An oil return structure of a compressor, a compressor and an air conditioner

Abstract

The present invention provides an oil return structure for a compressor, a compressor, and an air conditioner. The oil return structure of the compressor includes: a bracket, a moving disk, a static disk, a cover body, a crankshaft, and a first bearing. The interior of the bracket has a lubrication cavity, and the first bearing is disposed in the lubrication cavity. One axial end of the crankshaft penetrates into the lubrication cavity and is supported by the first bearing; an oil storage cavity is further formed inside the bracket, and the oil storage cavity is located radially outside the lubrication cavity; the side of the oil storage cavity facing the moving disk has an opening, and a sealing cover plate is arranged at the opening, and the sealing cover plate can move along the axial direction of the crankshaft. Through the effective design inside the bracket, the present invention effectively utilizes this part of the space, so that an oil storage cavity is effectively formed without increasing the axial and radial dimensions of the compressor, while increasing the oil storage volume of the lubricating oil without increasing the weight and size of the compressor.

Description

Technical Field

[0001] The present invention relates to the technical field of compressors, and in particular to an oil return structure of a compressor, a compressor and an air conditioner. Background Art

[0002] For vehicle aluminum alloy scroll compressors, there is no stable oil sump inside the compressor for the internal oil pumping system of the compressor to mechanically supply oil to the lubrication parts. Instead, it relies on the suction refrigerant of the compressor to carry lubricating oil. After the refrigerant and lubricating oil are centrifugally separated during exhaust, a throttling oil return design is carried out on the lubricating oil. Therefore, the oil return efficiency of the exhaust centrifugal separation is crucial for the performance and reliability of the compressor. The existing centrifugal separation structures are very mature. The simple centrifugal separation structure has a very high separation efficiency and can fully meet the separation of most of the lubricating oil from the refrigerant. However, for the lubricating oil separated and then flowing back into the compressor, there are major problems in the existing technical solutions, mainly concentrated in: 1. The existing oil return lubrication structures directly return the high-temperature lubricating oil from the exhaust to the lubrication parts inside the compressor. The lubricating oil has a high temperature and poor lubrication effect; 2. The oil return oil storage structure is not reasonably set, and the oil storage structure is easily affected by the centrifugal separation structure, resulting in a small amount of oil stored in the actual oil storage structure or the separated lubricating oil being carried away by the refrigerant again; 3. The oil return structure directly uses a throttling structure to connect the high pressure to the low pressure or medium pressure lubrication parts. Due to the large throttling pressure difference, there is insufficient throttling during actual operation in the large pressure difference working condition, resulting in high-pressure gas entering the low pressure or medium pressure parts and affecting the performance of the compressor; in the small pressure difference working condition, the oil return flow is too small, and the lubricating oil separated by the centrifugal separation structure cannot be timely returned to the compressor. The excess lubricating oil remains in the separation structure and is carried away by the refrigerant again, resulting in poor heat exchange effect of the system.

[0003] The patent with the patent number US6511530B2 discloses a structure for exhaust oil separation and oil storage inside a compressor, such as Figure 1As shown in the figure, an exhaust cavity 13a, an oil-gas separation cavity 11, and a lubricating oil storage cavity 15 are provided between the back surface of the compressor stationary scroll plate 2 and the exhaust cover 4. The oil storage cavity 15 returns to the internal suction cavity of the compressor through the oil return passage 2a, realizing the circulation of the lubricating oil inside the compressor. However, there are the following problems: In order not to affect the oil separation efficiency of the separation cavity 11, the oil storage cavity 15 needs to be arranged in the gravity direction below the oil separation cavity and the highest liquid level in the oil storage cavity needs to be lower than the oil outlet 14 of the oil separation cavity. Otherwise, the lubricating oil enters the separation cavity and affects the oil separation effect. Therefore, the problem of the same problem as the technical patent number CN107575383A of such an oil storage cavity technology lies in the small oil storage volume, and the excess lubricating oil will still be carried into the refrigeration system by the refrigerant. Otherwise, in order to increase the volume of the oil storage cavity, it is necessary to increase the axial height of the oil storage cavity, which brings problems such as large compressor size, heavy weight, and high production cost. At the same time, the pressure in such an oil storage cavity is the exhaust high pressure. Affected by the exhaust fluctuation of the pump body, the exhaust pressure fluctuates greatly, resulting in difficulty in stabilizing the liquid level in the oil storage cavity, and it also fluctuates greatly with the exhaust.

[0004] The patent with the patent number CN107605726A discloses another oil return structure. As Figure 2 shown, the oil return passage 7 in the compressor exhaust cover 4 communicates with the stationary plate 3 and the bracket 1, and a throttling passage is arranged in the bracket 1, so that the lubricating oil in the oil return passage 7 is introduced into the lubricating cavity 11 in the bracket 1 to realize the lubrication of the bearings in the lubricating cavity. Although the lubricating oil is directly introduced into the key lubricating components inside the compressor, since the lubricating cavity 11 is a containing cavity and the cavity space is limited, most of the lubricating oil in the oil return passage 7 cannot flow back into the compressor in time, resulting in a large amount of lubricating oil entering the refrigeration system with the exhaust, affecting the heat exchange effect of the system.

[0005] At the same time, in the existing automotive scroll compressors, a medium-pressure cavity is often formed on the back surface of the moving plate, and the moving plate is pressed against the stationary plate by relying on the medium-pressure, realizing the axial seal of the pump body. And the compressor driving main shaft passes through the medium-pressure cavity. In order to realize the seal of the medium-pressure cavity, a shaft seal structure needs to be arranged on the crankshaft. Such a design increases the frictional power consumption at the shaft seal, and at the same time, the dynamic seal structure increases the sealing difficulty, and the performance and reliability of the compressor are easily affected. Such as in the patent CN107605726A Figure 11 such a back-pressure cavity design.

[0006] Due to the unreasonable setting of the oil return and oil storage structure in the existing scroll compressors, resulting in technical problems such as less oil storage in the actual oil storage structure, the present invention researches and designs an oil return structure, a compressor, and an air conditioner of a compressor. Summary of the Invention

[0007] Therefore, the technical problem to be solved by the present invention is to overcome the defect that the oil return and oil storage structure in the existing scroll compressor is unreasonably arranged, resulting in a small amount of oil stored in the actual oil storage structure, so as to provide an oil return structure for a compressor, a compressor and an air conditioner.

[0008] To solve the above problems, the present invention provides an oil return structure for a compressor, which includes:

[0009] A bracket, a moving disk, a stationary disk, a cover body, a crankshaft and a bearing I. The bracket has a lubrication cavity inside, the bearing I is arranged in the lubrication cavity, and one axial end of the crankshaft penetrates into the lubrication cavity and is supported by the bearing I; an oil storage cavity is also formed inside the bracket, and the oil storage cavity is located radially outside the lubrication cavity;

[0010] One side of the oil storage cavity facing the moving disk has an opening, and a sealing cover plate is arranged at the opening, and the sealing cover plate can move along the axial direction of the crankshaft.

[0011] In some embodiments, a pump body compression cavity is formed between the moving disk and the stationary disk, and an air inlet hole III is arranged on the sealing cover plate. The air inlet hole III can introduce the gas in the pump body compression cavity into the oil storage cavity to form gas pressure on one axial side of the sealing cover plate, so as to drive the sealing cover plate to move axially.

[0012] In some embodiments, a moving disk air guiding channel is formed on the moving disk. One end of the moving disk air guiding channel is communicated with the pump body compression cavity, and the other end can be communicated with the air inlet hole III; the air inlet hole III is axially arranged along the crankshaft and penetrates through the two axial end faces of the sealing cover plate.

[0013] In some embodiments, the moving disk air guiding channel includes an air inlet hole I, an air inlet channel I, an air inlet hole II and an air inlet channel II. The air inlet hole I is arranged on the axial end face of the moving disk facing the stationary disk and extends axially. The air inlet channel I is arranged inside the moving disk and extends in the radial direction. The air inlet hole I is communicated between the pump body compression cavity and the air inlet channel I. The air inlet hole II is arranged inside the moving disk and extends axially. The air inlet hole II is communicated between the air inlet channel I and the air inlet channel II. The air inlet channel II is arranged on the axial end face of the moving disk facing the sealing cover plate and extends in the radial direction. The air inlet channel II is communicated between the air inlet hole II and the air inlet hole III.

[0014] In some embodiments, the air inlet hole I is located radially inside the air inlet hole II, the radial length of the air inlet channel II is greater than the radial length of the air inlet hole II, the radial length of the air inlet channel II is greater than the radial length of the air inlet hole III, and the radial length of the air inlet channel I is greater than the radial length of the air inlet channel II.

[0015] In some embodiments, the radially inner periphery of the sealing cover plate is connected to the bracket, and a first sealing member mounting portion is provided on the radially inner periphery of the sealing cover plate, and a first sealing member is provided at the first sealing member mounting portion; the radially outer periphery of the sealing cover plate is connected to the bracket, and a second sealing member mounting portion is provided on the radially outer periphery of the sealing cover plate, and a second sealing member is provided at the second sealing member mounting portion.

[0016] In some embodiments, a first sealing portion mounting groove and a second sealing portion mounting groove are provided on an axial end face of the bracket opposite to the sealing cover plate. The first sealing portion mounting groove is disposed closer to the radially outer periphery of the sealing cover plate relative to the radially inner periphery of the sealing cover plate, and the second sealing portion mounting groove is disposed closer to the radially inner periphery of the sealing cover plate relative to the radially outer periphery of the sealing cover plate. A third sealing member is provided in the first sealing portion mounting groove, and a fourth sealing member is provided in the second sealing portion mounting groove.

[0017] In some embodiments, a first sealing portion pre-tightening structure is provided at the bottom of the first sealing portion mounting groove. The first sealing portion pre-tightening structure has an elastic force to always abut the third sealing member against the sealing cover plate. A second sealing portion pre-tightening structure is provided at the bottom of the second sealing portion mounting groove. The second sealing portion pre-tightening structure has an elastic force to always abut the fourth sealing member against the sealing cover plate.

[0018] In some embodiments, a dynamic disk self-rotation limiting pin and a sealing cover plate limiting pin are further included. A dynamic disk self-rotation limiting portion and a sealing cover plate self-rotation limiting portion are provided on the sealing cover plate. A self-rotation limiting portion mounting portion is further provided on the bracket. The dynamic disk self-rotation limiting pin cooperates with the dynamic disk self-rotation limiting portion to form a self-rotation limit for the dynamic disk. The sealing cover plate limiting pin cooperates with both the sealing cover plate self-rotation limiting portion and the self-rotation limiting portion mounting portion to form a self-rotation limit for the sealing cover plate.

