upward from its lower end to its upper end, and the rotation direction of the upper oil groove 1101 from its lower end to its upper end is the same as the rotation direction of the crankshaft. The upper flange is sleeved on the outer periphery of the crankshaft; the lower oil groove 1103 is a spiral oil groove structure formed on the inner wall of the upper flange 11. The lower oil groove 1103 extends spirally downward from its upper end to its lower end, and the rotation direction of the lower oil groove 1103 from its upper end to its lower end is the same as the rotation direction of the crankshaft. By setting the upper oil groove in the form of a spiral groove and having the rotation direction from the lower end to the upper end the same as the rotation direction of the crankshaft, the present invention can effectively drive the oil in the upper oil groove to flow into the oil storage tank as the crankshaft rotates. The present invention also sets the lower oil groove in the form of a spiral groove and has the rotation direction from the upper end to the lower end the same as the rotation direction of the crankshaft, which can effectively drive the oil in the oil storage tank to flow into the lower oil groove as the crankshaft rotates, and then discharge it through the lower oil groove to the lower part of the upper flange. That is, through the design of the upper and lower spiral oil grooves, the present invention can effectively utilize the rotation of the crankshaft to drive the lubricating oil to move from the upper oil groove through the oil storage tank and the lower oil groove in sequence to effectively lubricate the joint surface between the upper flange and the crankshaft.

[0073] In some embodiments, the upper end of the upper oil groove 1101 is communicated with a first position of the oil storage tank 1102, the upper end of the lower oil groove 1103 is communicated with a second position of the oil storage tank 1102, and the first position and the second position are located at different positions. This is the preferred position where the upper oil groove and the lower oil groove of the present invention are respectively communicated with the oil storage tank, that is, the upper oil groove is communicated to the first position, the lower oil groove is communicated to the second position, and the upper oil groove and the lower oil groove are communicated to different positions of the oil storage tank, which can enable the oil conveyed by the upper oil groove to be stored in the oil storage tank, and then discharge the stored oil, preventing the oil conveyed by the upper oil groove from being directly discharged through the lower oil groove without passing through the oil storage tank, thereby improving the lubrication effect between the upper flange and the crankshaft.

[0074] In some embodiments, the oil storage tank 1102 includes a first end and a second end in the horizontal direction. The first position is disposed closer to the first end than the second end or coincides with the first end, and the second position is disposed closer to the second end than the first end or coincides with the second end. This is a preferred structural form of the oil storage tank of the present invention. The first position where the upper oil tank communicates with the oil storage tank can be the first end or close to the first end, and the second position where the lower oil tank communicates with the oil storage tank can be the second end or close to the second end. The optimal choice is that the first position is the first end and the second position is the second end. In this way, the length between the first position and the second position can be maximally extended, thereby increasing the oil storage length and further maximizing the lubrication effect between the upper flange and the crankshaft.

[0075] The present invention also provides a pump body, which includes the pump body oil circuit structure described in any one of the preceding items.

[0076] The present invention also provides a compressor, which includes the aforementioned pump body.

[0077] The compressor of the present invention includes an innovative internal circulation oil return structure for the lubricating oil circuit of the pump body, which can prevent a large amount of lubricating oil pumped out from the spiral oil groove on the upper flange of the pump body lubricating oil circuit from being pumped into the lower cavity of the motor, being carried by the disturbance and impact of the high-speed air flow to the upper cavity of the motor and discharged from the compressor housing, greatly reducing the oil spitting rate of the compressor and improving the performance and reliability of the compressor; it can also further realize that the oil return flow path structure avoids the heavy oil film load area of the crankshaft flange friction pair without affecting the flexible deformation effect of the flexible groove, thereby enhancing the excellent effect of the performance and reliability of the compressor.

[0078] A compressor of the present invention has a pump body assembly with the structural characteristics described in the present invention. The compressor can be a single-cylinder, double-cylinder, multi-cylinder rotary compressor, or a rotating cylinder compressor, a sliding vane compressor, a scroll compressor, etc.

[0079] The present invention also protects an air conditioner having a compressor with the structural characteristics described in the present invention.

