Scroll compressor floating back pressure structure, scroll compressor, air conditioner

Abstract

The present invention provides a scroll compressor floating back pressure structure, a scroll compressor, and an air conditioner, wherein the scroll compressor floating back pressure structure comprises a crankshaft, a movable scroll plate, and an upper bracket, wherein the movable scroll plate has a movable plate bearing seat, the crankshaft has a crankshaft eccentric portion which can be rotatably inserted into the movable plate bearing seat, the upper bracket is configured with a sleeve matching hole, and further comprises a balancing sleeve, the balancing sleeve has an inner hole and an outer circle, wherein the movable plate bearing seat can be rotatably inserted into the inner hole, the balancing sleeve can be rotatably inserted into the sleeve matching hole, the center of the outer circle coincides with the rotation center of the crankshaft, and the center of the inner hole does not coincide with the center of the outer circle, and a sealing ring is provided on the axial end face of the balancing sleeve, the radial inner region of the sealing ring has a refrigerant of a first pressure, and the radial outer region has a refrigerant of a second pressure, and the first pressure is greater than the second pressure. According to the present invention, the stability of the movable plate movement is improved, end face leakage is avoided, and the performance of the compressor is improved.

Description

Technical Field

[0001] The invention belongs to the technical field of compressor manufacturing, and in particular relates to a scroll compressor floating back pressure structure, a scroll compressor, and an air conditioner. Background Art

[0002] The scroll compressor consists of a sealed shell, a fixed scroll, a movable scroll, a bracket, an eccentric crankshaft, an anti-rotation mechanism and a motor. The profiles of the movable and fixed scrolls are both spiral. The movable scroll is eccentric to the fixed scroll and installed 180° apart, so multiple crescent-shaped spaces are formed between the movable and fixed scrolls. The movable scroll rotates with the center of the fixed scroll as the center and rotates at a certain rotation eccentric radius without self-rotation. The outer crescent-shaped space moves continuously toward the center. At this time, the refrigerant is gradually pushed toward the center space, and its volume continues to shrink while the pressure continues to increase until it is connected to the central exhaust hole. The high-pressure refrigerant is discharged from the pump body, completing the compression process.

[0003] When the scroll compressor is running, the gas force in the compression chamber causes the scroll disk to separate and overturn, causing the axial clearance to increase and refrigerant leakage. Summary of the invention

[0004] Therefore, the present invention provides a scroll compressor floating back pressure structure, a scroll compressor, and an air conditioner, which improve the stability of the moving disk movement, avoid end surface leakage, and improve the compressor performance.

[0005] In order to solve the above problems, the present invention provides a floating back pressure structure of a scroll compressor, including a crankshaft, a movable scroll plate, and an upper bracket, wherein the movable scroll plate has a movable plate bearing seat, and the crankshaft eccentric portion of the crankshaft can be rotatably inserted in the movable plate bearing seat, and the upper bracket is configured with a sleeve matching hole, and also includes a balancing sleeve, the balancing sleeve has an inner hole and an outer circle, wherein the movable plate bearing seat can be rotatably inserted in the inner hole, and the balancing sleeve can be rotatably inserted in the sleeve matching hole, the center of the outer circle coincides with the rotation center of the crankshaft and the center of the inner hole does not coincide with the center of the outer circle, the axial end face of the balancing sleeve facing the movable scroll plate is a first axial end face, and a first sealing ring is provided on the first axial end face, the radial inner area of ​​the first sealing ring has a refrigerant of a first pressure, and the radial outer area of ​​the first sealing ring has a refrigerant of a second pressure, and the first pressure is greater than the second pressure.

[0006] In some embodiments, the refrigerant at the second pressure is introduced from an intermediate compression chamber formed between the fixed scroll and the orbiting scroll.

