Compressor oil supply structure and scroll compressor

Abstract

The present application provides a compressor oil supply structure and a scroll compressor. The compressor oil supply structure includes a crankshaft (16), a moving plate (1), a stationary plate (2) and an upper bracket (15). The moving plate (1) is rotatably connected to the eccentric portion (17) of the crankshaft (16) through a moving plate bearing (8). A high-pressure chamber (26) is formed between the eccentric portion (17) and the moving plate (1). A medium-pressure chamber (27) is formed between the upper bracket (15), the moving plate (1) and the crankshaft (16). The high-pressure chamber (26) and the medium-pressure chamber (27) are spaced apart. A high-pressure oil groove connected to the high-pressure oil chamber is formed between the moving plate (1) and the stationary plate (2). The high-pressure chamber (26) provides a second pressure to the moving plate (1), and the high-pressure oil groove provides a first pressure opposite to the second pressure to the moving plate (1). According to the compressor oil supply structure of the present application, the proportion of exhaust pressure in back pressure can be reduced, and the proportion of medium pressure in back pressure can be increased, so that the medium pressure can effectively balance the overturning moment.

Description

Technical Field

[0001] The present application relates to the technical field of compressors, and in particular to a compressor oil supply structure and a scroll compressor. Background Art

[0002] In scroll compressors, the profile and the pump body have always been the core issues of compressor technology. In the process of scroll compression, the meshing of the profile of the moving and static disks, and the meshing of the top and bottom of the teeth of the moving and static disks have always been technical difficulties that need to be addressed. These meshing structures require as much sealing as possible, but once metal is in direct contact with metal, wear will occur. Therefore, the oil circuit design in the scroll compressor is also very important. The oil circuit needs to ensure the lubrication of each bearing and the meshing of the profile. In order to ensure lubrication, some gaps are reserved between the bearings, profiles, tooth tops, and tooth bottoms. In actual operation, deformation of parts and overturning torque generated by the compression force of the moving and static disks during compression will cause these gaps to change, thereby causing wear.

[0003] In current scroll compressors, a medium pressure greater than the suction pressure but less than the exhaust pressure is usually drawn from the pump body to the back of the moving plate to form a back pressure, thereby pressing the moving plate onto the stationary plate. However, the back pressure of most current compressors is not completely introduced into the medium pressure, but is divided into two parts: the exhaust pressure and the medium pressure. After most traditional compressors introduce the oil circuit from the oil pool of the high-pressure chamber into the crankshaft, they will be drawn out from the eccentric part of the crankshaft to lubricate the moving plate bearing matched with the eccentric part. Although this allows the eccentric part of the crankshaft and the moving plate bearing to obtain sufficient oil, it also causes the moving plate bearing to actually be a high-pressure chamber composed of high-pressure oil and gas. Therefore, in general traditional compressors, a sealing ring is provided on the outside of the eccentric part, or on the moving plate, or on the crankshaft, or on the main balance block placed above the upper bracket, so as to separate the exhaust pressure chamber in the main bearing from the medium pressure chamber drawn out from the pump body in the form of a sealing ring.

[0004] The outer intermediate pressure not only presses the moving plate onto the stationary plate, but also balances the overturning moment. When the overturning moment is generated inside the moving plate, as long as the outer intermediate pressure is large enough, the overturning moment can be balanced. Obviously, since the exhaust pressure is too close to the rotation center when the moving plate overturns, this part of the pressure can hardly play an effective role in balancing the force arm. The only thing that can play a role is the intermediate pressure on the outside. In the same plane, the intermediate pressures on both sides of the rotation center can be equivalent to basically symmetrical points of action. At this time, when the overturning moment of the moving plate is less than the product of the intermediate pressure and the intermediate pressure arm, the overturning moment will not cause the moving plate to overturn.

[0005] Obviously, under the same back pressure, if the proportion of the exhaust pressure in the center is too high, the proportion of the intermediate pressure will be reduced, and the overturning moment cannot be effectively balanced. On the contrary, the smaller the proportion of the exhaust pressure, the greater the intermediate pressure, and the more effectively the overturning moment can be balanced.

[0006] For the solution of using medium pressure to balance the overturning moment, in the compressor of the related technology, since the exhaust pressure in the cavity of the moving plate bearing on the back-pressure side is too high, the exhaust pressure accounts for a large proportion of the back pressure, and the medium pressure accounts for a small proportion, resulting in insufficient medium pressure back pressure and inability to effectively balance the overturning moment. Summary of the invention

[0007] Therefore, the technical problem to be solved by the present application is to provide a compressor oil supply structure and a scroll compressor, which can reduce the proportion of exhaust pressure in back pressure and increase the proportion of medium pressure in back pressure, so that the medium pressure can effectively balance the overturning moment.

[0008] In order to solve the above problems, the present application provides a compressor oil supply structure, including a crankshaft, a moving plate, a stator plate and an upper bracket. The moving plate is rotatably connected to the eccentric part of the crankshaft through a moving plate bearing. A high-pressure chamber is formed between the eccentric part and the moving plate. A medium-pressure chamber is formed between the upper bracket, the moving plate and the crankshaft. The high-pressure chamber and the medium-pressure chamber are separated. A high-pressure oil groove connected to the high-pressure oil chamber is formed between the moving plate and the stator plate. The high-pressure chamber provides a second pressure to the moving plate, and the high-pressure oil groove provides a first pressure opposite to the second pressure to the moving plate.

[0009] Preferably, the area of ​​the movable plate acted on by the first pressure in the high-pressure oil groove is S1, the area of ​​the movable plate acted on by the second pressure in the high-pressure chamber is S2, and 0.5S2≤S1≤2S2.

[0010] Preferably, the first pressure in the high-pressure chamber acts on the movable disk with an area S1 and a first pressure intensity P1, the second pressure in the high-pressure oil tank acts on the movable disk with an area S2 and a second pressure intensity P2, and P1*S1=P2*S2.

[0011] Preferably, the end surface of the moving disk facing the stator disk is provided with a protrusion protruding toward the stator disk, and the end surface of the stator disk facing the moving disk is provided with a recessed portion. The protrusion can be movably arranged in the recessed portion and divides the recessed portion into a high-pressure area and a medium-pressure area isolated from each other. The high-pressure area is connected to the high-pressure oil chamber through an oil inlet channel.

[0012] Preferably, the compressor oil supply structure further includes an oil outlet channel, which is connected to the high-pressure area, and the oil entering the high-pressure area from the oil inlet channel can flow out of the high-pressure area through the oil outlet channel.

[0013] Preferably, the protrusion is a convex ring, the recess is an annular groove, the inner ring wall of the convex ring and the inner ring wall of the annular groove form a high-pressure area, and the outer ring wall of the convex ring and the outer ring wall of the annular groove form a medium-pressure area.

[0014] Preferably, the high-pressure area is a dynamic annular oil groove. During the revolution of the moving plate, the range of the high-pressure area changes, but the total area of ​​the high-pressure area remains unchanged.

[0015] Preferably, an oil storage cavity is provided on the recessed portion of the stator disc, and the oil storage cavity is intermittently connected with the high-pressure area or the medium-pressure area, and oil is stored in the high-pressure area and supplied to the medium-pressure area.

[0016] Preferably, the oil storage cavity is arranged at the bottom of the recessed portion, and there are at least two oil storage cavities, and at least two oil storage cavities are arranged along the circumference of the stator disk.

[0017] Preferably, when the protruding portion is a convex ring and the concave portion is an annular groove, when the convex ring moves to the oil storage cavity, the convex ring can completely cover the oil storage cavity.