[0019] In some embodiments, both the dynamic disk self-rotation limiting portion and the sealing cover plate self-rotation limiting portion are hole structures. One end of the dynamic disk self-rotation limiting pin is fixedly connected to the dynamic disk and the other end is inserted into the dynamic disk self-rotation limiting portion to form a self-rotation limit for the dynamic disk. The self-rotation limiting portion mounting portion is also a hole structure. The sealing cover plate limiting pin passes through the sealing cover plate self-rotation limiting portion and is inserted into the self-rotation limiting portion mounting portion to form a self-rotation limit for the sealing cover plate. The sealing cover plate limiting pin is fixedly connected to the sealing cover plate self-rotation limiting portion and has a clearance fit with the self-rotation limiting portion mounting portion.

[0020] In some embodiments, an oil distribution cavity is formed inside the cover body. The oil storage cavity can communicate with the oil distribution cavity to obtain oil. An oil outlet channel of the cover body, i.e., an oil outlet, is formed inside the cover body. An oil inlet channel of the static disc is formed inside the static disc. An oil inlet channel of the bracket is formed inside the bracket. One end of the oil outlet channel of the cover body communicates with the oil distribution cavity, and the other end communicates with one end of the oil inlet channel of the static disc. The other end of the oil inlet channel of the static disc communicates with one end of the oil inlet channel of the bracket. The other end of the oil inlet channel of the bracket communicates with the oil storage cavity, so that the oil outlet, the oil inlet channel of the static disc, and the oil inlet channel of the bracket are sequentially communicated, and oil can be guided from the oil distribution cavity to the oil storage cavity.

[0021] In some embodiments, the oil outlet extends along the axial direction of the crankshaft. The oil inlet channel of the static disc includes an oil inlet channel one and an oil inlet channel two. The oil inlet channel one extends along the axial direction of the static disc. The extending direction of the oil inlet channel two has a first inclination angle with the axial direction of the static disc. The first inclination angle is an angle between 0 and 90°, so that the extending direction of the oil inlet channel two is neither parallel nor perpendicular to that of the oil inlet channel one.

[0022] The oil inlet channel of the bracket includes an oil inlet channel three and an oil inlet channel four. The oil inlet channel three extends along the axial direction of the bracket. The extending direction of the oil inlet channel four has a second inclination angle with the axial direction of the bracket. The second inclination angle is an angle between 0 and 90°, so that the extending direction of the oil inlet channel three is neither parallel nor perpendicular to that of the oil inlet channel four. The oil outlet, the oil inlet channel two, the oil inlet channel one, the oil inlet channel three, and the oil inlet channel four are sequentially communicated, and the oil inlet channel four communicates with the oil storage cavity.

[0023] In some embodiments, a housing is further included. A cavity is formed inside the housing. The bracket, the static disc, and the moving disc are all arranged in the cavity of the housing. A pump body suction cavity is formed between the static disc, the moving disc, and the sealing cover plate. The pump body suction cavity communicates with the pump body compression cavity. The position where the bracket is located is a low-pressure suction cavity inside the housing. Refrigerant gas is sucked into the pump body suction cavity through the low-pressure suction cavity. When the refrigerant gas passes through the bracket, it can cool down the oil storage cavity inside the bracket.

[0024] In some embodiments, a first oil return channel is further formed on the bracket. One end of the first oil return channel can communicate with the oil storage cavity; the other end can communicate with at least one of the low-pressure suction cavity, the pump body suction cavity, and the lubrication cavity.

[0025] In some embodiments, the oil return structure of the compressor further includes a second bearing and an eccentric member. One end of the eccentric member is sleeved on the axial end of the crankshaft located in the lubrication cavity, and the other end can be used to drive the moving disk. The second bearing is supported between the eccentric member and the moving disk, and the second bearing communicates with the lubrication cavity.

[0026] In some embodiments, an oil return hole 1 is further formed in the sealing cover plate, and a moving disk oil return channel is formed in the moving disk. One end of the moving disk oil return channel can communicate with the oil return hole 1, and the other end communicates with the position of the second bearing to lubricate the second bearing.

[0027] In some embodiments, the oil return hole 1 is a hole axially formed in the sealing cover plate and penetrating through both axial end faces thereof. The moving disk oil return channel includes an oil return hole 2, an oil return hole 3, and an oil return hole 4. The oil return hole 2 is formed on the axial end face of the moving disk facing the sealing cover plate and extends radially. The oil return hole 3 is formed inside the moving disk and extends axially. The oil return hole 4 is formed inside the moving disk and extends in the radial direction. The oil return hole 2 communicates between the oil return hole 1 and the oil return hole 3, and the oil return hole 3 communicates between the oil return hole 2 and the oil return hole 4, so that the oil return hole 1, the oil return hole 2, the oil return hole 3, and the oil return hole 4 are sequentially communicated, and one end of the oil return hole 4 communicates with the position of the second bearing to lubricate the second bearing.

[0028] In some embodiments, the radial length of the oil return hole 2 is greater than the radial lengths of the oil return hole 1 and the oil return hole 3 respectively, and the radial length of the oil return hole 4 is greater than the radial length of the oil return hole 2.

[0029] In some embodiments, an oil return channel 2 and an oil return channel 3 are further arranged inside the bracket. The oil return channel 1, the oil return channel 2, and the oil return channel 3 are sequentially communicated, and one end of the oil return channel 3 also communicates with the lubrication cavity to lubricate the first bearing and the second bearing in the lubrication cavity.

[0030] In some embodiments, the extending direction of the oil return channel 1 forms a third inclined angle with the axis direction of the crankshaft, and the third inclined angle is between 0 and 90°. The extending direction of the oil return channel 2 is along the radial direction of the bracket, and the extending direction of the oil return channel 3 is along the axis direction of the crankshaft.

[0031] In some embodiments, a throttling component is further provided in the oil return hole four or the oil return passage two; the throttling component is of a cylindrical structure and includes a first section, a second section, and a third section that are sequentially connected along its axial direction. The outer diameter of the first section is greater than the outer diameter of the second section to form a first step at the connection between the two, so that the first section has the function of limiting and sealing. The outer diameter of the third section is greater than the outer diameter of the second section to form a second step at the connection between the two, so that a fluid flow channel can be formed on the outer peripheral surface of the second section. A spiral throttling flow groove one is provided on the outer peripheral wall of the third section, so that the fluid can be throttled through the throttling flow groove one.

[0032] In some embodiments, an oil-gas separation plate is further provided inside the oil storage cavity. The oil-gas separation plate divides the oil storage cavity into a gas storage cavity and a second oil storage cavity. The gas storage cavity is located between the oil-gas separation plate and the sealing cover plate. A communication diversion hole penetrating through the two axial end faces of the oil-gas separation plate is further provided on the oil-gas separation plate.

[0033] In some embodiments, the oil return structure of the compressor further includes a bearing three. The compressor includes a motor. The bearing three is arranged at an axial end of the crankshaft close to the motor relative to the bracket; a crankshaft communication hole one and a crankshaft communication hole two are provided inside the crankshaft. One end of the crankshaft communication hole one can communicate with the space where the bearing three is located, and the other end communicates with the crankshaft communication hole two. The other end of the crankshaft communication hole two communicates with the lubrication cavity. The crankshaft communication hole one extends along the axial direction of the crankshaft, and the extending direction of the crankshaft communication hole two has a fourth inclination angle with the axial direction of the crankshaft. The fourth inclination angle is between 0 and 90°, so that centrifugal inertia force can be generated when oil enters the crankshaft communication hole two.

[0034] The present invention further provides a compressor, which includes the oil return structure of the compressor described in any one of the preceding items.

[0035] The present invention further provides an air conditioner, which includes the compressor described above.

[0036] The oil return structure of a compressor, the compressor, and the air conditioner provided by the present invention have the following beneficial effects:

[0037] 1. The oil return structure of the compressor of the present invention effectively utilizes the internal space of the bracket by providing an oil storage cavity inside the bracket, and the oil storage cavity is a separate cavity different from the lubrication cavities where the first and second bearings are provided. The oil storage cavity can receive the oil separated from the exhaust cavity and / or the oil separation cavity and store it therein. Without increasing the axial and radial dimensions of the compressor, the oil storage cavity is effectively formed, and the accommodation space of the oil storage cavity is large, enabling a large amount of oil to be stored in the oil return structure. The cavity volume is large, and in particular, it is not necessary to additionally increase the size of other components, especially the upper cover size. Moreover, it effectively prevents the separated lubricating oil from being carried away by the refrigerant. While increasing the oil storage volume of the lubricating oil in the compressor, it does not increase the weight and size of the compressor. The present invention also enables the oil storage cavity to communicate with the pump body compression cavity through the air inlet hole three on the sealing cover plate. By introducing the intermediate pressure, the oil storage cavity can also act as a backpressure cavity, effectively driving the sealing cover plate to move in the axial direction, applying a backpressure to the moving disk, and preventing the situation of air leakage or the overturning of the moving disk caused by the insufficient tightness of the contact between the moving disk and the static disk. The oil storage cavity can realize the function of the backpressure cavity while storing oil, eliminating the need to additionally provide a backpressure cavity, further making the internal structure of the compressor more compact, reducing the space layout, and being more conducive to the miniaturization development of the scroll compressor.