[0007] In some embodiments, a stationary disk medium-pressure flow channel is constructed on the stationary scroll disk, and the stationary disk medium-pressure flow channel is connected to the intermediate compression chamber. A moving disk medium-pressure flow channel is constructed on the moving scroll disk, and the moving disk medium-pressure flow channel is connected to the radial outer area of ​​the sealing ring, and the moving disk medium-pressure flow channel can be connected to the stationary disk medium-pressure flow channel.

[0008] In some embodiments, the static plate medium-pressure flow channel has a static plate drainage outlet, and the static plate drainage outlet forms a countersunk hole. The movable plate medium-pressure flow channel has a movable plate drainage inlet. With the orbital and translational motion of the movable scroll plate, the movable plate drainage inlet can be connected to or disconnected from the countersunk hole.

[0009] In some embodiments, a sleeve sealing ring groove is configured on the first axial end surface, and the first sealing ring is installed in the sleeve sealing ring groove.

[0010] In some embodiments, the axial end face of the balancing sleeve facing away from the movable scroll is a second axial end face, the second axial end face has a second sealing ring, the radial inner area of ​​the second sealing ring has a refrigerant of a first pressure, and the radial outer area of ​​the second sealing ring has a refrigerant of a second pressure.

[0011] In some embodiments, the first sealing ring and / or the second sealing ring has an oil-passing cutout, and the oil-passing cutout can allow lubricating oil to flow between the radial inner side and the radial outer side of the first sealing ring and / or the second sealing ring.

[0012] In some embodiments, the first pressure is Pd, the second pressure is Pm, the self-weight of the balancing sleeve is G, the area covered by the outer circumference of the first sealing ring is S1, the area covered by the outer circumference of the second sealing ring is S2, and (S1-S2)*(Pd-Pm)=G.

[0013] The present invention also provides a scroll compressor, comprising the above-mentioned scroll compressor floating back pressure structure.

[0014] The present invention also provides an air conditioner, comprising the scroll compressor.

[0015] The present invention provides a scroll compressor floating back pressure structure, a scroll compressor, and an air conditioner, wherein the inner hole cooperates with the outer circumferential wall of the movable plate bearing seat, and the outer circle cooperates with the upper bracket through the sleeve matching hole, and the crankshaft rotates to drive the movable scroll plate to revolve and translate through the crankshaft eccentric part, and the movable scroll plate drives the balancing sleeve to rotate. Since the rotation center of the balancing sleeve coincides with the rotation center of the crankshaft, the balancing sleeve is sleeved on the movable plate bearing seat and combined with the crankshaft eccentric part to form a non-eccentric cylinder, so that the unbalanced mass on the shaft system is only the base plate of the movable scroll plate and the scroll teeth on the base plate, and the motion mass that needs to be balanced is To reduce, so that the rotation of the shaft system is more stable, the mass of the required balancing block can be selected to be smaller, the deformation of the crankshaft is reduced, and the vibration and noise of the compressor are reduced; in addition, the balancing sleeve arranged outside the movable plate bearing seat can also be supported under the movable scroll plate, which can effectively reduce the probability of overturning of the movable scroll plate, improve the operating stability of the pump body, and improve the efficiency of the compressor; the balancing sleeve is in a rotating motion state and has a follow-up relationship with the movable scroll plate. Therefore, the point of action of the back pressure resultant force on the back of the movable scroll plate always coincides with the center of the movable scroll plate base plate, so that a torque that causes the movable plate to overturn is eliminated during operation, thereby improving the stability of the movable plate movement, avoiding end surface leakage, and improving the performance of the compressor. BRIEF DESCRIPTION OF THE DRAWINGS

[0016] Figure 1 A longitudinal sectional view of the structure of a scroll compressor according to an embodiment of the present invention;

[0017] Figure 2 It is a schematic diagram of the three-dimensional structure of a balancing sleeve in a floating back pressure structure of a scroll compressor according to an embodiment of the present invention;

[0018] Figure 3 for Figure 2 A top view of

[0019] Figure 4 for Figure 3 Schematic diagram of the cross section of AA;

[0020] Figure 5 It is a schematic diagram of the assembly of the floating back pressure structure of the scroll compressor of the present invention;

[0021] Figure 6 for Figure 1 A schematic diagram of the structure of the upper bracket in FIG.