[0018] Preferably, when the protrusion is a convex ring and the recessed portion is an annular groove, the minimum distance between the oil storage cavity and the outer annular wall of the annular groove is greater than the thickness of the convex ring; and / or the minimum distance between the oil storage cavity and the inner annular wall of the annular groove is greater than the thickness of the convex ring.

[0019] Preferably, when the protrusion is a convex ring and the recessed portion is an annular groove, when the preset point on the convex ring moves to the farthest position from the inner ring wall of the annular groove, the oil storage chamber located on the same radial direction as the preset point can be completely located in the high-pressure area, and when the preset point on the convex ring moves to the closest position to the inner ring wall of the annular groove, the oil storage chamber located on the same radial direction as the preset point can be completely located in the medium-pressure area.

[0020] Preferably, when the protruding portion is a protruding ring and the recessed portion is an annular groove, during the entire movement process of the moving plate, the moving plate does not collide with the inner annular wall or the outer annular wall of the annular groove.

[0021] Preferably, a moving plate bearing and a first oil supply channel are provided on the moving plate. The moving plate bearing is arranged on the back side of the moving plate away from the stationary plate. The first end of the first oil supply channel is connected to the high-pressure area, and the second end of the first oil supply channel is connected to the inner cavity of the moving plate bearing.

[0022] Preferably, a second oil supply channel is provided on the stator disk, a first end of the second oil supply channel is communicated with the high pressure area, and a second end of the second oil supply channel is provided on the outer peripheral side of the annular groove and is spaced apart from the annular groove.

[0023] Preferably, the first end of the second oil supply channel is arranged on the inner circumference of the annular groove, and an oil groove is arranged on the end surface of the stator plate located on the inner circumference of the annular groove, and the first end of the second oil supply channel is connected to the high-pressure area through the oil groove.

[0024] Preferably, the compressor oil supply structure also includes a crankshaft oil circuit, an upper bracket oil circuit and an oil return passage. When a first oil supply passage is provided on the moving plate and a second oil supply passage is provided on the stationary plate, the oil flows back to the oil pool through the crankshaft oil circuit, the upper bracket oil circuit, the second oil supply passage, the high-pressure area, the first oil supply passage, the inner cavity of the moving plate bearing and the oil return passage in sequence.

[0025] Preferably, the crankshaft also includes a main journal, a main bearing is arranged between the main journal and the upper bracket, a connecting hole connecting the crankshaft oil circuit and the upper bracket oil circuit is opened on the main bearing, and a first connecting channel is arranged between the main journal and the main bearing, one end of the first connecting channel is connected to the connecting hole, and the other end is connected to the crankshaft oil circuit.

[0026] Preferably, one side of the main journal has a first cut edge, the first cut edge extends along the axial direction of the main journal, and a first connecting channel is formed between the first cut edge and the main bearing. An oil storage ring is provided on the inner circumferential wall of the upper bracket, and the oil storage ring extends along the circumferential direction of the main journal. The connecting hole is connected to the oil circuit of the upper bracket through the oil storage ring.

[0027] Preferably, a second cutting edge is provided on one side of the eccentric portion, the second cutting edge extends along the axial direction of the eccentric portion, a second connecting passage is formed between the second cutting edge and the movable plate bearing, and the high-pressure chamber is connected to the oil return passage through the second connecting passage.

[0028] Preferably, the compressor oil supply structure also includes a crankshaft oil circuit, an upper bracket oil circuit and an oil return passage. When a first oil supply passage is provided on the moving plate and a second oil supply passage is provided on the stationary plate, the oil flows back to the oil pool through the crankshaft oil circuit, the inner cavity of the moving plate bearing, the first oil supply passage, the high-pressure area, the second oil supply passage and the oil return passage in sequence.

[0029] Preferably, an oil return structure is provided at the bottom of the medium pressure chamber, and the oil return structure includes an oil return channel and a one-way valve arranged at the oil return channel. The one-way valve can open the oil return channel when the oil level in the medium pressure chamber reaches a preset height.

[0030] According to another aspect of the present application, a scroll compressor is provided, comprising a compressor oil supply structure, wherein the compressor oil supply structure is the above-mentioned compressor oil supply structure.

[0031] The compressor oil supply structure provided by the present application includes a crankshaft, a moving plate, a stator plate and an upper bracket. The moving plate is rotatably connected to the eccentric part of the crankshaft through a moving plate bearing. A high-pressure chamber is formed between the eccentric part and the moving plate. A medium-pressure chamber is formed between the upper bracket, the moving plate and the crankshaft. The high-pressure chamber and the medium-pressure chamber are separated. A high-pressure oil groove connected to the high-pressure oil chamber is formed between the moving plate and the stator plate. The high-pressure chamber provides a second pressure to the moving plate, and the high-pressure oil groove provides a first pressure opposite to the second pressure to the moving plate. The compressor oil supply structure forms a high-pressure oil groove between the moving plate and the stationary plate that is connected to the high-pressure oil chamber. The high-pressure oil can be introduced into the high-pressure oil groove through the high-pressure oil chamber, so that the high-pressure pressure in the high-pressure oil groove is maintained. The high-pressure pressure in the high-pressure oil groove can be used to apply a force opposite to the high-pressure pressure in the high-pressure chamber to the moving plate. The compressor oil supply structure can be used to offset at least a part of, or even all of, the exhaust back pressure on the moving plate. This can reduce the proportion of exhaust pressure in the back pressure and increase the proportion of medium pressure in the back pressure. The medium pressure can effectively balance the overturning moment, effectively avoid the overturning of the moving plate, and improve the stability and reliability of the compressor operation structure. BRIEF DESCRIPTION OF THE DRAWINGS

[0032] Figure 1 This is a schematic diagram of the high-pressure oil tank structure of the compressor oil supply structure according to one embodiment of the present application;

[0033] Figure 2 This is a schematic cross-sectional structural diagram of a moving plate of a compressor oil supply structure according to an embodiment of the present application;

[0034] Figure 3 This is a three-dimensional structural schematic diagram of a stator plate of a compressor oil supply structure according to an embodiment of the present application;

[0035] Figure 4 This is a diagram of the oil circuit structure of a scroll compressor according to one embodiment of the present application;

[0036] Figure 5 This is a diagram of the oil circuit structure of a scroll compressor according to one embodiment of the present application;

[0037] Figure 6 This is a diagram of the oil circuit structure of a scroll compressor according to one embodiment of the present application;

[0038] Figure 7 This is a schematic diagram of the high-pressure oil tank structure of the compressor oil supply structure according to one embodiment of the present application;

[0039] Figure 8 This is a three-dimensional structural schematic diagram of a stator plate of a compressor oil supply structure according to an embodiment of the present application;

[0040] Fig. 9 This is a diagram of the oil circuit structure of a scroll compressor according to one embodiment of the present application;

[0041] Fig.10 This is a schematic diagram of the oil return structure of a scroll compressor according to an embodiment of the present application.