[0038] 2. The present invention also enables the oil separated from the oil separation cavity to be throttled and depressurized first through a plurality of oil inlet channels and then enter the interior of the oil storage cavity, so that the pressure inside the oil storage cavity is the intermediate pressure between the suction pressure and the discharge pressure. As a result, the high-pressure lubricating oil separated from the exhaust can timely return to the oil storage cavity due to the pressure difference, preventing the liquid level in the oil storage cavity from being affected by the height of the oil separation cavity and reducing the oil storage capacity, thereby effectively increasing the oil storage capacity. The present invention also enables the medium-pressure oil inside the oil storage cavity to be throttled and depressurized through the setting of a plurality of oil return channels and then led to at least one of the lubrication cavity, the pump body suction cavity, and the low-pressure suction cavity, effectively ensuring the continuous and effective supply of oil in the lubrication cavity, the pump body suction cavity, and the low-pressure suction cavity. Moreover, due to the influence of moving components such as the crankshaft, eccentric components, and moving disk, the amount of lubricating oil stored inside the lubrication cavity of the present invention is unstable. Therefore, compared with the structure in the prior art where the medium-pressure cavity is used as the oil storage cavity, the oil storage cavity of the present invention is formed within the space inside the bracket, and its space does not change, preventing the situation of limited oil storage capacity and ensuring continuous oil supply. BRIEF DESCRIPTION OF THE DRAWINGS

[0039] Figure 1 Internal cross-sectional view of the scroll compressor of Background Art 1;

[0040] Figure 2 Internal cross-sectional view of the scroll compressor of Background Art 2;

[0041] Figure 3 Internal cross-sectional view of the scroll compressor of the present invention;

[0042] Figure 4 Detailed structural diagram of the oil storage chamber part of the present invention;

[0043] Figure 5 Schematic connection diagram of the intake passage of the present invention;

[0044] Figure 6 Three-dimensional structural diagram of the oil storage chamber (bracket part) of the present invention;

[0045] Figure 7 Top view of the sealing cover plate of the present invention;

[0046] Figure 8 Partial cross-sectional view of another embodiment of the oil return passage of the present invention;

[0047] Figure 9 Partial cross-sectional view of yet another embodiment of the oil return passage of the present invention;

[0048] Figure 10 Structural diagram of the throttling component of the present invention;

[0049] Figure 11 Partial cross-sectional view of another embodiment of the sealing cover plate of the present invention;

[0050] Figure 12 is Figure 11 left view of the sealing cover plate in

[0051] Figure 13 Partial cross-sectional view of yet another embodiment of the sealing cover plate of the present invention;

[0052] Figure 14 Partial cross-sectional view of an embodiment of the present invention with an oil-gas separation plate;

[0053] Figure 15 Cross-sectional view of the compressor with crankshaft communication holes one and two opened on the crankshaft of the present invention.

[0054] Reference numerals are shown as:

[0055] 1. Cover body; 101. Oil outlet; 102. Oil distribution chamber; 103. Air inlet; 2. Static disk; 201. First oil inlet passage; 202. Second oil inlet passage; 3. Moving disk; 301. First air inlet hole; 302. First air inlet passage; 303. Second air inlet hole; 304. Second air inlet passage; 305. Second oil return hole; 306. Third oil return hole; 307. Fourth oil return hole; 308. Third air inlet passage; 4. Bracket; 401. Third oil inlet passage; 402. Fourth oil inlet passage; 403. Installation part for self-rotation limit part; 404. First oil return passage; 405. Internal reinforcing rib; 406. Second oil return passage; 407. Third oil return passage; 408. First sealing part installation groove; 409. Second sealing part installation groove; 5. Housing; 6. Motor; 7. Crankshaft; 701. First crankshaft communication hole; 702. Second crankshaft communication hole; 8. Housing air suction port; 9. Low-pressure air suction chamber; 10. Oil storage chamber; 11. Lubrication chamber; 12. Pump body air suction chamber; 13. Pump body compression chamber; 14. Exhaust chamber; 16. Compressor exhaust port component; 17. Sealing cover plate; 171. Third air inlet hole; 172. First sealing part installation part; 173. Second sealing part installation part; 174. Moving disk self-rotation limit part; 175. Sealing cover plate self-rotation limit part; 176. First oil return hole; 18. Moving disk self-rotation limit pin; 19. Moving disk self-rotation limit support ring; 20. Sealing cover plate limit pin; 21. First bearing; 22. First sealing part; 23. Second sealing part; 22a. Third sealing part; 23a. Fourth sealing part; 221. First sealing part pre-tightening structure; 231. Second sealing part pre-tightening structure; 24. Throttle component; 241. First section; 242. Second section; 243. First throttle flow-through groove; 244. Third section; 25. Second bearing; 26. Eccentric component; 27. Oil-gas separation plate; 270. Air storage chamber; 271. Connecting and guiding hole; 272. Second oil storage chamber; 28. Third bearing. Detailed implementation manners

[0056] To make the objectives, technical solutions and advantages of the present invention clearer, the technical solutions of the present invention will be clearly and completely described below in conjunction with specific embodiments of the present invention and the corresponding drawings. Obviously, the described embodiments are only a part of the embodiments of the present invention, rather than all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those of ordinary skill in the art without making creative efforts shall fall within the protection scope of the present invention.

[0057] As Figure 1As shown in the figure, it is the compressor structure of the prior art, which mainly includes a compressor upper cover, a static disk, a moving disk, and a compressor drive support structure. An exhaust cavity, an oil separation cavity, and an oil storage cavity are formed between the compressor static disk and the upper cover. The oil storage cavity is relatively arranged below the oil separation cavity, and the highest oil storage level in the oil storage cavity corresponds to the bottom oil outlet hole of the oil separation cavity. The structural positions of the exhaust cavity, the oil separation cavity, and the oil storage cavity in the prior art are such that the upper cover needs to be set very large, resulting in a large size and heavy weight of the compressor. The axial oil separation length of the oil separation cavity is limited, resulting in a decrease in the actual oil separation efficiency. At the same time, the oil storage cavity is directly connected to the exhaust cavity through the oil separation cavity, without a throttling and pressure-reducing structure in the middle. The pressure in the oil storage cavity fluctuates with the exhaust pressure. Due to the large pressure fluctuation between the oil storage cavity and the oil separation cavity, it is difficult for the lubricating oil separated by the oil separation cavity to enter the oil storage cavity in time and then be taken away by the exhaust, affecting the oil storage and oil separation effects. And the oil storage cavity in the prior art is arranged in the exhaust high-temperature area, and the lubricating oil in the oil storage cavity is at the exhaust high temperature. The high-temperature oil directly enters the lubricating part after throttling, resulting in a decrease in the lubrication effect.

[0058] As Figure 2 In the prior art shown in the figure, the compressor has a housing, a bracket, a moving disk, a static disk, an upper cover, and a driving member. By arranging an oil return channel in the compressor upper cover, the static disk, and the bracket, the lubricating oil separated by the exhaust oil separation structure of the upper cover is returned to the cavity in the bracket. The two bearings in the lubricating cavity. Since this bracket cavity is a housing for moving parts, the cavity space is limited, and there are eccentric parts and moving disks of the moving parts, which affect the oil storage capacity of the cavity, resulting in the separated lubricating oil not being completely stored in the compressor. The excess lubricating oil will still be taken away by the exhaust and enter the system, affecting the system heat exchange. And because the lubricating oil at the exhaust high temperature directly enters the lubricating part after throttling, the lubrication effect is reduced. In addition, as shown in the figure, the cavity is a back pressure cavity arranged on the back of the moving disk to support the axial force of the moving disk. Since the driving crankshaft penetrates into this cavity through the cover, in order to achieve the sealing of the cavity, a sealing component (not shown) for sealing with the crankshaft needs to be set. This design will undoubtedly increase the frictional power consumption of the crankshaft. At the same time, because the crankshaft penetrates into the back pressure cavity, there is a pressure difference on both sides of the crankshaft, resulting in an additional axial pressure on the bearings arranged on the crankshaft, affecting the reliability of the bearings.

[0059] The present invention combines Figures 3 - 15 As shown in the figure, the present invention provides an oil return structure for a compressor, which includes:

[0060] A bracket 4, a moving disk 3, a static disk 2, a cover body 1, a crankshaft 7, and a first bearing 21. The bracket 4 has an internal lubricating cavity 11, the first bearing 21 is arranged in the lubricating cavity 11, and one axial end of the crankshaft 7 penetrates into the lubricating cavity 11 and is supported by the first bearing 21; an oil storage cavity 10 is also formed inside the bracket 4, and the oil storage cavity 10 is located radially outside the lubricating cavity 11;

[0061] One side of the oil storage cavity 10 facing the moving disk 3 has an opening, and a sealing cover plate 17 is arranged at the opening. The sealing cover plate 17 can move along the axial direction of the crankshaft 7.

[0062] For the oil return structure of the compressor of the present invention, by arranging an oil storage cavity inside the bracket, and the oil storage cavity is a separate cavity different from the lubricating cavities where the first and second bearings are arranged, the internal space of the bracket is effectively utilized, so that the oil storage cavity can receive the oil separated from the exhaust cavity and / or the oil separation cavity and store it in the oil storage cavity. Without increasing the axial and radial dimensions of the compressor, the oil storage cavity is effectively opened, and the accommodation space of the oil storage cavity is large, so that a large amount of oil can be stored in the oil storage structure. The cavity volume is large and there is no need to increase the size of other components, especially the upper cover size. In addition, it effectively prevents the separated lubricating oil from being carried away by the refrigerant. While increasing the oil storage volume of the lubricating oil in the compressor, it does not increase the weight and size of the compressor; the present invention also enables the oil storage cavity to act as a back pressure cavity through the arrangement of the sealing cover plate, effectively driving the sealing cover plate to move in the axial direction, applying a back pressure to the moving disk, and preventing the situation of air leakage or the overturning of the moving disk caused by the insufficient contact and sealing between the moving disk and the static disk. The oil storage cavity can realize the function of the back pressure cavity while realizing oil storage, without the need to additionally open a back pressure cavity, further making the internal structure of the compressor more compact, reducing the space layout, and being more conducive to the miniaturization development of the scroll compressor.

[0063] In some embodiments, a pump body compression cavity 13 is formed between the moving disk 3 and the static disk 2, and an air inlet hole three 171 is arranged on the sealing cover plate 17. The air inlet hole three 171 can introduce the gas in the pump body compression cavity 13 into the oil storage cavity 10 to form a gas pressure on one axial side of the sealing cover plate, so as to drive the sealing cover plate to move axially (that is, enabling the oil storage cavity 10 to have the function of a back pressure cavity to drive the movement of the sealing cover plate 17). The present invention also enables the oil storage cavity to communicate with the pump body compression cavity through the air inlet hole three on the sealing cover plate through the arrangement of the sealing cover plate. By introducing the intermediate pressure, the oil storage cavity can also act as a back pressure cavity, effectively driving the sealing cover plate to move in the axial direction, applying a back pressure to the moving disk, and preventing the situation of air leakage or the overturning of the moving disk caused by the insufficient contact and sealing between the moving disk and the static disk. The oil storage cavity can realize the function of the back pressure cavity while realizing oil storage, without the need to additionally open a back pressure cavity, further making the internal structure of the compressor more compact, reducing the space layout, and being more conducive to the miniaturization development of the scroll compressor.