[0022] Figure 7 for Figure 1 A top view of the orbiting scroll in FIG.

[0023] Figure 8 for Figure 7 A cross-sectional view of

[0024] Fig. 9 for Figure 1 A bottom view of the fixed scroll disk in FIG.

[0025] Fig.10 for Fig. 9 Cross-sectional view of CC;

[0026] Fig.11 for Figure 1 Schematic diagram of the force acting on the balancing sleeve;

[0027] Fig.12 for Figure 1 Schematic diagram of the internal structure of the upper bracket;

[0028] Fig.13 is a schematic structural diagram of a first sealing ring;

[0029] Fig.14 A schematic diagram of the flow path of the pressure fluid in the floating back pressure structure of the scroll compressor and the back pressure of the movable scroll in an embodiment of the present invention;

[0030] Fig.15 The relative position relationship between the countersunk hole and the drainage inlet of the movable scroll before the back pressure of the movable scroll is connected to the intermediate pressure chamber is shown;

[0031] Fig.16 The relative position relationship between the countersunk hole and the drainage inlet of the movable disk when the back pressure of the movable scroll disk is connected with the intermediate pressure chamber is shown;

[0032] Fig.17 The diagram shows the relative position relationship between the countersunk hole and the movable disk drainage inlet after the back pressure of the movable scroll disk is connected to the intermediate pressure chamber.

[0033] The reference numerals are:

[0034] 1. Scroll compressor; 2. Compression mechanism; 3. Driving part; 4. Motor; 5. Stationary scroll; 5a. Stationary scroll tooth; 5b. Stationary scroll exhaust port; 5c. Stationary scroll medium pressure inlet hole; 5d. Stationary scroll medium pressure outlet channel; 5e. Stationary scroll medium pressure outlet hole; 5f. Countersunk hole; 5g. Sealing pin; 6. Moving scroll; 6a. Moving disk bearing seat; 6b. Moving disk scroll tooth; 6c. Moving disk base plate; 6c1. Front of moving disk base plate; 6c2. Back of moving disk base plate; 6d. Moving disk drainage inlet; 7. Cross slip ring; 8. Upper bracket; 8a. Sleeve matching hole; 8b. Moving disk supporting surface; 9. Upper cover; 10. Shell; 11. Balancing sleeve; 11a. Inner hole; 11b. Outer circle; 11c. Sleeve sealing ring groove; 111. First sealing ring; 111a. Oil cut; 112. Second sealing ring; 12. Moving plate sliding bearing; 12a. Inner hole of moving plate sliding bearing; 13. Crankshaft; 13a. Eccentric part of crankshaft; 13b. Center oil hole of crankshaft; 14. Thrust bearing; 15. Main bearing; 16. Main balance block; 17. Motor rotor; 18. Motor stator; 19. Auxiliary balance block; 20. Auxiliary bearing cover plate; 21. Lower bracket; 22. Auxiliary bearing; 23. Oil return pipe; 24. Oil supply mechanism; 25. Lower cover; 26. Oil storage tank. DETAILED DESCRIPTION