[0042] The reference numerals are as follows:

[0043] 1. Moving plate; 2. Static plate; 3. High-pressure area; 4. Medium-pressure area; 5. Oil storage chamber; 6. Convex ring; 7. Annular groove; 8. Moving plate bearing; 9. First oil supply channel; 10. Second oil supply channel; 11. Oil groove; 12. Crankshaft oil circuit; 13. Upper bracket oil circuit; 14. Oil return passage; 15. Upper bracket; 16. Crankshaft; 17. Eccentric part; 18. Main journal; 19. Main bearing; 20. Connecting hole; 21. First connecting passage; 22. First trimming; 23. Oil storage ring; 24. Second trimming; 25. Second connecting passage; 26. High-pressure chamber; 27. Medium-pressure chamber; 28. Oil return passage; 29. ​​One-way valve; 30. Moving plate sealing ring; 31. Crankshaft sealing ring. DETAILED DESCRIPTION

[0044] Usually, the moving plate bearing needs a lot of lubricating oil to keep it lubricated, so it is often necessary to introduce high-pressure oil from the bottom oil pool into the moving plate bearing cavity. This results in that in almost all compressors, the pressure on the back of the moving plate and within the moving plate bearing range must be the exhaust pressure. Based on this phenomenon, the back pressure of the current compressor is generally too large and difficult to control.

[0045] In order to solve the problems in the related art that the back pressure in the back pressure chamber of the compressor is difficult to control, the moving plate is prone to overturning, there is extra power consumption due to excessive back pressure, and the tooth head and end surface are prone to wear due to excessive back pressure, the technical solution of the present application is specially proposed.

[0046] See also Figures 1 to 10 As shown, the compressor oil supply structure includes a crankshaft 16, a moving plate 1, a stator plate 2 and an upper bracket 15. The moving plate 1 is rotatably connected to the eccentric portion 17 of the crankshaft 16 through a moving plate bearing 8. A high-pressure chamber 26 is formed between the eccentric portion 17 and the moving plate 1. A medium-pressure chamber 27 is formed between the upper bracket 15, the moving plate 1 and the crankshaft 16. The high-pressure chamber 26 is separated from the medium-pressure chamber 27. A high-pressure oil groove connected to the high-pressure oil chamber is formed between the moving plate 1 and the stator plate 2. The high-pressure chamber 26 provides a second pressure to the moving plate 1, and the high-pressure oil groove provides a first pressure opposite to the second pressure to the moving plate 1.

[0047] The compressor oil supply structure forms a high-pressure oil groove connected to the high-pressure oil chamber between the moving plate 1 and the stationary plate 2. The high-pressure oil can be introduced into the high-pressure oil groove through the high-pressure oil chamber to maintain a high-pressure pressure in the high-pressure oil groove. The high-pressure pressure in the high-pressure oil groove can be used to apply a force opposite to the high-pressure pressure in the high-pressure chamber to the moving plate 1. The compressor oil supply structure can be used to offset at least a part of, or even all of, the exhaust back pressure on the moving plate 1. This can reduce the proportion of exhaust pressure in the back pressure and increase the proportion of medium pressure in the back pressure. The medium pressure can effectively balance the overturning moment, effectively avoid the overturning of the moving plate 1, and improve the stability and reliability of the compressor operation structure.

[0048] The high-pressure oil chamber here may be an exhaust chamber in a compressor housing, or other chambers capable of providing high-pressure oil.

[0049] After the pressure area of ​​the high-pressure oil tank is reasonably designed, the high-pressure pressure applied to the moving disc 1 by the high-pressure oil in the high-pressure oil tank can be basically offset by the exhaust back pressure on the moving disc 1, so that the moving disc 1 can only leave the medium-pressure part to function. The medium pressure changes in proportion to the suction pressure, so the medium pressure can be made more controllable.

[0050] In this embodiment, the intermediate pressure is a pressure between the suction pressure and the exhaust pressure. The intermediate pressure is related to the suction pressure. The higher the suction pressure, the greater the intermediate pressure.

[0051] The high-pressure oil tank and the medium-pressure chamber 27 are isolated from each other and have a certain volume. Therefore, the oil in the compressor oil supply structure can be stored in the high-pressure oil tank instead of in the back-pressure chamber. The oil supply to the moving plate 1 and the stationary plate 2 of the compressor can be provided through the high-pressure oil tank, and there is no need to stir the oil pool through the moving plate 1. Therefore, the operating resistance of the moving plate 1 is reduced and the operating efficiency of the compressor is improved.

[0052] Since the high-pressure oil groove is located at the mating surface of the moving plate 1 and the stator plate 2, the high-pressure oil groove can store oil on the surface of the moving and stator plates. Compared with compressors in other related technologies, it has a more sufficient end face lubrication effect. At the same time, it will not reduce the oil flow entering the moving plate bearing 8, thereby improving the reliability of the compressor.

[0053] In one embodiment, the first pressure in the high-pressure oil tank acts on the area of ​​the moving disk 1 S1, and the second pressure in the high-pressure chamber 26 acts on the area of ​​the moving disk 1 S2, 0.5S2≤S1≤2S2. Since the pressures in the high-pressure oil tank and the high-pressure chamber 26 are both high-pressure pressures, the pressure difference between the two will not be too large. Therefore, in order to better balance the pressures on both ends of the moving disk 1, the effective areas of the two cannot differ too much. After analysis and verification, limiting the effective area relationship between the two within the above range can better control the pressure relationship at both ends of the moving disk 1, so that the high-pressure pressure generated by the oil in the high-pressure oil tank can better offset the high-pressure pressure generated by the oil in the high-pressure chamber 26, reduce the proportion of exhaust pressure in back pressure, and increase the proportion of medium pressure in back pressure.

[0054] In one embodiment, the first pressure in the high-pressure chamber 26 acts on the movable disc 1 with an area S1 and a first pressure P1, and the second pressure in the high-pressure oil tank acts on the movable disc 1 with an area S2 and a second pressure P2, P1*S1=P2*S2, thereby optimizing the pressure applied to the movable disc 1 by the high-pressure oil in the high-pressure chamber 26 and the pressure applied to the movable disc 1 by the high-pressure oil in the high-pressure oil tank, so that the two are completely equal and can be completely offset. As the best embodiment, when the high-pressure pressure generated by the oil in the high-pressure oil tank is completely offset by the high-pressure pressure generated by the oil in the high-pressure chamber 26, the back pressure is only a medium pressure at this time, and the controllability of the back pressure is the best, which can effectively improve the ability of the movable disc 1 to balance the overturning moment, while reducing the deformation of the movable disc 1.

[0055] See also Figure 2 , Figure 7 and Figure 8 As shown, in one embodiment, the end surface of the moving disk 1 facing the stator disk 2 is provided with a protrusion protruding toward the stator disk 2, and the end surface of the stator disk 2 facing the moving disk 1 is provided with a recessed portion. The protrusion can be movably arranged in the recessed portion and divides the recessed portion into a high-pressure area 3 and a medium-pressure area 4 isolated from each other. The high-pressure area 3 is connected to the high-pressure oil chamber through an oil inlet channel.

[0056] In addition, during the orbital motion of the moving plate 1 relative to the stationary plate 2, the ranges of the high-pressure area 3 and the medium-pressure area 4 will constantly change, so that oil lubrication can be supplied to different areas of the contact surface of the moving plate 1 and the stationary plate 2, thereby achieving lubrication of the sliding surfaces of the moving plate 1 and the stationary plate 2 and supplying oil to the mating surfaces of the moving plate 1 and the stationary plate 2.

[0057] In one embodiment, the compressor oil supply structure further includes an oil outlet channel, which is connected to the high-pressure area 3, and the oil entering the high-pressure area 3 from the oil inlet channel can flow out of the high-pressure area 3 through the oil outlet channel. By adding the oil outlet channel, the high-pressure oil tank formed by the high-pressure area 3 is connected to the oil inlet channel and the oil outlet channel respectively, and an oil circuit circulation can be formed, so that the oil can enter the high-pressure oil tank and flow out of the high-pressure oil tank, thereby ensuring the circulation of the oil and avoiding the problem of oil accumulation caused by the oil being accumulated in the high-pressure oil tank and unable to participate in the circulation in time.