[0064] The present invention solves the following technical problems

[0065] 1. Increasing the oil storage volume of the lubricating oil in the compressor without increasing the weight and size of the compressor;

[0066] 2. Design the back pressure chamber of the moving disk away from the crankshaft through cavity. The sealing of the back pressure chamber does not need to be designed with dynamic sealing for the rotating main shaft, reducing the power consumption of the main shaft.

[0067] 3. Set up an oil storage chamber in the low-temperature area inside the compressor to reduce the temperature of the lubricating oil. Cool the high-temperature oil separated from the exhaust and returned to the oil, and then introduce it into other lubricating parts inside the compressor to improve the lubrication effect of the lubricating oil.

[0068] 4. Increase the oil return path of the lubricating oil inside the compressor to accelerate the lubrication of the lubricating oil in the compressor.

[0069] Beneficial effects:

[0070] 1. Design the back pressure chamber on the back of the moving disk away from the crankshaft through space, effectively avoiding the setting of dynamic sealing on the crankshaft, reducing the frictional power consumption at this place, increasing the energy efficiency of the compressor and improving the sealing reliability.

[0071] 2. Reduce the oil temperature and improve the lubrication effect: In the present invention, an oil storage chamber is provided between the moving disk and the moving disk support part of the compressor, and the oil storage chamber is in the low-temperature area of the compressor suction. The oil storage chamber stores the high-temperature lubricating oil separated and returned from the exhaust, and by setting it close to the low-temperature area, the low-temperature refrigerant cools down the high-temperature lubricating oil in the oil storage chamber and then returns it to other lubricating parts inside the compressor. When the temperature of the lubricating oil decreases, it takes away more heat from the lubricating parts, which can greatly improve the lubrication effect of the lubricating oil.

[0072] Core invention point 1: The present invention "a scroll compressor oil return, oil storage and back pressure structure" is an oil storage and sealing structure. A gas and oil storage cavity is provided between the back of the moving disk and the bracket. This cavity is within the non-crankshaft through space. A sealing cover plate that can move freely axially is provided on the side of the cavity close to the moving disk. The cover plate supports the rotation and axial movement of the moving disk. The above cavity has an oil inlet channel, an air inlet channel and an oil return channel.

[0073] Core invention point 2: The above oil storage and sealing structure: Its position is set in the area between the compression unit and the drive unit of the compressor, and at least has an opening part facing the compression unit, and the gas pressure in this cavity is the intermediate pressure between the suction and the exhaust, and this intermediate pressure forms a corresponding relationship through connecting the compression cavity of the compression unit.

[0074] Core invention point 3: The sealing cover plate of the above oil storage structure is set at the opening of the oil storage cavity, between the moving disk and the oil storage cavity, and realizes the sealing inside and outside the cover plate with the main body structure of the oil storage cavity. The sealing cover plate has a limiting structure for supporting the moving disk and restricting the self-rotation of the moving disk, is provided with a connecting channel connecting the inside of the oil storage cavity and the compression cavity, and has a limiting structure for restricting the relative axial rotation of the sealing cover plate with respect to the main body of the oil storage cavity. The sealing cover plate is set to be able to move freely axially (in the direction of the drive shaft).

[0075] Core inventive point 4: The above-mentioned oil storage cavity body structure has a bearing accommodation cavity and an oil storage cavity respectively in the radial direction. The two cavities are sealed by the above-mentioned sealing cover plate. The body structure has a sealing cooperation part with the sealing cover plate, an axial and circumferential limiting part of the sealing cover plate, an oil inlet passage connecting the inside of the oil storage cavity and the exhaust and oil return cavity, and an oil return passage connecting the inside of the oil storage cavity and the low-pressure area outside the oil storage cavity.

[0076] Figure 3 This is Embodiment 1 of the scroll compressor according to the present invention, which includes a cover body 1; a stationary disk 2; a moving disk 3; a bracket 4; a housing 5; a motor 6; a crankshaft 7; a housing suction port 8; a low-pressure suction cavity 9; an oil storage cavity 10; a lubrication cavity 11; a pump body suction cavity 12; a pump body compression cavity 13; an exhaust cavity 14; an oil separation cavity 102; and a compressor exhaust port component 16. The compressor drive and compression unit is arranged between the cover body 1 and the housing 5. The compression unit is composed of the stationary disk 2 and the moving disk 3, and the drive unit is composed of the motor 6, the crankshaft 7, etc. The compression unit is driven by the drive unit to compress and discharge the refrigerant. At the same time, the compressor also has a pump body support unit, an oil-gas separation unit, and an oil storage cavity unit. The pump body support unit includes the bracket 4 and the housing 5, etc., or the bracket 4 and the housing 5 are of an integral structure, and the present invention is illustrated by the shown structure. The oil-gas separation unit includes the cover body 1, the oil separation cavity 102, etc. (Note that the oil separation structure shown in the figure can be arranged in the oil separation cavity, or other structures with an oil separation effect can be used). The oil storage cavity 10 includes cavities formed between various components inside the compressor, etc., and is arranged between the drive unit and the compression unit. A moving disk support and limiting unit is also arranged on the oil storage cavity, which has the function of supporting the axial movement of the moving disk relative to the oil storage unit. In addition, there is also / or an oil return unit, and the oil return unit connects the oil storage unit and the lubrication part inside the compressor.

[0077] Combined with Figure 3 and Figure 4 Describe Inventive Point 1 of the Present Invention: A compressor includes at least a housing 5 and a cover body 1 to form a closed cavity. A drive unit (motor 6), an oil storage unit (including a bracket 4 and an oil storage cavity 10), a compression unit (stationary disk 2, moving disk 3), and a support unit (sealing cover plate 17) are arranged in the closed cavity. The support unit is arranged between the oil storage unit and the compression unit and can move freely axially to achieve the sealing of the oil storage unit and the axial sealing of the compression unit. In the present invention, the sealing of the oil storage cavity is achieved through the axially floating support unit, and at the same time, under the action of the gas (intermediate pressure) in the oil storage unit, the moving disk is pressed against the stationary disk to achieve the floating sealing of the moving disk. In the prior art, an intermediate pressure gas unit for supporting the moving disk to be tightly attached is arranged in the illustrated lubrication cavity 11. To achieve the sealing of this unit, a dynamic seal needs to be arranged at the joint with the crankshaft in the lubrication cavity 11, which increases the rotational friction power consumption of the crankshaft.

[0078] In some embodiments, an air guiding channel is formed on the moving disk 3. One end of the air guiding channel on the moving disk communicates with the compression chamber 13 of the pump body, and the other end can communicate with the third air inlet hole 171. The third air inlet hole 171 is axially formed along the crankshaft 7 and penetrates through the two axial end faces of the sealing cover plate 17. This is the preferred structural manner for forming the back pressure channel in the present invention. That is, through the air guiding channel on the moving disk, the gas in the compression chamber of the pump body can be guided to the third air inlet hole and enter the oil storage chamber to provide back pressure to the oil storage chamber, forming a back pressure chamber. At the same time, the sealing cover plate can move axially to generate a back pressure effect on the moving disk through the back pressure, ensuring effective sealing between the moving and static disks and normal compression.

[0079] Invention point 2: The above-mentioned oil storage unit includes an oil storage chamber 10 and a bracket 4 (as Figure 4 and Figure 6 ) The bracket 4 is provided with a support bearing mounting portion (bearing one, two) for supporting the driving unit and the compression unit, and the oil storage chamber 10 is separated from the bearing mounting portion. The oil storage unit at least includes an oil storage chamber 10, an oil inlet channel, an air inlet channel, and also includes an oil return channel. A mating sealing portion and a circumferential limiting portion are also provided on the body structure and cooperate with the above-mentioned support unit. Explanation: The support unit, that is, the sealing cover plate 17, is arranged in the body part, that is, the illustrated bracket 4. A sealing member is arranged between the sealing cover plate and the bracket to achieve the sealing between the oil storage chamber 10 and other low-pressure chambers (pump body suction chamber, low-pressure suction chamber, lubrication chamber 11). At the same time, the moving disk is arranged on the sealing cover plate. During the operation of the moving disk, the bottom of the moving disk (the side exceeding the sealing cover plate) always remains in contact with the sealing cover plate. The sealing cover plate is affected by the gas in the oil storage chamber on the side facing the oil storage chamber, and is affected by the gas force in the compression chamber of the moving disk on the side facing the moving disk. By controlling the gas pressure in the oil storage chamber, the axial resultant force (in the direction of the driving shaft axis) on the sealing cover plate always remains towards the side of the moving disk, that is, always presses the moving disk towards the static disk side, realizing the axial sealing between the moving and static disks of the pump body.

[0080] In some embodiments, the moving disk air guiding channel includes a first air inlet hole 301, a first air inlet channel 302, a second air inlet hole 303, and a second air inlet channel 304. The first air inlet hole 301 is opened on the axial end face of the moving disk 3 facing the static disk 2 and extends axially. The first air inlet channel 302 is opened inside the moving disk 3 and extends in the radial direction. The first air inlet hole 301 communicates between the pump body compression chamber 13 and the first air inlet channel 302. The second air inlet hole 303 is opened inside the moving disk 3 and extends axially. The second air inlet hole 303 communicates between the first air inlet channel 302 and the second air inlet channel 304. The second air inlet channel 304 is opened on the axial end face of the moving disk 3 facing the sealing cover plate 17 and extends in the radial direction. The second air inlet channel 304 communicates between the second air inlet hole 303 and the third air inlet hole 171. This is the preferred structural form of the moving disk air guiding channel of the present invention. The gas can be transported through the first air inlet hole, the first air inlet channel, the second air inlet hole, and the second air inlet channel. The first air inlet channel is for transporting the gas to the radial outer side to facilitate entering the oil storage chamber. The second air inlet channel is for ensuring that it is always communicated with the third air inlet hole on the sealing cover plate during the movement of the moving disk, so as to realize the function of continuously providing back pressure.