[0035] See also Figures 1 to 17As shown, according to an embodiment of the present invention, a scroll compressor floating back pressure structure is provided, comprising a crankshaft 13, a movable scroll plate 6 (also referred to as a movable plate, the same below), and an upper bracket 8, wherein the movable scroll plate 6 has a movable plate bearing seat 6a, and the crankshaft 13 has a crankshaft eccentric portion 13a which is rotatably inserted into the movable plate bearing seat 6a, and the upper bracket 8 is configured with a sleeve matching hole 8a, and further comprises a balancing sleeve 11, and the balancing sleeve 11 has an inner hole 11a and an outer circle 11b, wherein the movable plate bearing seat 6a is rotatably inserted into the inner hole 11a, and the balancing sleeve 11 is rotatably inserted into the sleeve In the matching hole 8a, the center of the outer circle 11b coincides with the rotation center of the crankshaft 13, and the center of the inner hole 11a does not coincide with the center of the outer circle 11b, that is, the inner hole 11a and the outer circle 11b have an eccentric design structure, and the axial end face of the balancing sleeve 11 facing the movable scroll 6 is a first axial end face, and a first sealing ring 111 is provided on the first axial end face, and a radially inner area of ​​the first sealing ring 111 has a refrigerant of a first pressure, and a radially outer area of ​​the first sealing ring 111 has a refrigerant of a second pressure, and the first pressure is greater than the second pressure. In this technical solution, on the one hand, the inner hole 11a cooperates with the outer circumferential wall of the movable plate bearing seat 6a, and the outer circle 11b cooperates with the upper bracket 8 through the sleeve matching hole 8a. The crankshaft 13 rotates to drive the movable scroll plate 6 to revolve and translate through the crankshaft eccentric portion 13a, and the movable scroll plate 6 drives the balancing sleeve 11 to rotate. Since the rotation center of the balancing sleeve 11 coincides with the rotation center of the crankshaft 13, the balancing sleeve 11 is sleeved on the movable plate bearing seat 6a and combined with the crankshaft eccentric portion 13a. The three are combined together to form a non-eccentric cylinder, so that the unbalanced mass on the shaft system is only the base plate of the movable scroll plate 6 and the scroll teeth on the base plate, and the moving mass that needs to be balanced is reduced, so that the rotation of the shaft system is more stable, and the mass of the balancing block required can be selected to be smaller, thereby reducing the deformation of the crankshaft 13 and reducing the vibration and noise of the compressor; the balancing sleeve 11 sleeved outside the movable plate bearing seat 6a can also be supported under the movable scroll plate 6, which can effectively reduce the overturning probability of the movable scroll plate 6, improve the operating stability of the pump body, and improve the efficiency of the compressor; on the other hand, the balancing sleeve 11 is in a rotating motion state and is in a follow-up relationship with the movable scroll plate 6. Therefore, the point of action of the back pressure resultant force on the back of the movable scroll plate 6 always coincides with the center of the base plate of the movable scroll plate 6, so that a torque that causes the movable plate to overturn is eliminated during operation, thereby improving the stability of the movable plate movement, avoiding end face leakage, and improving the performance of the compressor.

[0036] It should be noted that the floating back pressure refers to the axial floating state of the orbiting scroll 6 caused by the back pressure.

[0037] In some embodiments, the refrigerant of the second pressure is introduced from the intermediate compression chamber S formed between the fixed scroll 5 (also referred to as the fixed scroll, the same below) and the movable scroll 6. It can be understood that the refrigerant gas introduced from the intermediate compression chamber S is at medium pressure, and the refrigerant of the first pressure can be understood as the exhaust pressure refrigerant gas in the shell 10. It can be understood that the intermediate compressor chamber S is a chamber in the compression process between the suction and exhaust of the compressor, which is a dynamic process. The specific selection of the intermediate compression chamber S can be selected according to the actual working conditions.

[0038] As a specific implementation method, the static scroll plate 5 is constructed with a static disk medium-pressure flow channel, and the static disk medium-pressure flow channel is connected to the intermediate compression chamber S. The movable scroll plate 6 is constructed with a movable disk medium-pressure flow channel, and the movable disk medium-pressure flow channel is connected to the radial outer area of ​​the sealing ring 111, and the movable disk medium-pressure flow channel can be connected to the static disk medium-pressure flow channel.