[0058] In one embodiment, the protrusion is a protruding ring 6, the recess is an annular groove 7, the inner ring wall of the protruding ring 6 and the inner ring wall of the annular groove 7 form a high-pressure area 3, and the outer ring wall of the protruding ring 6 and the outer ring wall of the annular groove 7 form a medium-pressure area 4. Preferably, the protruding ring 6 is a circular ring with uniform wall thickness.

[0059] In this embodiment, the high-pressure area 3 is a dynamic annular oil groove. During the revolution of the moving disc 1, the range of the high-pressure area 3 will change with the movement of the convex ring 6, and the total lubrication area of ​​the high-pressure area 3 remains unchanged. The pressure provided by this dynamic and constant-area high-pressure oil groove can be balanced with the back pressure caused by the moving disc bearing 8 through appropriate design, so that most of the back pressure of the moving disc 1 is provided by the medium pressure. This improves the ability of the moving disc 1 to balance the overturning moment on the one hand, and makes the deformation of the moving disc 1 more controllable on the other hand, allowing the moving disc 1 to have a smaller upper bracket floating clearance. Since the high-pressure oil groove is always located on the surface of the moving disc 1, it can achieve stable lubrication of the moving disc 1 and the static disc 2.

[0060] The dynamic annular high-pressure oil groove forms a high-pressure oil thrust ring with a constant area on the surface of the movable plate 1. According to the oil pressure principle, when the movable plate 1 overturns, the contact area between the pressed part and the oil becomes larger, the oil pressure increases, and it starts to lift up, and the contact area between the lifted part and the oil becomes smaller, the oil pressure decreases, and it starts to drop, so that the movable plate 1 can return to its normal position. That is, this structure will use the change in oil pressure to automatically correct the overturning tendency of the movable plate 1 during operation, so that the contact surface lubrication of the movable plate 1 and the static plate 2 can always be adequately maintained, thereby reducing the wear on the tooth top.

[0061] See also Figures 1 to 3 As shown, in one embodiment, an oil storage chamber 5 is provided on the recessed portion of the stator disc 2, and the oil storage chamber 5 is intermittently connected to the high-pressure area 3 or the medium-pressure area 4, so that oil is stored in the high-pressure area 3 and oil is supplied to the medium-pressure area 4.

[0062] The oil supply structure of the compressor forms a high-pressure area 3 and a medium-pressure area 4 between the moving plate 1 and the stationary plate 2, and the high-pressure area 3 is always connected to the high-pressure oil chamber, and can continuously provide high-pressure oil to the high-pressure area 3 through the high-pressure oil chamber, and continuously supply oil to the high-pressure area 3, while the oil storage chamber 5 can be intermittently connected to the high-pressure area 3 or the medium-pressure area 4. When the oil storage chamber 5 is connected to the high-pressure area 3, the high pressure of the high-pressure area 3 can be used to fill the oil storage chamber 5 with oil. When the oil storage chamber 5 is connected to the medium-pressure area 4, the high-pressure oil stored in the oil storage chamber 5 enters the medium-pressure area 4 under the action of oil pressure and gravity, and replenishes the oil for the medium-pressure area 4. Since the volume of the oil storage chamber 5 is constant, and the oil in the high-pressure area 3 can only enter the medium-pressure area 4 through the oil storage chamber 5, it is possible to ensure that the supply of oil entering the medium-pressure area 4 through the oil storage chamber 5 is constant, thereby achieving stable oil supply to the pump body and precise control of the oil supply amount.

[0063] In this embodiment, the high-pressure area 3 is a closed high-pressure oil tank, and the medium-pressure area 4 is a medium-pressure oil tank. The medium-pressure oil tank is connected to the back-pressure chamber. The oil in the high-pressure oil tank enters the medium-pressure oil tank through the oil storage chamber 5, and then enters the medium-pressure back-pressure chamber from the medium-pressure oil tank to supply oil to the back-pressure chamber.

[0064] See also Figure 1 As shown, it shows a schematic diagram of the high-pressure oil tank formed by the moving and static disks at a certain moment. It can be seen from the figure that during the revolution of the moving disk 1, the high-pressure oil tank intermittently covers the range of the oil storage chamber 5, wherein the connection relationship between the high-pressure oil tank and the oil storage chamber 5 is determined by the revolution position of the moving disk 1. After the oil storage chamber 5 enters the range of the high-pressure oil tank, the oil storage chamber 5 is filled with the oil in the high-pressure oil tank. Then, when the high-pressure oil tank leaves this range, under the action of the surface tension, oil pressure and gravity of the protruding part of the moving disk 1, the oil in the oil storage chamber 5 will fall into the medium-pressure back pressure chamber, thereby providing lubrication for the anti-rotation mechanism.

[0065] Since the moving plate 1 has a larger mating surface for the high-pressure oil groove, the oil attached to the surface of the moving plate 1 will also continuously enter the pump body as the moving plate revolves. Therefore, compared with other traditional compressors in which the oil in the back pressure chamber needs to satisfy the lubrication of the anti-self-rotation device and supply oil to the medium-pressure oil groove and the pump body during the operation of the moving plate 1, the oil storage chamber 5 of the compressor oil supply structure of the embodiment of the present application only needs to satisfy the lubrication of the anti-self-rotation mechanism, so the oil supply can be controlled more accurately.

[0066] The oil storage cavity 5 is, for example, an oil storage hole or an oil storage tank, and the cross-sectional shape of the oil storage hole or the oil storage tank is, for example, circular, triangular, rectangular, elliptical, etc. The overall structure of the oil storage hole or the oil storage tank can be cylindrical, truncated cone, prism, prism, cone, pyramid, etc.

[0067] In one embodiment, the oil storage chamber 5 is arranged at the bottom of the recessed portion, and there are at least two oil storage chambers 5. At least two oil storage chambers 5 are arranged along the circumference of the stator plate 2. When the moving plate 1 revolves to different positions, lubricating oil can be provided to the back pressure chamber in a timely manner to ensure the oil supply frequency and achieve stable oil supply.

[0068] As a preferred embodiment, there are four oil storage chambers 5, and the four oil storage chambers 5 are evenly arranged along the circumference of the static plate 2. The oil supply frequency of the oil storage chamber 5 to the back pressure chamber can be reasonably adjusted through the four oil storage chambers 5, and the uniformity and stability of the oil supply frequency can be ensured through the setting positions of the four oil storage chambers 5. The reason for setting four oil storage chambers 5 is that for the moving plate 1, during the revolution, its movement is mainly composed of sliding in two directions perpendicular to each other, and there are four farthest sliding points in the two sliding directions, which can just correspond to the circumferential positions of the four oil storage chambers 5, so it can better match the revolution trajectory of the moving plate 1, making the overall structural design more reasonable.

[0069] In one embodiment, when the convex ring 6 moves to the oil storage chamber 5, the convex ring 6 can completely cover the oil storage chamber 5, thereby preventing the high-pressure oil grooves on both sides of the convex ring 6 from being connected to the medium-pressure oil grooves when the oil storage chamber 5 moves to the position of the convex ring 6, resulting in the phenomenon of high-pressure and low-pressure being connected. The stability and reliability of the compressor oil supply structure are effectively improved. Preferably, the radial thickness of the convex ring 6 is greater than the radial distance between the two farthest points of the oil storage chamber 5 in the radial direction, thereby effectively ensuring the sealing effect of the convex ring 6 on the oil storage chamber 5.