[0081] Invention point 4: The air inlet channel as described above is characterized by the channel structure provided on the support body (sealing cover plate 17) and the moving disk substrate. As Figure 4 shown, the air inlet channel on the moving disk includes a first air inlet hole 301 that connects the compression chamber and starts on the moving disk substrate, a first air inlet channel 302 extending from the outer periphery of the moving disk substrate, a second air inlet hole 303 opened from the support body side and communicating with the first air inlet channel, and a second air inlet channel 304 connected and matched with the support body. The second air inlet channel and the third air inlet hole 171 on the support body form a connection from the compression chamber to the oil storage chamber, and in order to make the pressures in the compression chamber and the oil storage chamber closer, the second air inlet hole and the third air inlet hole are always kept in communication. As Figure 5The figure shows a schematic diagram of always maintaining connectivity. At a certain moment, the position of the second intake passage 304. Since the second intake passage 304 starts on the moving disk, this intake hole rotates periodically with the moving disk. Relative to the third intake hole 171, its rotation trajectory is a circular motion as shown by the dotted line in the figure. The figure shows the optimal implementation features of the present invention. By setting the sizes of the third intake hole and the second intake hole, specifically, the diameter of the second intake hole is at least larger than the third intake hole + the crankshaft eccentricity distance. Explanation: As described above, the pressure in the oil storage chamber of the present invention is related to the angle at which the first intake hole 301 is located in the compression chamber (that is, the aperture of the first intake hole 301 is set to be smaller than the wall thickness of the scroll profile. That is, the connection relationship between the first intake hole and the compression chamber is connected at some compression moments and disconnected at some compression moments. The pressure in the oil storage chamber is realized according to the connected angle range. In addition, in order to obtain the same pressure in the oil storage chamber, it can also be set like this: Use the connection and disconnection relationship between the second intake passage and the third intake hole to determine the pressure in the oil storage chamber, and the connection range between the first intake hole and the compression chamber can be set to be at least larger than the connection range between the second intake hole and the third intake hole.)

[0082] As Figure 4 , in some embodiments, the first intake hole 301 is located radially inside the second intake hole 303, the radial length of the second intake passage 304 is greater than the radial length of the second intake hole 303, the radial length of the second intake passage 304 is greater than the radial length of the third intake hole 171, and the radial length of the first intake passage 302 is greater than the radial length of the second intake passage 304. The first intake passage adopts a structure with a longer radial length. On the one hand, it is to guide the backpressure gas from the radial inside to the radial outside. On the other hand, it can store a certain amount of gas and also play a role in throttling and reducing pressure. The second intake passage has a certain length in the radial direction. On the one hand, it ensures that it is always connected to the third intake hole and continuously provides backpressure gas. On the other hand, it can also play a role in throttling and reducing pressure.

[0083] As Figure 13, in some embodiments, the radially inner circumference of the sealing cover plate 17 is connected to the bracket 4, and a first sealing member mounting portion 172 is provided at the radially inner circumference of the sealing cover plate 17, and a first sealing member 22 is provided at the first sealing member mounting portion 172; the radially outer circumference of the sealing cover plate 17 is connected to the bracket 4, and a second sealing member mounting portion 173 is provided at the radially outer circumference of the sealing cover plate 17, and a second sealing member 23 is provided at the second sealing member mounting portion 173. In the present invention, by providing the first sealing member mounting portion at the radially inner circumference of the sealing cover plate and providing the first sealing member there, the sealing effect between the radially outer circumference of the sealing cover plate and the bracket can still be ensured during the axial movement of the sealing cover plate. By providing the second sealing member mounting portion at the radially inner circumference of the sealing cover plate and providing the second sealing member there, the sealing effect between the radially inner circumference of the sealing cover plate and the bracket can still be ensured during the axial movement of the sealing cover plate.

[0084] The first sealing member mounting portion 172 is preferably in the structure of an annular groove, and the first sealing member is preferably in the structure of an annular strip; the second sealing member mounting portion 173 is preferably in the structure of an annular groove, and the second sealing member is preferably in the structure of an annular strip.

[0085] Invention Point 3 (in combination with Figure 4 and Figure 7 description): The above-mentioned support unit is characterized in that: the support unit at least includes a support body (sealing cover plate 17), a sealing member and an air inlet channel. The support body is in the shape of a flat plate that is hermetically designed with the sealing mating portion on the bracket 4. The sealing member is arranged at any position on the support body or the bracket 4. Figure 4 is a structure mounted on the support body. Thus, mounting portions are respectively designed on the axial mating surfaces of the support body, and the sealing member is arranged therein. (In addition, the mounting portion can also be arranged on the axial mating surface or the radial mating surface of the bracket body. For example Figure 13 is another embodiment of the sealing component: the sealing component is mounted on the radial mating surface of the bracket 4, and sealing member mounting grooves are respectively opened on the inner and outer circles of the radial mating surface, and the sealing component is arranged therein. In addition, a pre-tightening component with elasticity in the axial direction is provided, so that the sealing member is always in contact with the sealing cover plate 17 when the sealing cover plate 17 moves axially.) The self-rotation limiting portion of the moving disk and the limiting portion for preventing the support unit from rotating circumferentially relative to the bracket 4. For example Figure 4 shows a limiting structure, which respectively has a cylindrical pin arranged on the support body and a pin hole structure cooperating with the cylindrical pin. The cylindrical pin is press-fitted or integrally arranged on the sealing cover plate 17, and has a clearance fit with the pin hole. The cylindrical pin can move axially freely in the pin hole. For example Figure 11 and 12 , is another embodiment of the limiting mounting portion. The limiting portion is a rectangular boss structure integrally provided with the sealing cover plate 17, and a rectangular groove structure is provided on the bracket 4 to achieve axial limiting.

[0086] In some embodiments, a first sealing portion mounting groove 408 and a second sealing portion mounting groove 409 are provided on an axial end surface of the bracket 4 opposite to the sealing cover plate 17. The first sealing portion mounting groove 408 is arranged close to the outer circumference in the radial direction of the sealing cover plate 17 relative to the inner circumference in the radial direction of the sealing cover plate 17, and the second sealing portion mounting groove 409 is arranged close to the inner circumference in the radial direction of the sealing cover plate 17 relative to the outer circumference in the radial direction of the sealing cover plate 17. A third sealing member 22a is arranged in the first sealing portion mounting groove 408, and a fourth sealing member 23a is arranged in the second sealing portion mounting groove 409. This is the second sealing structure form of the present invention, that is, a sealing structure is formed at the axial end surface of the sealing cover plate facing the bracket. The first sealing portion mounting groove and the second sealing portion mounting groove are provided on the axial end surface of the bracket, and the third sealing member and the fourth sealing member are respectively arranged therein, which can play an axial sealing role in the part of the inner circumference in the radial direction and the position of the outer circumference in the radial direction of the sealing cover plate.

[0087] In some embodiments, a first sealing portion pre-tightening structure 221 is provided at the bottom of the first sealing portion mounting groove 408. The first sealing portion pre-tightening structure 221 has an elastic force to always abut the third sealing member 22a against the sealing cover plate 17. A second sealing portion pre-tightening structure 231 is provided at the bottom of the second sealing portion mounting groove 409. The second sealing portion pre-tightening structure 231 has an elastic force to always abut the fourth sealing member 23a against the sealing cover plate 17. The present invention can also apply elastic forces to the third and fourth sealing members respectively through the first and second sealing portion pre-tightening structures, ensuring that the third and fourth sealing members always abut against the sealing cover plate, and further improving the sealing effect.

[0088] In some embodiments, it further includes a dynamic disk self-rotation limiting pin 18 and a sealing cover plate limiting pin 20. A dynamic disk self-rotation limiting portion 174 and a sealing cover plate self-rotation limiting portion 175 are provided on the sealing cover plate 17. A self-rotation limiting portion mounting portion 403 is further provided on the bracket 4. The dynamic disk self-rotation limiting pin 18 cooperates with the dynamic disk self-rotation limiting portion 174 to form a self-rotation limit for the dynamic disk 3, and the sealing cover plate limiting pin 20 cooperates with both the sealing cover plate self-rotation limiting portion 175 and the self-rotation limiting portion mounting portion 403 to form a self-rotation limit for the sealing cover plate 17. This is the preferred anti-self-rotation structure form of the present invention. The cooperation between the dynamic disk self-rotation limiting pin and the dynamic disk self-rotation limiting portion on the sealing cover plate can effectively prevent the dynamic disk from rotating relative to the sealing cover plate. The cooperation between the sealing cover plate limiting pin, the sealing cover plate self-rotation limiting portion, and the self-rotation limiting portion mounting portion on the bracket can effectively prevent the sealing cover plate from rotating relative to the bracket, ultimately preventing the occurrence of the situation where the dynamic disk rotates.

[0089] In some embodiments, both the moving disk self-rotation limiting portion 174 and the sealing cover self-rotation limiting portion 175 are hole structures. One end of the moving disk self-rotation limiting pin 18 is fixedly connected to the moving disk 3, and the other end is inserted into the moving disk self-rotation limiting portion 174 to form a self-rotation limit for the moving disk 3. The self-rotation limiting portion mounting portion 403 is also a hole structure. The sealing cover limiting pin 20 passes through the sealing cover self-rotation limiting portion 175 and is inserted into the self-rotation limiting portion mounting portion 403 to form a self-rotation limit for the sealing cover 17. The sealing cover limiting pin 20 is fixedly connected to the sealing cover self-rotation limiting portion 175 and has a clearance fit with the self-rotation limiting portion mounting portion 403. This is the preferred structural form of the moving disk self-rotation limiting portion 174 and the sealing cover self-rotation limiting portion of the present invention, that is, the moving disk self-rotation limiting pin preferably has an interference fit with the moving disk and the sealing cover respectively, the sealing cover limiting pin has an interference fit with the sealing cover, and has a clearance fit with the self-rotation limiting mounting portion on the bracket, so that the sealing cover limiting pin can axially slide relative to the bracket, effectively restricting the self-rotation of the sealing cover.

[0090] In some embodiments, an oil distribution cavity 102 is formed in the cover body 1. The oil storage cavity 10 can communicate with the oil distribution cavity 102 to obtain oil. An oil outlet channel of the cover body is formed inside the cover body 1, that is, the oil outlet 101. An oil inlet channel of the static disk is formed inside the static disk 2, and an oil inlet channel of the bracket is formed inside the bracket 4. One end of the oil outlet channel of the cover body communicates with the oil distribution cavity 102, and the other end communicates with one end of the oil inlet channel of the static disk. The other end of the oil inlet channel of the static disk communicates with one end of the oil inlet channel of the bracket. The other end of the oil inlet channel of the bracket communicates with the oil storage cavity 10, so that the oil outlet 101, the oil inlet channel of the static disk, and the oil inlet channel of the bracket are sequentially communicated, so as to guide the oil from the oil distribution cavity 102 to the oil storage cavity 10. Through the oil outlet on the cover body, the oil inlet channel of the static disk, and the oil inlet channel of the bracket, the present invention can sequentially communicate to introduce the oil in the oil distribution cavity into the oil storage cavity, completing the oil supply function for the oil storage cavity.