[0080] The above are only the preferred embodiments of the present invention and are not intended to limit the present invention. Any modifications, equivalent replacements, and improvements made within the spirit and principle of the present invention shall be included in the protection scope of the present invention. The above is only the preferred implementation manner of the present invention. It should be noted that for those of ordinary skill in the art, several improvements and variations can be made without departing from the technical principle of the present invention, and these improvements and variations should also be regarded as the protection scope of the present invention.

Claims

1. A pump body oil circuit structure, characterized in that: Comprising: An upper flange (11), on the inner wall of the shaft hole of the upper flange, there are an upper oil groove (1101), an oil storage groove (1102) and a lower oil groove (1103). The lower end of the upper oil groove (1101) can be used to suck oil. The upper oil groove (1101) extends upward until its upper end communicates with the oil storage groove (1102). The oil storage groove (1102) extends horizontally on the inner wall of the upper flange (11). The upper end of the lower oil groove (1103) communicates with the oil storage groove (1102) to be able to suck oil from the oil storage groove (1102). The lower oil groove (1103) extends downward. Inside the upper flange (11), there is also an oil return inclined hole (1109). The oil return inclined hole (1109) extends obliquely downward, and the upper end of the oil return inclined hole (1109) communicates with the lower end of the lower oil groove (1103). The lower end of the oil return inclined hole (1109) can extend to lead the oil to an oil pool below the upper flange (11); On the upper flange (11), there is also an annular flexible groove (1106). The annular flexible groove (1106) is located on the outer periphery of the inner wall of the shaft hole and is spaced a preset distance from the inner wall of the shaft hole. The connecting end of the oil return inclined hole (1109) and the lower oil groove (1103) is above the upper end of the annular flexible groove (1106); and the minimum distance between the oil return inclined hole (1109) and the annular flexible groove (1106) is a, and a ≥ 1 mm. The upper flange (11) includes a flange plate (111) and a shaft diameter part (112). The shaft diameter part (112) is located on the upper end face of the flange plate (111) and extends upward. The outer peripheral surface of the shaft diameter part (112) intersects with the upper end face of the flange plate (111) at a bending part (113). And the minimum distance between the outer peripheral surface of the shaft diameter part (112), the bending part (113) and the upper end face of the flange plate (111) and the oil return inclined hole (1109) is b, and b ≥ 1 mm.

2. The pump body oil circuit structure according to claim 1, characterized in that: Also includes a crankshaft (13), and the crankshaft (13) passes through the shaft hole of the upper flange (11); Inside the crankshaft (13), there are a central oil hole (1301) and side oil holes (1302). The central oil hole (1301) extends along the axial direction of the crankshaft (13). The side oil holes (1302) extend along the radial direction of the crankshaft (13). One end of the side oil hole (1302) communicates with the central oil hole (1301), and the other end extends to communicate with the radial outside of the crankshaft (13). And the side oil holes (1302) face the inner wall of the upper flange (11) to be able to transport oil into the upper oil groove (1101); The distance between the lower end of the lower oil groove (1103) and the lower end face of the flange plate (111) is c. The lower end of the lower oil groove (1103) is higher than the upper end of the annular flexible groove (1106). The lower end of the lower oil groove (1103) is higher than the upper end of the side oil hole (1302).

3. The pump body oil circuit structure according to claim 1, characterized in that: The circumferential arrangement position of the oil storage tank (1102) is a non-load-bearing area of the pump body, set within the projection plane of the axial end face of the upper flange (11). The projection point of the central axis of the upper flange (11) is O, the projection point of the central axis of the exhaust hole (114) of the upper flange (11) is M1, and the connection line between O and M1 is L1. The projection point of the starting edge end of the oil storage tank (1102) along the rotation direction of the pump body is M2, and the projection point of the terminating edge end is M3. The connection lines between the projection point O and M2, M3 are L2 and L3 respectively. Along the rotation direction of the pump body, the included angle between L2 and L1 is set as α, and the included angle between L3 and L1 is β. The parameters α and β satisfy: 80° ≤ β ≤ 150°, 0° ≤ α ≤ 60°.