[0070] In one embodiment, the minimum distance between the oil storage chamber 5 and the outer ring wall of the annular groove 7 is greater than the thickness of the convex ring 6, thereby ensuring that when the convex ring 6 moves to the minimum position from the outer ring wall of the annular groove 7, the oil storage chamber 5 can be completely located inside the inner ring wall of the convex ring 6, and oil can be fully stored, thereby avoiding interference of the convex ring 6 with the oil storage chamber 5.

[0071] In one embodiment, the minimum distance between the oil storage chamber 5 and the inner ring wall of the annular groove 7 is greater than the thickness of the convex ring 6, thereby ensuring that when the convex ring 6 moves to the minimum position away from the inner ring wall of the annular groove 7, the oil storage chamber 5 can be completely located outside the outer ring wall of the convex ring 6, so that the oil stored in the oil storage chamber 5 can be fully released to the back pressure chamber, avoiding interference of the convex ring 6 with the oil storage chamber 5.

[0072] In one embodiment, when the preset point on the convex ring 6 moves to the farthest position from the inner ring wall of the annular groove 7, the oil storage chamber 5 located on the same radial direction as the preset point can be completely located in the high-pressure area 3, and when the preset point on the convex ring 6 moves to the closest position to the inner ring wall of the annular groove 7, the oil storage chamber 5 located on the same radial direction as the preset point can be completely located in the medium-pressure area 4, thereby ensuring that the setting position of the oil storage chamber 5 is accurate, and regular intermittent connection with the high-pressure area 3 and the medium-pressure area 4 can be achieved, thereby ensuring the stability and reliability of oil storage and oil discharge of the oil storage chamber 5.

[0073] In one embodiment, during the entire movement of the moving plate 1, the moving plate 1 does not collide with the inner annular wall or the outer annular wall of the annular groove 7, thereby effectively avoiding interference between the moving plate 1 and the stationary plate 2 during the orbital motion, thereby ensuring the safe and stable operation of the compressor oil supply structure.

[0074] In one embodiment, the compression chamber of the static plate 2 is not connected with the high-pressure area 3, so that the low-pressure oil in the compression chamber of the static plate 2 and the high-pressure oil in the high-pressure area 3 will not be connected, thereby avoiding the connection between the compression chamber of the static plate 2 and the high-pressure area 3, and improving the reliability of the moving plate 1 and the static plate 2 during movement.

[0075] In one embodiment, a moving disc bearing 8 and a first oil supply channel 9 are provided on the moving disc 1. The moving disc bearing 8 is provided on the back side of the moving disc 1 away from the stationary disc 2. The first end of the first oil supply channel 9 is connected to the high-pressure area 3, and the second end of the first oil supply channel 9 is connected to the inner cavity of the moving disc bearing 8. The high-pressure oil tank of the high-pressure area 3 is connected to the inner cavity of the moving disc bearing 8 of the moving disc 1 through the first oil supply channel 9. The first oil supply channel 9 can be used as both an oil inlet channel and an oil outlet channel. When used as an oil inlet channel, the high-pressure oil in the moving disc bearing 8 enters the high-pressure area 3 through the first oil supply channel 9 to provide high-pressure oil for the high-pressure area 3. When used as an oil outlet channel, the high-pressure oil in the high-pressure area 3 can enter the inner cavity of the moving disc bearing 8 through the first oil supply channel 9 to realize the circulation of the high-pressure oil in the high-pressure area 3.

[0076] The inner cavity of the movable plate bearing 8 is a high-pressure cavity, and the outer cavity of the movable plate bearing 8 is a medium-pressure cavity. The high-pressure cavity and the medium-pressure cavity are sealed and separated to avoid the high-pressure cavity and the medium-pressure cavity from being connected, so that the back-pressure cavity always remains a medium-pressure cavity.

[0077] In one embodiment, a second oil supply channel 10 is provided on the stator 2, and a first end of the second oil supply channel 10 is connected to the high pressure area 3, and a second end of the second oil supply channel 10 is provided on the outer peripheral side of the annular groove 7 and is spaced apart from the annular groove 7, so as to avoid the second end of the second oil supply channel 10 being directly connected to the high pressure oil groove. The second oil supply channel 10 can be used as both an oil inlet channel and an oil outlet channel. When used as an oil inlet channel, the high pressure oil in the compressor housing enters the high pressure area 3 through the second oil supply channel 10, and provides the high pressure oil for the high pressure area 3. When used as an oil outlet channel, the high pressure oil in the high pressure area 3 can flow out to the compressor housing through the second oil supply channel 10, and the circulation of the high pressure oil in the high pressure area 3 is realized.

[0078] The first end of the second oil supply channel 10 is arranged on the inner circumference of the annular groove 7, and an oil groove 11 is arranged on the end surface of the stator plate 2 located on the inner circumference of the annular groove 7. The first end of the second oil supply channel 10 is connected with the high-pressure area 3 through the oil groove 11. The setting of the oil groove 11 makes it more convenient to connect the second oil supply channel 10 with the annular groove 7.

[0079] Most traditional compressors supply oil from the bottom of the moving plate bearing 8 of the moving plate 1, bringing a small amount of oil to the medium-pressure chamber, and then entering the pump body under the stirring of the moving plate 1. Since the pressure of the medium-pressure chamber needs to be constant, the amount of oil entering the medium-pressure chamber is generally small relative to the oil in each moving plate bearing. However, the high-pressure oil tank used for the oil supply structure of the oil supply compressor in the present application can be used as a part of the oil circuit circulation, so a large amount of oil flows through, and the continuous change of the annular oil tank area can be used to achieve oil supply and lubrication of the pump body, and the oil storage chamber 5 can be used to achieve continuous and stable oil supply to the back pressure chamber. Therefore, the compressor oil supply structure of the present application can still achieve stable oil supply to the pump body without relying on the stirring of the moving plate 1 to supply oil, wasting power and increasing the oil circulation rate.

[0080] At the same time, since the high-pressure oil tank is relatively sealed, only a small amount of oil for lubrication of the anti-rotation mechanism will flow into the medium-pressure chamber. Compared with the compressor with an oil pool in the back-pressure chamber, the compressor oil supply structure of the present application reduces the amount of oil in contact with the refrigerant, which can effectively reduce the oil circulation rate, reduce the miscibility of the refrigerant and the oil, and improve the system performance.

[0081] The oil storage chamber 5 of the compressor oil supply structure of the present application is intermittently connected to the high-pressure oil tank during operation, during which the oil storage chamber 5 is filled with oil. After the high-pressure oil tank leaves the oil storage chamber 5, this part of the oil naturally falls into the anti-self-rotation mechanism for lubrication under the action of oil pressure, so that the oil brought out by each rotation of the compressor is quantitative and the oil supply is controllable. Since this part of the oil only needs to meet the lubrication of the anti-self-rotation mechanism, this part of the oil is less and the oil circulation rate is low.

[0082] The compressor oil supply structure of the present application stores sufficient high-pressure oil on the end surfaces of the movable and static plates. During the revolution of the movable plate 1, the revolution of the movable plate 1 will bring a sufficient and stable amount of lubricating oil into the meshing part of the movable and static plate profiles, without the need to introduce a medium-pressure oil tank like a traditional compressor.