[0091] Invention point 5: As Figure 4 , as described above, the oil inlet channel specifically includes: an oil inlet channel provided on the static disk 2, one end communicating with the oil inlet channel inlet on the bracket 4, and the other end connecting to the oil outlet 101 on the upper cover oil distribution cavity 102. Oil inlet channels three and four are provided on the bracket 4, respectively communicating with the oil storage cavity and the oil inlet channel of the static disk, realizing the connection between the upper cover oil distribution cavity 102 and the oil storage cavity 10. After the lubricating oil carried by the exhaust refrigerant is separated in the upper cover oil distribution cavity, it can smoothly pass through the oil outlet 101 and finally enter the oil storage cavity through the above-mentioned oil inlet channel. In addition, part of the refrigerant also enters the oil storage cavity along with the above-mentioned oil inlet channel. Therefore, the size of the oil inlet channel is generally set between 0.5 and 5 mm. Utilizing the capillary throttling effect, the exhaust high pressure is throttled and reduced to the medium pressure in the oil storage cavity.

[0092] In some embodiments, the oil outlet 101 extends along the axial direction of the crankshaft 7. The static disk oil inlet passage includes a first oil inlet passage 201 and a second oil inlet passage 202. The first oil inlet passage 201 extends along the axial direction of the static disk 2. The extending direction of the second oil inlet passage 202 has a first inclined angle with the axial direction of the static disk 2. The first inclined angle is an angle between 0 and 90°, such that the extending direction of the second oil inlet passage 202 is neither parallel nor perpendicular to the extending direction of the first oil inlet passage 201.

[0093] The bracket oil inlet passage includes a third oil inlet passage 401 and a fourth oil inlet passage 402. The third oil inlet passage 401 extends along the axial direction of the bracket 4. The extending direction of the fourth oil inlet passage 402 has a second inclined angle with the axial direction of the bracket 4. The second inclined angle is an angle between 0 and 90°, such that the extending direction of the third oil inlet passage 401 is neither parallel nor perpendicular to the extending direction of the fourth oil inlet passage 402. The oil outlet 101, the second oil inlet passage 202, the first oil inlet passage 201, the third oil inlet passage 401, and the fourth oil inlet passage 402 are connected in sequence. The fourth oil inlet passage 402 is connected to the oil storage cavity 10.

[0094] This is a preferred structural form of the oil outlet, the static disk oil inlet passage, and the bracket oil inlet passage of the present invention, that is, the static disk oil inlet passage includes a first oil inlet passage extending axially and a second oil inlet passage inclined to the axis, effectively realizing the conduction of the oil in the oil distribution cavity relatively located on the radial inner side to the oil inlet passage relatively located on the radial outer side. The bracket oil inlet passage includes a third oil inlet passage extending axially and an inclined fourth oil inlet passage, completing the conduction of the oil located on the radial outer side to the oil storage cavity relatively located on the radial inner side.

[0095] In some embodiments, a housing 5 is further included. The interior of the housing 5 has a cavity. The bracket 4, the static disk 2, and the moving disk 3 are all disposed in the cavity of the housing 5. A pump body suction cavity 12 is formed between the static disk 2, the moving disk 3, and the sealing cover plate 17. The pump body suction cavity 12 is communicated with the pump body compression cavity 13. The position where the bracket 4 is located is the low-pressure suction cavity 9 inside the housing 5. The refrigerant gas is sucked into the pump body suction cavity 12 through the low-pressure suction cavity 9. When the refrigerant gas passes through the bracket 4, it can cool the oil storage cavity 10 inside the bracket 4. By arranging the oil storage cavity inside the bracket and at a position not communicated with the lubrication cavity, and the bracket is located at the position of the low-pressure suction cavity, the present invention can effectively cool the oil storage cavity inside the bracket through the refrigerant of the low-pressure suction, improving the lubrication effect of the lubricating oil.

[0096] In some embodiments, an oil return passage one 404 is further formed on the bracket 4. One end of the oil return passage one 404 can communicate with the oil storage cavity 10, and the other end can communicate with at least one of the low-pressure suction cavity 9, the pump body suction cavity 12, and the lubrication cavity 11. By providing the oil return passage one on the bracket, the present invention can further effectively divert the oil in the oil storage cavity to at least one of the low-pressure suction cavity 9, the pump body suction cavity 12, and the lubrication cavity 11, so as to complete the cooling of structures such as the motor in the low-pressure suction cavity and the lubrication of bearing three, complete the lubrication of the friction between the static disc and the moving disc inside the pump body, and achieve the effective lubrication of bearing one and bearing two in the lubrication cavity.

[0097] In some embodiments, the oil return structure of the compressor further includes bearing two 25 and an eccentric member 26 (preferably an eccentric sleeve). One end of the eccentric member 26 is sleeved on the axial end of the crankshaft 7 located in the lubrication cavity 11, and the other end can be used to drive the moving disc 3. The bearing two 25 is supported between the eccentric member 26 and the moving disc 3, and the bearing two 25 communicates with the lubrication cavity 11. By providing the bearing two and the eccentric member, the present invention can drive the moving disc to perform eccentric translational motion through the eccentric member. The bearing two is used to support the eccentric member and the moving disc, and the bearing two communicates with the lubrication cavity to be able to suck lubricating oil from the lubrication cavity, thereby improving its lubrication performance.

[0098] Such as Figure 8 , in some embodiments, an oil return hole one 176 is further formed on the sealing cover plate 17, and a moving disc oil return passage is formed on the moving disc. One end of the moving disc oil return passage can communicate with the oil return hole one 176, and the other end communicates with the position of the bearing two 25 to lubricate the bearing two 25. The present invention can also introduce lubricating oil to the position of the bearing two through the oil return hole one on the sealing cover plate and the moving disc oil return passage on the moving disc, so as to provide and improve the lubrication effect on the bearing two.

[0099] In some embodiments, the first oil return hole 176 is a hole axially opened through both axial end faces of the sealing cover plate 17. The moving disk oil return passage includes a second oil return hole 305, a third oil return hole 306, and a fourth oil return hole 307. The second oil return hole 305 is axially opened on the axial end face of the moving disk 3 facing the sealing cover plate 17 and extends radially. The third oil return hole 306 is opened inside the moving disk 3 and extends axially. The fourth oil return hole 307 is opened inside the moving disk 3 and extends in the radial direction. The second oil return hole 305 communicates between the first oil return hole 176 and the third oil return hole 306. The third oil return hole 306 communicates between the second oil return hole 305 and the fourth oil return hole 307, such that the first oil return hole 176, the second oil return hole 305, the third oil return hole 306, and the fourth oil return hole 307 are sequentially communicated. One end of the fourth oil return hole 307 communicates to the position of the second bearing 25 to lubricate the second bearing 25. As Figure 8 , this is the preferred structural form of the moving disk oil return passage of the present invention, that is, the sequentially arranged second, third, and fourth oil return holes can throttle and reduce the pressure of the oil.

[0100] In some embodiments, the radial length of the second oil return hole 305 is respectively greater than the radial lengths of the first oil return hole 176 and the third oil return hole 306, and the radial length of the fourth oil return hole 307 is greater than the radial length of the second oil return hole 305. The relatively long radial length of the second oil return hole can effectively ensure that the moving disk is always communicated with the first oil return hole during rotation to suck lubricating oil. The relatively long radial length of the fourth oil return hole can provide an effective throttling effect, ensure that the oil entering the second bearing is throttled and pressure-reduced, ensure the pressure difference between the lubricating cavity and the oil storage cavity, and effectively ensure the continuous supply of oil to the lubricating cavity.

[0101] Invention point 6: In order to increase the utilization rate of the lubricating oil in the oil storage cavity, the oil storage cavity may further be provided with a first oil return passage 404. The oil return passage generally starts on the bracket 4, as Figure 4 shown. One end of the oil return passage is connected to the oil storage cavity 10, and the other end is connected to the internal suction area of the compressor. Figure 4 The structure shown is connected to the suction cavity on the motor side of the compressor. The oil return passage may be a slender hole with a small diameter, or a throttling component may be provided in the passage, as long as it has a throttling and pressure-reducing effect, to achieve the pressure drop of the medium-pressure gas in the oil storage cavity entering the low-pressure area. Explanation: With such a setting, the stored oil can enter the low-pressure suction cavity through the oil storage cavity, and then the suction oil-carrying effect of the pump body is utilized to realize the lubrication of the pump body by the lubricating oil.

[0102] In addition, the above oil return passage may also be set such that one end communicates with the oil storage cavity and the other end communicates with the installation chamber of the second bearing 25 on the moving disk, as Figure 8As shown, the oil return passage specifically includes an oil return hole 176 provided on the sealing cover plate 17, an oil return hole 305, an oil return hole 306 opened on the moving disk substrate and communicated with the first oil return hole, and an oil return hole 307 that is radially communicated from the outside to the inside of the outer periphery of the driven disk substrate. The lubricating oil enters the installation chamber of the second bearing 25 through the above oil return passage to lubricate the second bearing 25. In addition, in order to prevent the compressed gas in the oil storage chamber from entering the lubricating chamber 11, a throttling structure is provided on the above passage. As shown in the figure, a throttling component is provided on the fourth oil return hole as Figure 10 shown. The throttling component forms a throttling passage by providing a fine passage on its outer periphery or relying on the fine gap between the outer periphery (the second section 242) of the throttling component and the mating surface during assembly. In order to obtain the best lubrication effect, the first oil return hole 176 is always kept in communication with the second oil return hole 305. The illustration of the always-on communication can be referred to Figure 5 shown in the principle design.

[0103] In addition, the above oil return passage can also be entirely provided on the bracket 4 to achieve the communication between the oil storage chamber and the lubricating chamber, as Figure 9 shown. The specific features include an oil return passage 404, an oil return passage 406, an oil return passage 407 provided inside the bracket 4, and a throttling component 24 installed in any of the above passages.

[0104] As Figure 9 shown, in some embodiments, an oil return passage 406 and an oil return passage 407 are further provided inside the bracket 4. The oil return passage 404, the oil return passage 406, and the oil return passage 407 are communicated in sequence. One end of the oil return passage 407 is also communicated with the lubricating chamber 11 to lubricate the first bearing 21 and the second bearing 25 in the lubricating chamber 11. This is another embodiment of the present invention for supplying oil to the lubricating chamber, that is, the third and fourth oil return passages opened on the bracket can be communicated with the first oil return passage to provide oil transportation while throttling and reducing the pressure, ensuring the pressure difference between the lubricating chamber and the oil storage chamber, and effectively ensuring the continuous oil supply to the lubricating chamber.