4. The pump body oil circuit structure according to claim 1, characterized in that: It further includes an oil return groove (1110) and a cylinder (2). The axial upper end face of the cylinder (2) is connected to the axial lower end face of the flange plate of the upper flange (11). The oil return groove (1110) is opened on the upper flange (11) and / or the cylinder (2). An upper flange hollow cavity (1105) is axially opened on the flange plate (111). The upper flange hollow cavity (1105) penetrates from the upper end face of the flange plate (111) to its lower end face. One end of the oil return groove (1110) is communicated with the oil return inclined hole (1109), and the other end is communicated with the upper flange hollow cavity (1105).

5. The pump body oil circuit structure according to claim 4, characterized in that: The oil return groove (1110) is arranged on the lower end face of the upper flange (11), and the oil return groove (1110) extends along the radial direction. The minimum distance between the lower end of the oil return inclined hole (1109) and the inner circular surface of the cylinder (2) is d, and the minimum distance between the end of the oil return groove (1110) communicated with the oil return inclined hole (1109) and the inner circular surface of the cylinder (2) is e. And d ≥ 1.5 mm, e ≥ 1.5 mm, and d = e.

6. The pump body oil circuit structure according to claim 4, characterized in that: The oil return groove (1110) is arranged on the axial upper end face of the cylinder (2) and extends radially. The lower end of the oil return inclined hole (1109) extends to the lower end face of the flange plate (111).

7. The pump body oil circuit structure according to claim 4, characterized in that: The oil return groove (1110) is arranged inside the upper flange (11). The oil return groove (1110) is located between the upper end face and the lower end face of the flange plate (111), and the oil return groove (1110) extends along the radial direction. The lower end of the oil return inclined hole (1109) extends to the lower end face of the flange plate (111).

8. The pump body oil circuit structure according to claim 4, characterized in that: Part of the oil return groove (1110) is opened on the lower end face of the upper flange (11), and part is opened on the axial upper end face of the cylinder (2). The part of the oil return groove opened on the upper flange (11) and the part of the oil return groove opened on the cylinder (2) are opposite and communicated, splicing to form a complete oil return groove.

9. The pump body oil circuit structure according to claim 1, characterized in that: The oil return inclined hole (1109) is a straight hole, which is inclined with respect to both the horizontal direction and the vertical direction. The extension direction of the oil return inclined hole (1109) forms an angle with the axial direction of the upper flange (11) within the range of (0, 90°), and the extension direction of the oil return inclined hole (1109) forms an angle with the horizontal direction within the range of (0, 90°). The axial direction of the upper flange (11) is along the vertical direction, and the axial end face of the upper flange (11) is along the horizontal direction.

10. The pump body oil circuit structure according to any one of claims 1-9, characterized in that: The upper oil groove (1101) is a spiral oil groove structure formed on the inner wall of the upper flange (11). The upper oil groove (1101) extends spirally upward from its lower end to its upper end, and the rotation direction of the upper oil groove (1101) from its lower end to its upper end is the same as the rotation direction of the crankshaft. The upper flange is sleeved on the outer periphery of the crankshaft; the lower oil groove (1103) is a spiral oil groove structure formed on the inner wall of the upper flange (11). The lower oil groove (1103) extends spirally downward from its upper end to its lower end, and the rotation direction of the lower oil groove (1103) from its upper end to its lower end is the same as the rotation direction of the crankshaft.

11. The pump body oil circuit structure according to any one of claims 1-9, characterized in that: The upper end of the upper oil groove (1101) communicates with the first position of the oil storage groove (1102), the upper end of the lower oil groove (1103) communicates with the second position of the oil storage groove (1102), and the first position and the second position are located at different positions.

12. The pump body oil circuit structure according to claim 11, characterized in that: The oil storage groove (1102) includes a first end and a second end along the horizontal direction. The first position is set closer to the first end relative to the second end or the first position coincides with the first end. The second position is set closer to the second end relative to the first end or the second position coincides with the second end.

13. A pump body, characterized in that: It includes the pump body oil circuit structure according to any one of claims 1-12.

14. A compressor, characterized in that: It includes the pump body according to claim 13.

15. An air conditioner, characterized in that: It includes the compressor according to claim 14.

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