[0039] In some embodiments, the static plate medium-pressure flow channel has a static plate drainage outlet, and the static plate drainage outlet forms a countersunk hole 5f. The movable plate medium-pressure flow channel has a movable plate drainage inlet 6d. As the movable scroll plate 6 revolves and moves, the movable plate drainage inlet 6d can be connected to or cut off from the countersunk hole 5f, thereby preventing excessive back pressure caused by one-way connection. Intermittent connection can control the back pressure value and avoid excessive back pressure. The area of ​​the countersunk hole 5f can be appropriately designed to be larger (larger than the movable plate drainage inlet 6d) to ensure that the connection time meets the back pressure requirement.

[0040] A sleeve sealing ring groove 11 c is configured on the first axial end surface, and the first sealing ring 111 is installed in the sleeve sealing ring groove 11 c, which can effectively limit the position of the first sealing ring 111.

[0041] In some embodiments, the axial end face of the balancing sleeve 11 facing away from the movable scroll plate 6 is a second axial end face, and a second sealing ring 112 is provided on the second axial end face. The radial inner area of ​​the second sealing ring 112 has a refrigerant of a first pressure, and the radial outer area of ​​the second sealing ring 112 has a refrigerant of a second pressure. It can be understood that the radial inner sides of the first sealing ring 111 and the second sealing ring 112 are connected through the central through hole of the balancing sleeve 11, and the radial outer sides of the first sealing ring 111 and the second sealing ring 112 are connected through the sleeve matching hole 8a.

[0042] The first sealing ring 111 and / or the second sealing ring 112 has an oil passage cutout 111a, and the oil passage cutout 111a can allow the lubricating oil to flow between the radial inner side and the radial outer side of the first sealing ring 111 and / or the second sealing ring 112, thereby ensuring sufficient lubrication between the friction pairs corresponding to the radial outer and inner areas. The oil passage cutout 111a can specifically utilize the principle of labyrinth sealing. It can be understood that the size of the oil passage cutout 111a should not be too large, so as to allow the lubricating oil to flow between the radial inner side and the radial outer side and to form an oil film seal to prevent the penetration of pressure refrigerant on both sides, which is a design premise.

[0043] In some embodiments, the area of ​​the first axial end face and the second axial end face is S0, the first pressure is Pd, the second pressure is Pm, the self-weight of the balancing sleeve 11 is G, the area covered by the outer circumference of the first sealing ring 111 is S1, and the area covered by the outer circumference of the second sealing ring 112 is S2, (S1-S2)*(Pd-Pm)=G, at this time, the resultant force of the two axial end faces of the balancing sleeve 11 is 0. In theory, the end face contact friction power consumption of the movable scroll 6 and the fixed scroll 5 is smaller, the power consumption is less, and the energy efficiency is improved.

[0044] The present invention also provides a scroll compressor, comprising the above-mentioned scroll compressor floating back pressure structure.

[0045] The following combination Figures 1 to 10 The technical solution of the present invention is further explained.

[0046] like Figure 1 As shown, the scroll compressor 1 contains a compression mechanism 2 and a driving part 3 in a sealed container. The sealed container is composed of a sealed container upper cover 9, a sealed container shell 10 and a sealed container lower cover 25; the compression mechanism 2 is composed of a fixed scroll 5, a movable scroll 6, and a cross slip ring 7; the driving part 3 is mainly composed of a motor 4 and a crankshaft 13. During the operation of the scroll compressor, the movable scroll 6 is driven by the driving part 3 to rotate and mesh with the fixed scroll 5 to form a compression chamber. As the crankshaft 13 rotates, the refrigerant enters the compression mechanism 2, the movable scroll 6 continues to rotate and translate and always maintains a good meshing state, the suction chamber continuously moves toward the center, the volume continuously decreases, and the pressure in the chamber continuously increases. When the compression reaches a predetermined compression ratio, the refrigerant is discharged from the central exhaust port 5b of the fixed scroll 5, enters the space of the sealed container upper cover, passes through the exhaust channel of the fixed scroll 5 and the upper bracket 8, enters the space of the motor 4, cools the motor 4, and then is discharged from the scroll compressor 1 and enters the air conditioning system to complete the refrigeration / heating cycle.