[0105] In some embodiments, the extending direction of the oil return passage 404 forms a third inclined angle with the axis direction of the crankshaft 7, and the third inclined angle is between 0 and 90°. The extending direction of the oil return passage 406 is along the radial direction of the bracket 4, and the extending direction of the oil return passage 407 is along the axis direction of the crankshaft 7. This is the preferred opening method of the first, second, and third oil return passages of the present invention, that is, this setting form can improve the effect of throttling and reducing the pressure of the oil.

[0106] As Figure 10, in some embodiments, a throttling component 24 is further provided in the fourth oil return hole 307 or the second oil return passage 406; the throttling component 24 is of a cylindrical structure and includes a first section 241, a second section 242 and a third section 244 that are sequentially connected along its axial direction. The outer diameter of the first section 241 is greater than the outer diameter of the second section 242 to form a first step at the junction of the two, so that the first section 241 has the function of limiting and sealing. The outer diameter of the third section 244 is greater than the outer diameter of the second section 242 to form a second step at the junction of the two, so that a fluid flow passage can be formed on the outer peripheral surface of the second section 242. A spiral throttling flow groove 243 is provided on the outer peripheral wall of the third section 244, so that the fluid can be throttled through the throttling flow groove 243. By providing a throttling component in the fourth oil return hole or the second oil return passage, the present invention can further improve the effect of throttling and reducing the pressure of the oil; and the throttling component of the present invention includes three sections. The first section is used to effectively achieve the sealing function. The part with a slightly smaller outer diameter of the second section can be used to effectively conduct the oil. The spiral groove of the third section can effectively play the role of throttling and reducing the pressure, thereby improving the throttling effect on the oil.

[0107] As Figure 14 , in some embodiments, an oil-gas separation plate 27 is further provided inside the oil storage chamber 10. The oil-gas separation plate 27 divides the oil storage chamber 10 into a gas storage chamber 270 and a second oil storage chamber 272. The gas storage chamber 270 is located between the oil-gas separation plate 27 and the sealing cover plate 17. A communication and diversion hole 271 penetrating through the two axial end faces of the oil-gas separation plate 27 is further provided on the oil-gas separation plate 27. This is a further preferred structural form of the present invention. By providing an oil-gas separation plate inside the oil storage chamber, a unique gas storage chamber structure can be separated from the inside of the oil storage chamber, and the effect of a back pressure chamber can be formed through this gas storage chamber to provide back pressure for the moving disc and drive the sealing cover plate to move; while the other second oil storage chamber is used for storing oil. The communication and diversion holes provided on the oil-gas separation plate can achieve the function of air pressure buffering, ensure the effective pressure relief and conduction of the gas storage chamber, and ensure continuous and reliable operation.

[0108] Inventive Point 7: A compressor includes at least a housing 5 and a cover 1 to form a closed cavity. A drive unit, an oil storage unit, a gas storage unit (gas storage chamber), a support unit (sealing cover plate 17), and a compression unit are arranged in the closed cavity. The support unit is arranged between the gas storage unit and the compression unit and can move freely axially. The gas storage unit is arranged between the oil storage unit and the support unit. The oil storage unit has at least an air inlet channel communicating with one of the oil storage unit and the compression unit to realize the gas force on the support unit. The support unit realizes the sealing of the gas storage unit and the axial sealing of the compression unit. The above-mentioned oil storage unit includes at least an oil inlet channel, which is consistent with the previous inventive point, and / or includes an oil return channel communicating with the low-pressure area, which is consistent with the above characteristics. Explanation: Such an arrangement can achieve more stable medium-pressure gas for the support unit without being affected by the pressure in the oil storage chamber.

[0109] As Figure 15 , in some embodiments, the oil return structure of the compressor further includes bearing three 28. The compressor includes a motor 6. Bearing three 28 is arranged at an axial end of the crankshaft 7 relative to the bracket 4 and close to the motor 6. A first crankshaft communication hole 701 and a second crankshaft communication hole 702 are formed inside the crankshaft 7. One end of the first crankshaft communication hole 701 can communicate with the space where bearing three 28 is located, and the other end communicates with the second crankshaft communication hole 702. The other end of the second crankshaft communication hole 702 communicates with the lubrication cavity 11. The first crankshaft communication hole 701 extends along the axial direction of the crankshaft 7. The extending direction of the second crankshaft communication hole 702 has a fourth inclination angle with the axial direction of the crankshaft 7, and this fourth inclination angle is between 0 and 90°, so that oil entering the second crankshaft communication hole 702 can generate centrifugal inertia force. The present invention can also provide centrifugal inertia force during the rotation of the crankshaft through the inclined second crankshaft communication hole provided inside the crankshaft, thereby forming internal negative pressure and driving the gas or oil inside the crankshaft to flow into the lubrication cavity.

[0110] As Figure 15 As shown, it is an alternative embodiment of the present invention. For a compressor with the above-mentioned oil storage structure characteristics, the crankshaft has a first crankshaft communication hole 701, which respectively communicates with the bearing installation chamber of the suction crankshaft and the bearing installation chamber at the moving disc, and the communication through hole has an inclined part (second crankshaft communication hole 702) inclined to the bearing installation chamber of the over-moving disc. During the rotation of the crankshaft, the oil in the second air inlet channel with the inclined part forms centrifugal inertia force, and a pumping effect is formed on the oil and gas in the first air inlet channel (first crankshaft communication hole). As shown by the arrow, the flow direction of the oil and gas in the crankshaft enters from the left side of the compressor diagram shown and forms a cycle on the right side. At the same time, an air inlet channel three 308 communicating with the lubrication cavity 11 and the pump body suction cavity 12 is also formed on the moving disc 3 of the compressor. Compared with the above scheme, this scheme can increase the gas flow circulation inside the compressor and improve the reliability of the compressor.

[0111] The present invention also provides a compressor, which includes the oil return structure of the compressor described in any one of the preceding items.

[0112] The present invention also provides an air conditioner, which includes the compressor described above.

[0113] It is easy for those skilled in the art to understand that, on the premise of no conflict, the above-mentioned advantageous modes can be freely combined and superimposed.

[0114] 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 pointed out that for those of ordinary skill in the art, without departing from the technical principle of the present invention, several improvements and modifications can still be made, and these improvements and modifications should also be regarded as the protection scope of the present invention.

Claims

1. An oil return structure of a compressor, characterized in that: Including: A bracket (4), a moving disk (3), a stationary disk (2), a cover body (1), a crankshaft (7) and a first bearing (21). The interior of the bracket (4) has a lubrication cavity (11), the first bearing (21) is arranged in the lubrication cavity (11), and one axial end of the crankshaft (7) penetrates into the lubrication cavity (11) and is supported by the first bearing (21); an oil storage cavity (10) is further formed inside the bracket (4), and the oil storage cavity (10) is located radially outside the lubrication cavity (11). The side of the oil storage cavity (10) facing the moving disk (3) has an opening, and a sealing cover plate (17) is arranged at the opening, and the sealing cover plate (17) can move along the axial direction of the crankshaft (7).

2. The oil return structure of the compressor according to claim 1, characterized in that: A pump body compression cavity (13) is formed between the moving disk (3) and the stationary disk (2), and an air inlet hole three (171) is arranged on the sealing cover plate (17). The air inlet hole three (171) can introduce the gas in the pump body compression cavity (13) into the oil storage cavity (10) to form gas pressure on one axial side of the sealing cover plate, so as to drive the sealing cover plate to move axially.

3. The oil return structure of the compressor according to claim 2, characterized in that: A moving disk air guiding channel is formed on the moving disk (3). One end of the moving disk air guiding channel is communicated with the pump body compression cavity (13), and the other end can be communicated with the air inlet hole three (171); the air inlet hole three (171) is axially arranged along the crankshaft (7) and penetrates through the two axial end faces of the sealing cover plate (17).

4. The oil return structure of the compressor according to claim 3, characterized in that: The moving disk air guiding channel includes an air inlet hole one (301), an air inlet channel one (302), an air inlet hole two (303) and an air inlet channel two (304). The air inlet hole one (301) is formed on the axial end face of the moving disk (3) facing the stationary disk (2) and extends axially. The air inlet channel one (302) is formed inside the moving disk (3) and extends in the radial direction. The air inlet hole one (301) is communicated between the pump body compression cavity (13) and the air inlet channel one (302). The air inlet hole two (303) is formed inside the moving disk (3) and extends axially. The air inlet hole two (303) is communicated between the air inlet channel one (302) and the air inlet channel two (304). The air inlet channel two (304) is formed on the axial end face of the moving disk (3) facing the sealing cover plate (17) and extends in the radial direction. The air inlet channel two (304) is communicated between the air inlet hole two (303) and the air inlet hole three (171).

5. The oil return structure of the compressor according to claim 4, characterized in that: The intake hole 1 (301) is located radially inside the intake hole 2 (303). The radial length of the intake passage 2 (304) is greater than the radial length of the intake hole 2 (303). The radial length of the intake passage 2 (304) is greater than the radial length of the intake hole 3 (171). The radial length of the intake passage 1 (302) is greater than the radial length of the intake passage 2 (304).

6. The oil return structure of the compressor according to claim 1, wherein: The radially inner circumference of the sealing cover plate (17) is connected to the bracket (4), and a first sealing member mounting portion (172) is provided on the radially inner circumference of the sealing cover plate (17), and a first sealing member (22) is provided at the first sealing member mounting portion (172); the radially outer circumference of the sealing cover plate (17) is connected to the bracket (4), and a second sealing member mounting portion (173) is provided on the radially outer circumference of the sealing cover plate (17), and a second sealing member (23) is provided at the second sealing member mounting portion (173).

7. The oil return structure of the compressor according to claim 1, wherein: A first sealing portion mounting groove (408) and a second sealing portion mounting groove (409) are provided on the axial end face of the bracket (4) opposite to the sealing cover plate (17). The first sealing portion mounting groove (408) is arranged closer to the radially outer circumference of the sealing cover plate (17) relative to the radially inner circumference of the sealing cover plate (17), and the second sealing portion mounting groove (409) is arranged closer to the radially inner circumference of the sealing cover plate (17) relative to the radially outer circumference of the sealing cover plate (17). A third sealing member (22a) is provided in the first sealing portion mounting groove (408), and a fourth sealing member (23a) is provided in the second sealing portion mounting groove (409).