[0083] The high-pressure oil tank of the compressor oil supply structure of the present application can play a role similar to that of a sliding movable plate bearing, that is, in the rapidly rotating lubricating oil, the oil pressure is high in narrow places and low in wide places. When the movable plate 1 tends to overturn, the height of the high-pressure oil tank on one side will inevitably become lower due to the overturning, and the height of the other side will become higher. This will form a torque that suppresses the overturning of the movable plate 1, thereby reducing the wear of the movable plate 1 caused by the overturning and improving reliability.

[0084] See also Figure 4 As shown, in one embodiment, the scroll compressor also includes an oil pump, a crankshaft oil circuit 12, an upper bracket oil circuit 13 and an oil return passage 14, the crankshaft 16 also includes a main journal 18, a main bearing 19 is arranged between the main journal 18 and the upper bracket 15, a moving plate bearing 8 and a first oil supply channel 9 are arranged on the moving plate 1, and a second oil supply channel 10 is arranged on the stator 2. The oil flows back to the oil pool through the crankshaft oil circuit 12, the upper bracket oil circuit 13, the second oil supply channel 10, the high-pressure area 3, the first oil supply channel 9, the inner cavity of the moving plate bearing 8 and the oil return passage 14 in sequence.

[0085] A connecting hole 20 is provided on the main bearing 19 to connect the crankshaft oil circuit 12 and the upper bracket oil circuit 13. A first connecting channel 21 is provided between the main journal 18 and the main bearing 19. One end of the first connecting channel 21 is connected to the connecting hole 20, and the other end is connected to the crankshaft 16 oil circuit. After the high-pressure oil is transported from the crankshaft oil circuit 12 to the first connecting channel 21, it can reach the connecting hole 20 along the first connecting channel 21, and then be sent to the upper bracket oil circuit 13 through the connecting hole 20, so that the high-pressure oil can be transported to the high-pressure oil tank through the upper bracket oil circuit 13 and the second oil supply channel 10. In order to ensure that the high-pressure oil can be continuously transported to the upper bracket oil circuit 13 during the rotation of the crankshaft 16, an annular oil groove can also be provided between the main journal 18 and the main bearing 19. The annular oil groove can always connect the first connecting channel 21 with the connecting hole 20 during the process of the outlet of the crankshaft oil circuit 12 changing along the circumferential direction.

[0086] In one embodiment, a first trimming edge 22 is provided on one side of the main journal 18, the first trimming edge 22 extends along the axial direction of the main journal 18, a first communication channel 21 is formed between the first trimming edge 22 and the main bearing 19, an oil storage ring 23 is provided on the inner peripheral wall of the upper bracket 15, the oil storage ring 23 extends along the circumference of the main journal 18, and the communication hole 20 is connected with the upper bracket oil passage 13 through the oil storage ring 23. In this embodiment, the existence of the first trimming edge 22 enables the first communication channel 21 to be formed between the main journal 18 and the main bearing 19, facilitating the delivery of high-pressure oil. In this embodiment, the position of the first trimming edge 22 is the exit position of the crankshaft oil circuit 12, that is, the crankshaft oil circuit 12 is located on the first trimming edge 22, and at least one connecting hole 20 on the main bearing 19 is also connected to the first trimming edge 22 along the circumferential direction, so that the connecting hole 20 and the first connecting channel 21 are always connected, so that the high-pressure oil in the crankshaft oil circuit can directly enter the first connecting channel 21 after flowing out, and then flow to the upper bracket oil circuit 13 through the first connecting channel 21. The oil storage ring 23 can make the first connecting channel 21 always connected to the upper bracket oil circuit 13 through the connecting hole 20 on the main bearing 19, so as to ensure that the high-pressure oil can be continuously transported to the high-pressure oil tank. At the same time, the oil storage ring 23 can form an oil storage space for oil storage, so that a buffer space can be formed when the oil pressure is too large to effectively buffer the oil. The cross-section of the oil storage ring 23 is, for example, semicircular, semi-elliptical, inferior arc, trapezoidal, rectangular or triangular. In this embodiment, the main bearing 19 can rotate with the main journal 18. Therefore, in order to ensure the connectivity between the connecting hole 20 and the oil storage ring 23 so that the high-pressure oil can be delivered to the upper bracket oil circuit 13 in a timely and effective manner, multiple connecting holes 20 can be arranged along the circumference of the main bearing 19.

[0087] In one embodiment, a second trimming edge 24 is provided on one side of the eccentric portion 17, and the second trimming edge 24 extends along the axial direction of the eccentric portion 17. A second connecting passage 25 is formed between the second trimming edge 24 and the movable plate bearing 8, and the high-pressure chamber 26 is connected to the oil return passage 14 through the second connecting passage 25. The high-pressure oil in the high-pressure chamber 26 can flow back to the oil pool at the bottom of the compressor from the oil return passage 14 through the second connecting passage 25. In this embodiment, an annular passage is formed between the movable plate bearing 8 and the end surface of the main journal 18, and the second connecting passage 25 is connected to the oil return passage 14 through the annular passage. In this way, even if the eccentric portion 17 rotates with the crankshaft 16, it will not affect the flow of the high-pressure oil in the high-pressure chamber 26 of the movable plate bearing 8, thereby ensuring the normal circulation of the high-pressure oil.

[0088] For this embodiment, the oil pump is connected to the crankshaft 16 and can supply oil from the bottom of the oil pool of the compressor, and introduce the lubricating oil into the second oil supply channel 10 on the stator 2 along the upper bracket oil path 13 of the upper bracket 15 through the oil hole on the main bearing 19. During the compression process, oil is pumped into the crankshaft oil circuit 12 from the oil pump, and then injected into the oil circuit outlet on the main journal 18 along the crankshaft oil circuit 12. A first trimming edge 22 is provided on the main journal 18, and an oil storage ring 23 is provided on the upper bracket 15 corresponding to the first trimming edge 22. An upper bracket oil circuit 13 is provided on the upper bracket 15. After the oil is stored and lubricated in the main bearing 19, it is introduced into the second oil supply channel 10 along the upper bracket oil circuit 13, and enters the high-pressure oil tank of the high-pressure area 3 along the second oil supply channel 10, and then flows out from the first oil supply channel 9, enters the inner cavity of the movable plate bearing 8, provides high-pressure oil for the inner cavity of the movable plate bearing 8, and uses the high-pressure oil to lubricate the movable plate bearing 8. After that, the high-pressure oil flows out from the inner cavity of the movable plate bearing 8, stays through the second trimming edge 24 on the side of the eccentric part 17, and then flows back to the oil pool through the oil return passage 14 provided on the upper bracket 15 on the inner side of the movable plate sealing ring 30, realizing oil circuit circulation. In this process, the second oil supply passage 10 serves as an oil inlet passage of the high-pressure oil tank, and the first oil supply passage 9 serves as an oil outlet passage of the high-pressure oil tank.

[0089] In this embodiment, a sealing structure is formed between the moving plate bearing 8 and the upper bracket 15, and a flange structure is provided at the end of the moving plate bearing 8 close to the main journal 18. The diameter of the flange structure needs to be large enough to ensure that the flange structure can always contact with the moving plate sealing ring 30 during the revolution of the moving plate 1 to maintain the seal. In this embodiment, the moving plate sealing ring 30 is provided on the upper bracket 15, and a dynamic seal is formed between the flange structure of the moving plate 1 and the moving plate sealing ring 30.