[0047] like Figures 2 to 4As shown, the structure of the scroll compressor balance sleeve 11 of the present invention has the core feature that the inner hole 11a and the outer circle 11b of the balance sleeve 11 are designed as eccentric structures, that is, the center of the inner hole 11a is not concentric with the outer circle 11b. Figure 3 As shown, the upper and lower end surfaces of the balancing sleeve 11 are each provided with a sleeve sealing ring groove 11c for accommodating the first sealing ring and the second sealing ring 112. Optimally, the two sleeve sealing ring grooves 11c on the upper and lower end surfaces of the balancing sleeve 11 have the same structure, and the sleeve sealing ring groove 11c is concentric with the inner hole 11a.

[0048] like Figure 5 and Figure 6 As shown, the shaft system of the scroll compressor of the present invention includes a movable scroll plate 6, a balancing sleeve 11, a main balancing block 16, and a motor rotor 17 assembled on a crankshaft 13, and a secondary balancing block 19 assembled on the motor rotor 17. The first sealing ring 111 is arranged in the sleeve sealing ring groove 11c on the upper and lower end surfaces of the balancing sleeve 11. The eccentric portion 13a of the crankshaft is inserted into the inner hole 12a of the movable plate sliding bearing.

[0049] like Figure 7 and Figure 8 As shown, the movable scroll 6 includes a movable scroll bearing seat 6a, an inner hole 11a cooperates with the movable scroll 6, and an outer circle 11b cooperates with the sleeve matching hole 8a of the upper bracket 8. The balancing sleeve 11 forms a constraint on the movable scroll 6 in the radial direction, which can increase the stability of the movable scroll when running at high speed, prevent the movable scroll from tipping over and causing pump body leakage, and improve the efficiency of the compressor.

[0050] The rotation of the motor drives the crankshaft 13 to rotate, and its eccentric part 13a drives the movable scroll 6 to revolve and translate. Then the movable scroll 6 drives the balancing sleeve 11 to rotate, and the core feature is that the rotation center of the balancing sleeve 11 is the same as the rotation center of the crankshaft 13, and is also concentric with the bracket bearing hole 8b. The front face 6c1 of the movable disc base plate cooperates with the end face 5h of the static disc, and the back face 6c2 of the movable disc base plate is located on the movable disc support surface 8b of the upper bracket 8. The movable disc drainage inlet 6d is set on the movable disc base plate 6c, and the optimal one is that the movable disc drainage inlet passes through the movable disc base plate 6c.

[0051] like Fig. 9 and Fig.10 As shown, the fixed scroll 5 is provided with a fixed scroll vortex 5a, and the compressed gas is discharged from the fixed scroll exhaust port 5b. The fixed scroll medium pressure inlet hole 5c is located in the middle compression chamber, and the fixed scroll medium pressure outlet channel 5d is sealed with a sealing pin 5g, and the fixed scroll medium pressure outlet channel 5d is connected with the fixed scroll medium pressure outlet hole 5e. At the same time, a countersunk hole 5f is provided on the end surface of the fixed scroll (the section facing the movable scroll 6) and is connected with the fixed scroll medium pressure outlet hole 5e.

[0052] like Fig.11The first sealing ring 111 of the upper end face (i.e., the first axial end face) of the balancing sleeve 11 cooperates with the back face 6c2 of the moving plate substrate to form an end face seal, and the second sealing ring 112 of the lower end face of the balancing sleeve 11 cooperates with the bottom face of the upper bracket to form an end face seal, and the inside of the sealing ring is the exhaust high pressure Pd (i.e., the first pressure), and the outside of the sealing ring is the intermediate pressure Pm (i.e., the second pressure). Therefore, the force on the balancing sleeve 11 is as follows:

[0053] Force on the upper end surface: Fu = (S0-S1)Pm+S1Pd;

[0054] Force on the lower end surface: Fd = (S0-S2)Pm+S2Pd;

[0055] The resultant force F0=Fu-Fd+G is 0, that is, (S1-S2)*(Pd-Pm)=G, which is theoretically optimal.