8. The oil return structure of the compressor according to claim 7, wherein: A first sealing portion pre-tightening structure (221) is provided at the bottom of the first sealing portion mounting groove (408). The first sealing portion pre-tightening structure (221) has an elastic force to always press the third sealing member (22a) against the sealing cover plate (17). A second sealing portion pre-tightening structure (231) is provided at the bottom of the second sealing portion mounting groove (409). The second sealing portion pre-tightening structure (231) has an elastic force to always press the fourth sealing member (23a) against the sealing cover plate (17).

9. The oil return structure of the compressor according to claim 1, wherein: It further includes a moving disk self-rotation limiting pin (18) and a sealing cover plate limiting pin (20). A moving disk self-rotation limiting portion (174) and a sealing cover plate self-rotation limiting portion (175) are provided on the sealing cover plate (17). A self-rotation limiting portion installation portion (403) is further provided on the bracket (4). The moving disk self-rotation limiting pin (18) cooperates with the moving disk self-rotation limiting portion (174) to form a self-rotation limit for the moving disk (3), and the sealing cover plate limiting pin (20) cooperates with both the sealing cover plate self-rotation limiting portion (175) and the self-rotation limiting portion installation portion (403) to form a self-rotation limit for the sealing cover plate (17).

10. The oil return structure of the compressor according to claim 9, characterized in that: Both the moving disk self-rotation limiting portion (174) and the sealing cover plate self-rotation limiting portion (175) are hole structures. One end of the moving disk self-rotation limiting pin (18) is fixedly connected to the moving disk (3), and the other end is inserted into the moving disk self-rotation limiting portion (174) to form a self-rotation limit for the moving disk (3). The self-rotation limiting portion installation portion (403) is also a hole structure. The sealing cover plate limiting pin (20) passes through the sealing cover plate self-rotation limiting portion (175) and is inserted into the self-rotation limiting portion installation portion (403) to form a self-rotation limit for the sealing cover plate (17). The sealing cover plate limiting pin (20) is fixedly connected to the sealing cover plate self-rotation limiting portion (175) and has a clearance fit with the self-rotation limiting portion installation portion (403).

11. The oil return structure of the compressor according to claim 1, characterized in that: An oil separation chamber (102) is formed inside the cover body (1). The oil storage chamber (10) can communicate with the oil separation chamber (102) to obtain oil. An oil outlet channel of the cover body, namely an oil outlet (101), is formed inside the cover body (1). An oil inlet channel of the stationary disk is formed inside the stationary disk (2), and an oil inlet channel of the bracket is formed inside the bracket (4). One end of the oil outlet channel of the cover body communicates with the oil separation chamber (102), and the other end communicates with one end of the oil inlet channel of the stationary disk. The other end of the oil inlet channel of the stationary disk communicates with one end of the oil inlet channel of the bracket, and the other end of the oil inlet channel of the bracket communicates with the oil storage chamber (10), so that the oil outlet (101), the oil inlet channel of the stationary disk, and the oil inlet channel of the bracket are sequentially communicated to guide the oil from the oil separation chamber (102) to the oil storage chamber (10).

12. The oil return structure of the compressor according to claim 11, characterized in that: The oil outlet (101) extends along the axial direction of the crankshaft (7). The oil inlet channel of the stationary disk includes an oil inlet channel one (201) and an oil inlet channel two (202). The oil inlet channel one (201) extends along the axial direction of the stationary disk (2). The extending direction of the oil inlet channel two (202) has a first inclination angle with the axial direction of the stationary disk (2). The first inclination angle is an angle between 0 and 90°, so that the extending direction of the oil inlet channel two (202) is neither parallel nor perpendicular to the extending direction of the oil inlet channel one (201). The oil inlet passage of the bracket includes an oil inlet passage three (401) and an oil inlet passage four (402). The oil inlet passage three (401) extends along the axial direction of the bracket (4). The extending direction of the oil inlet passage four (402) has a second inclined angle with the axial direction of the bracket (4). The second inclined angle is an angle between 0 and 90°, such that the extending directions of the oil inlet passage three (401) and the oil inlet passage four (402) are neither parallel nor perpendicular. The oil outlet (101), the oil inlet passage two (202), the oil inlet passage one (201), the oil inlet passage three (401), and the oil inlet passage four (402) are connected in sequence. The oil inlet passage four (402) is connected to the oil storage cavity (10).

13. The oil return structure of the compressor according to claim 2, characterized in that: It further includes a housing (5). The interior of the housing (5) has a cavity. The bracket (4), the stationary disk (2), and the moving disk (3) are all arranged in the cavity of the housing (5). A pump body suction cavity (12) is formed between the stationary disk (2), the moving disk (3), and the sealing cover plate (17). The pump body suction cavity (12) is communicated with the pump body compression cavity (13). The position where the bracket (4) is located is the low-pressure suction cavity (9) inside the housing (5). Refrigerant gas is sucked into the pump body suction cavity (12) through the low-pressure suction cavity (9). When the refrigerant gas passes through the bracket (4), it can cool down the oil storage cavity (10) inside the bracket (4).

14. The oil return structure of the compressor according to claim 13, characterized in that: A first oil return passage (404) is further formed on the bracket (4). One end of the first oil return passage (404) can be communicated with the oil storage cavity (10); the other end can be communicated with at least one of the low-pressure suction cavity (9), the pump body suction cavity (12), and the lubrication cavity (11).

15. The oil return structure of the compressor according to claim 14, characterized in that: The oil return structure of the compressor further includes a second bearing (25) and an eccentric member (26). One end of the eccentric member (26) is sleeved on the axial end of the crankshaft (7) located in the lubrication cavity (11), and the other end can be used to drive the moving disk (3). The second bearing (25) is supported between the eccentric member (26) and the moving disk (3), and the second bearing (25) is communicated with the lubrication cavity (11).

16. The oil return structure of the compressor according to claim 15, characterized in that: A first oil return hole (176) is further formed on the sealing cover plate (17). A moving disk oil return passage is formed on the moving disk. One end of the moving disk oil return passage can be communicated with the first oil return hole (176), and the other end is communicated to the position of the second bearing (25) to lubricate the second bearing (25).

17. The oil return structure of the compressor according to claim 16, characterized in that: The oil return hole 1 (176) is a hole axially opened through both axial end faces of the sealing cover plate (17). The moving disk oil return passage includes an oil return hole 2 (305), an oil return hole 3 (306), and an oil return hole 4 (307). The oil return hole 2 (305) is opened on the axial end face of the moving disk (3) facing the sealing cover plate (17) and extends radially. The oil return hole 3 (306) is opened inside the moving disk (3) and extends axially. The oil return hole 4 (307) is opened inside the moving disk (3) and extends in the radial direction. The oil return hole 2 (305) communicates between the oil return hole 1 (176) and the oil return hole 3 (306). The oil return hole 3 (306) communicates between the oil return hole 2 (305) and the oil return hole 4 (307), such that the oil return hole 1 (176), the oil return hole 2 (305), the oil return hole 3 (306), and the oil return hole 4 (307) are sequentially communicated. One end of the oil return hole 4 (307) communicates to the position of the second bearing (25) to lubricate the second bearing (25).

18. The oil return structure of the compressor according to claim 17, characterized in that: The radial length of the oil return hole 2 (305) is respectively greater than the radial length of the oil return hole 1 (176) and the radial length of the oil return hole 3 (306), and the radial length of the oil return hole 4 (307) is greater than the radial length of the oil return hole 2 (305).

19. The oil return structure of the compressor according to claim 17, characterized in that: An oil return passage 2 (406) and an oil return passage 3 (407) are further provided inside the bracket (4). The oil return passage 1 (404), the oil return passage 2 (406), and the oil return passage 3 (407) are sequentially communicated. One end of the oil return passage 3 (407) also communicates to the lubrication cavity (11) to lubricate the first bearing (21) and the second bearing (25) in the lubrication cavity (11).

20. The oil return structure of the compressor according to claim 19, characterized in that: The extending direction of the oil return passage 1 (404) forms a third inclined angle with the axial direction of the crankshaft (7), and this third inclined angle is between 0 and 90°. The extending direction of the oil return passage 2 (406) is along the radial direction of the bracket (4), and the extending direction of the oil return passage 3 (407) is along the axial direction of the crankshaft (7).

21. The oil return structure of the compressor according to claim 19, characterized in that: A throttling component (24) is further provided in the oil return hole four (307) or the oil return passage two (406); the throttling component (24) is of a cylindrical structure and includes a first section (241), a second section (242), and a third section (244) that are connected in sequence along its axial direction. The outer diameter of the first section (241) is greater than the outer diameter of the second section (242) to form a first step at the connection therebetween, so that the first section (241) functions as a limit seal. The outer diameter of the third section (244) is greater than the outer diameter of the second section (242) to form a second step at the connection therebetween, so that a fluid flow passage can be formed on the outer peripheral surface of the second section (242). A spiral throttling flow groove one (243) is provided on the outer peripheral wall of the third section (244), so that the fluid can be throttled via the throttling flow groove one (243).

22. The oil return structure of a compressor according to any one of claims 1-21, characterized in that: An oil-gas separation plate (27) is further provided inside the oil storage chamber (10). The oil-gas separation plate (27) divides the oil storage chamber (10) into a gas storage chamber (270) and a second oil storage chamber (272). The gas storage chamber (270) is located between the oil-gas separation plate (27) and the sealing cover plate (17). A communication diversion hole (271) penetrating through the axial two end faces of the oil-gas separation plate (27) is further provided on the oil-gas separation plate (27).

23. The oil return structure of a compressor according to any one of claims 1-21, characterized in that: The oil return structure of the compressor further includes a third bearing (28). The compressor includes a motor (6). The third bearing (28) is provided at an axial end of the crankshaft (7) close to the motor (6) relative to the bracket (4). A first crankshaft communication hole (701) and a second crankshaft communication hole (702) are provided inside the crankshaft (7). One end of the first crankshaft communication hole (701) can communicate with the space where the third bearing (28) is located, and the other end communicates with the second crankshaft communication hole (702). The other end of the second crankshaft communication hole (702) communicates with the lubrication chamber (11). The first crankshaft communication hole (701) extends along the axial direction of the crankshaft (7). The extending direction of the second crankshaft communication hole (702) has a fourth inclination angle with the axial direction of the crankshaft (7), and this fourth inclination angle is between 0 and 90°, so that centrifugal inertia force can be generated when oil enters the second crankshaft communication hole (702).

24. A compressor, characterized in that: An oil return structure of a compressor according to any one of claims 1-23 is included.

25. An air conditioner, characterized in that: A compressor according to claim 24 is included.

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