[0090] See also Figure 5 As shown, in one embodiment, the scroll compressor also includes a crankshaft oil circuit 12, an upper bracket oil circuit 13 and an oil return passage 14. When a moving plate bearing 8 and a first oil supply passage 9 are provided on the moving plate 1, and a second oil supply passage 10 is provided on the stator plate 2, the oil flows back to the oil pool through the crankshaft oil circuit 12, the inner cavity of the moving plate bearing 8, the first oil supply passage 9, the high-pressure area 3, the second oil supply passage 10 and the oil return passage 14 in sequence.

[0091] For this embodiment, during the compression process, the oil is first led out from the bottom of the crankshaft to the inner cavity of the movable plate bearing 8 of the movable plate 1, and then enters the high-pressure oil tank along the first oil supply channel 9, and then flows out from the second oil supply channel 10 through the high-pressure oil tank, and is led back to the upper bracket, and finally directly led back to the bottom oil pool by the oil return passage 14 on the upper bracket, so as to realize the oil circuit circulation. In this process, the first oil supply channel 9 serves as the oil inlet channel of the high-pressure oil tank, and the second oil supply channel 10 serves as the oil outlet channel of the high-pressure oil tank. In this embodiment, the oil circuit structure is simpler, and there is no need to open an upper bracket oil circuit on the upper bracket, so the number of parts can be reduced, the number of holes in the upper bracket can be reduced, and the processing cost can be reduced.

[0092] See also Figure 6 As shown, in this embodiment, the high-pressure oil tank is only connected to the oil inlet channel, and no oil outlet channel is provided, so the high-pressure oil will be stored in the high-pressure oil tank. In this case, the oil in the high-pressure oil tank only plays a role in enhancing lubrication and preventing overturning, and does not form an oil circuit circulation.

[0093] See also Fig. 9 As shown, it is Figure 4 The embodiment of the present invention is basically the same as that of the embodiment of the present invention, except that, in the present embodiment, the end of the movable plate bearing 8 is not provided with a flange structure, and the movable plate sealing ring 30 is directly installed in the sealing groove of the end face of the movable plate bearing 8, and performs orbital motion with the movable plate bearing 8, and realizes dynamic sealing with the end face of the main journal 18. At the same time, in order to ensure the sealing performance of the upper bracket 15 and the main journal 18 at the end, a flange structure is provided at the end where the main journal 18 and the movable plate bearing 8 match, and a sealing gap is formed between the flange structure and the upper bracket 15, and a crankshaft sealing ring 31 is provided in the sealing gap to ensure the sealing effect between the crankshaft 16 and the upper bracket 15.

[0094] In the present embodiment, since the moving plate sealing ring 30 does not need to realize the sealing between the crankshaft 16 and the upper bracket 15, there is no need to set up an additional oil return passage 14. The crankshaft 16 can realize oil return by setting up an oil return pipeline inside the crankshaft 16. Moreover, since there is no need to set a flange structure for the moving plate bearing 8, the structure of the upper bracket 15 can be made more compact.

[0095] See also Fig.10 As shown, it is Figure 5 The embodiment is basically the same, but the seal between the moving plate bearing 8, the crankshaft 16 and the upper bracket 15 adopts Fig. 9 In a similar manner, in addition, in this embodiment, an oil return structure is provided at the bottom of the medium pressure chamber 27, and the oil return structure includes an oil return channel 28 and a one-way valve 29 provided at the oil return channel 28, and the one-way valve 29 can open the oil return channel 28 when the oil level in the medium pressure chamber 27 reaches a preset height.

[0096] In the oil circuit structure of this embodiment, the oil in the medium-pressure chamber 27 is not required to lubricate the pump body under the stirring of the moving plate 1. Therefore, the oil circuit structure of this embodiment needs to drain the excess lubricating oil remaining in the medium-pressure chamber 27 in time to avoid the moving plate 1 wasting power to stir the oil in the medium-pressure chamber. The oil circuit structure of this embodiment, by providing an oil return structure at the lower oil level of the medium-pressure chamber 27, adds an oil return channel 28 at the lower oil level of the medium-pressure chamber 27, and installs a one-way valve 29 at the oil return channel 28, so as to realize the oil return of the medium-pressure chamber 27 to the bottom oil pool.

[0097] In one embodiment, a one-way valve 29 is provided in the oil return channel 28. The one-way valve 29 is used to prevent the high-pressure oil from entering the medium-pressure chamber 27 through the oil return channel 28. An oil pump is also provided at the oil return channel 28. The oil pump is arranged at one end of the one-way valve 29 close to the medium-pressure chamber 27. A liquid level detector for detecting the oil height is provided in the medium-pressure chamber 27. When the oil height reaches a preset high speed, the liquid level detector will send the liquid level information to the controller. The controller will control the oil pump to make the oil pump work and pump oil to the high-pressure side. When the oil pumping pressure is greater than the oil pressure on the high-pressure side, the one-way valve 29 opens, and the oil is pumped to the high-pressure side through the oil return channel 28, thereby realizing the oil return to the medium-pressure chamber 27.

[0098] See also Figures 1 to 10 As shown, according to an embodiment of the present application, the scroll compressor includes a compressor oil supply structure, and the compressor oil supply structure is the above-mentioned compressor oil supply structure.

[0099] It is easy for those skilled in the art to understand that, under the premise of no conflict, the above-mentioned advantageous methods can be freely combined and superimposed.

[0100] The above are only preferred embodiments of the present application and are not intended to limit the present application. Any modifications, equivalent replacements and improvements made within the spirit and principles of the present application shall be included in the protection scope of the present application. The above are only preferred implementations of the present application. It should be pointed out that for ordinary technicians in this technical field, several improvements and variations can be made without departing from the technical principles of the present application, and these improvements and variations should also be regarded as the protection scope of the present application.

Claims

1. A compressor oil supply structure, characterized in that: The invention comprises a crankshaft (16), a moving plate (1), a stationary plate (2) and an upper bracket (15), wherein the moving plate (1) is rotatably connected to an eccentric portion (17) of the crankshaft (16) via a moving plate bearing (8), a high-pressure chamber (26) is formed between the eccentric portion (17) and the moving plate (1), a medium-pressure chamber (27) is formed between the upper bracket (15), the moving plate (1) and the crankshaft (16), the high-pressure chamber (26) and the medium-pressure chamber (27) are spaced apart, a high-pressure oil groove connected to the high-pressure oil chamber is formed between the moving plate (1) and the stationary plate (2), the high-pressure chamber (26) provides a second pressure to the moving plate (1), and the high-pressure oil groove provides a first pressure opposite to the second pressure to the moving plate (1); The end surface of the moving plate (1) facing the stationary plate (2) is provided with a protrusion protruding toward the stationary plate (2), and the end surface of the stationary plate (2) facing the moving plate (1) is provided with a recessed portion, the protrusion being movably arranged in the recessed portion and dividing the recessed portion into a high-pressure area (3) and a medium-pressure area (4) isolated from each other, the high-pressure area (3) being connected to the high-pressure oil chamber through an oil inlet channel; the high-pressure area (3) forms the high-pressure oil groove; The compressor oil supply structure further comprises an oil outlet passage, the oil outlet passage being in communication with the high-pressure region (3), and the oil entering the high-pressure region (3) from the oil inlet passage can flow out of the high-pressure region (3) via the oil outlet passage; An oil storage chamber (5) is provided on the recessed portion of the stator (2), and the oil storage chamber (5) is intermittently connected to the high-pressure area (3) or the medium-pressure area (4), stores oil in the high-pressure area (3), and supplies oil to the medium-pressure area (4).

2. The compressor oil supply structure according to claim 1, characterized in that: The first pressure in the high-pressure oil groove acts on an area S1 of the movable plate (1), and the second pressure in the high-pressure chamber (26) acts on an area S2 of the movable plate (1), 0.5S2≤S1≤2S2.

3. The compressor oil supply structure according to claim 1, characterized in that: The first pressure in the high-pressure chamber (26) acts on the movable disc (1) with an area S1, and the first pressure is P1. The second pressure in the high-pressure oil groove acts on the movable disc (1) with an area S2, and the second pressure is P2. P1*S1=P2*S2.

4. The compressor oil supply structure according to claim 1, characterized in that: The protruding portion is a protruding ring (6), the recessed portion is an annular groove (7), the inner annular wall of the protruding ring (6) and the inner annular wall of the annular groove (7) enclose the high-pressure area (3), and the outer annular wall of the protruding ring (6) and the outer annular wall of the annular groove (7) enclose the medium-pressure area (4).

5. The compressor oil supply structure according to claim 4, characterized in that: The high-pressure region (3) is a dynamic annular oil groove. During the revolution of the moving disc (1), the range of the high-pressure region (3) changes, but the total area of ​​the high-pressure region (3) remains unchanged.

6. The compressor oil supply structure according to claim 1, characterized in that: The oil storage cavity (5) is arranged at the bottom of the recessed portion, there are at least two oil storage cavities (5), and at least two of the oil storage cavities (5) are arranged along the circumference of the stator (2).

7. The compressor oil supply structure according to claim 1, characterized in that: When the protruding portion is a protruding ring (6) and the recessed portion is an annular groove (7), when the protruding ring (6) moves to the oil storage chamber (5), the protruding ring (6) can completely cover the oil storage chamber (5).

8. The compressor oil supply structure according to claim 1, characterized in that: When the protruding portion is a protruding ring (6) and the recessed portion is an annular groove (7), the minimum distance between the oil storage cavity (5) and the outer annular wall of the annular groove (7) is greater than the thickness of the protruding ring (6); and / or the minimum distance between the oil storage cavity (5) and the inner annular wall of the annular groove (7) is greater than the thickness of the protruding ring (6).

9. The compressor oil supply structure according to claim 1, characterized in that: When the protruding portion is a protruding ring (6) and the recessed portion is an annular groove (7), when the preset point on the protruding ring (6) moves to the position farthest from the inner ring wall of the annular groove (7), the oil storage cavity (5) located on the same radial direction as the preset point can be completely located within the high-pressure area (3), and when the preset point on the protruding ring (6) moves to the position closest to the inner ring wall of the annular groove (7), the oil storage cavity (5) located on the same radial direction as the preset point can be completely located within the medium-pressure area (4).

10. The compressor oil supply structure according to claim 1, characterized in that: When the protruding portion is a protruding ring (6) and the recessed portion is an annular groove (7), during the entire movement process of the moving disc (1), the moving disc (1) does not collide with the inner annular wall or the outer annular wall of the annular groove (7).

11. The compressor oil supply structure according to claim 1, characterized in that: The movable plate (1) is provided with a movable plate bearing (8) and a first oil supply channel (9); the movable plate bearing (8) is arranged on the back side of the movable plate (1) away from the stationary plate (2); a first end of the first oil supply channel (9) is connected to the high-pressure area (3); a second end of the first oil supply channel (9) is connected to the inner cavity of the movable plate bearing (8); the first oil supply channel (9) serves as an oil inlet channel or an oil outlet channel.

12. The compressor oil supply structure according to claim 4, characterized in that: The stator plate (2) is provided with a second oil supply passage (10), a first end of the second oil supply passage (10) being connected to the high-pressure area (3), and a second end of the second oil supply passage (10) being arranged on the outer peripheral side of the annular groove (7) and spaced apart from the annular groove (7); the second oil supply passage (10) serves as an oil inlet passage or an oil outlet passage.

13. The compressor oil supply structure according to claim 12, characterized in that: The first end of the second oil supply passage (10) is arranged on the inner circumference side of the annular groove (7), and the stator (2) is provided with an oil groove (11) on the end surface of the inner circumference side of the annular groove (7), and the first end of the second oil supply passage (10) is connected to the high-pressure area (3) through the oil groove (11).

14. The compressor oil supply structure according to any one of claims 4 to 13, characterized in that: The compressor oil supply structure further comprises a crankshaft oil circuit (12), an upper bracket oil circuit (13) and an oil return passage (14); when a first oil supply passage (9) is provided on the moving plate (1) and a second oil supply passage (10) is provided on the stationary plate (2), oil flows back to the oil pool in sequence through the crankshaft oil circuit (12), the upper bracket oil circuit (13), the second oil supply passage (10), the high-pressure area (3), the first oil supply passage (9), the inner cavity of the moving plate bearing (8) and the oil return passage (14); the second oil supply passage (10) serves as an oil inlet passage and the first oil supply passage (9) serves as an oil outlet passage.

15. The compressor oil supply structure according to claim 14, characterized in that: The crankshaft (16) further comprises a main journal (18), a main bearing (19) being arranged between the main journal (18) and the upper bracket (15), a connecting hole (20) being arranged on the main bearing (19) for connecting the crankshaft oil circuit (12) and the upper bracket oil circuit (13), a first connecting channel (21) being arranged between the main journal (18) and the main bearing (19), one end of the first connecting channel (21) being connected to the connecting hole (20), and the other end being connected to the crankshaft (16) oil circuit.

16. The compressor oil supply structure according to claim 15, characterized in that: One side of the main journal (18) has a first cut edge (22), the first cut edge (22) extending in the axial direction of the main journal (18), and the first connecting passage (21) is formed between the first cut edge (22) and the main bearing (19). An oil storage ring (23) is provided on the inner peripheral wall of the upper bracket (15), the oil storage ring (23) extending in the circumferential direction of the main journal (18), and the connecting hole (20) is connected to the oil passage (13) of the upper bracket through the oil storage ring (23).

17. The compressor oil supply structure according to claim 14, characterized in that: A second cut edge (24) is provided on one side of the eccentric portion (17), the second cut edge (24) extending along the axial direction of the eccentric portion (17), a second connecting passage (25) is formed between the second cut edge (24) and the movable plate bearing (8), and the high-pressure chamber (26) is connected to the oil return passage (14) through the second connecting passage (25).

18. The compressor oil supply structure according to any one of claims 4 to 13, characterized in that: The compressor oil supply structure also includes a crankshaft oil circuit (12) and an oil return passage (14). When a first oil supply passage (9) is provided on the moving plate (1) and a second oil supply passage (10) is provided on the stationary plate (2), the oil flows back to the oil pool in sequence through the crankshaft oil circuit (12), the inner cavity of the moving plate bearing (8), the first oil supply passage (9), the high-pressure area (3), the second oil supply passage (10) and the oil return passage (14); the first oil supply passage (9) serves as an oil inlet passage and the second oil supply passage (10) serves as an oil outlet passage.

19. The compressor oil supply structure according to any one of claims 1 to 13, characterized in that: An oil return structure is provided at the bottom of the medium-pressure chamber (27), the oil return structure comprising an oil return channel (28) and a one-way valve (29) provided at the oil return channel (28), the one-way valve (29) being capable of opening the oil return channel (28) when the oil level in the medium-pressure chamber (27) reaches a preset height.

20. A scroll compressor, comprising a compressor oil supply structure, characterized in that: The compressor oil supply structure is the compressor oil supply structure according to any one of claims 1 to 19.

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