[0056] like Fig.14 As shown, using Fig.10 The intermediate pressure channel shown in the figure guides the intermediate pressure in the intermediate compression chamber S to the back side 6c2 of the moving disk substrate. At this time, the back side of the moving disk substrate is subjected to two pressures. Among them, the intermediate pressure Pm is outside the sealing ring, and the exhaust high pressure Pd is inside the sealing ring. The two form a combined force to push the moving scroll disk toward the static scroll disk, so that it can ensure the end face sealing and prevent leakage. And compared with the conventional back pressure structure, the back pressure structure of the present invention, the balance sleeve is in a rotating motion state, and is in a follow-up relationship with the moving scroll disk. Therefore, the point of action of the back pressure combined force on the back side of the moving disk substrate always coincides with the center of the moving disk substrate. This feature eliminates a moment that causes the moving disk to overturn during operation, further improves the stability of the moving scroll disk movement, avoids end face leakage, and improves the performance of the compressor.

[0057] For example Figures 15 to 17 Different connection states of the back pressure chamber are shown respectively. The drainage inlet 6d of the moving plate is intermittently connected and closed with the countersunk hole 5f on the end surface of the stationary plate. Fig.15 A schematic diagram showing when the back pressure starts to communicate, wherein the movable disk inlet 6d is about to communicate with the fixed scroll disk end surface countersunk hole 5f. Fig.16 Schematic diagram when the back pressure is already connected, where the movable disk drainage inlet 6d is already connected to the static scroll disk end surface countersunk hole 5f. Fig.17 The schematic diagram shows the back pressure is closed, in which the moving disk drainage inlet 6d is no longer connected to the fixed scroll disk end surface countersunk hole 5f. The inventive structure provides an effective back pressure system for high-speed scroll compressors to achieve floating seal of the pump body. Compared with the conventional oil supply design, it prevents the moving disk from tipping over, greatly improves the sealing effect of the compressor, avoids pump body leakage, and improves the efficiency of the compressor.

[0058] The above is a typical embodiment of the present invention, which briefly expresses the core idea of ​​the invention. Through the floating back pressure structure of the present invention, the lubrication and sealing effect of the scroll compressor when running at high speed is achieved, the leakage loss of the compressor during high-speed rotation is prevented, and the reliability and compressor performance are improved.

[0059] The present invention also provides an air conditioner, comprising the scroll compressor.

[0060] It is easy for those skilled in the art to understand that, under the premise of no conflict, the above-mentioned advantageous methods can be freely combined and superimposed.

[0061] The above are only preferred embodiments of the present invention and are not intended to limit the present invention. Any modifications, equivalent substitutions and improvements made within the spirit and principles of the present invention shall be included in the protection scope of the present invention. The above are only preferred embodiments of the present invention. It should be pointed out that for ordinary technicians in this technical field, several improvements and variations can be made without departing from the technical principles of the present invention, and these improvements and variations should also be regarded as the protection scope of the present invention.

Claims

1. A scroll compressor floating back pressure structure, It is characterized in that The invention comprises a crankshaft (13), a movable scroll (6), and an upper bracket (8), wherein the movable scroll (6) has a movable scroll bearing seat (6a), the crankshaft (13) has a crankshaft eccentric portion (13a) which is rotatably inserted into the movable scroll bearing seat (6a), the upper bracket (8) is provided with a sleeve matching hole (8a), and further comprises a balancing sleeve (11), wherein the balancing sleeve (11) has an inner hole (11a) and an outer circle (11b), wherein the movable scroll bearing seat (6a) is rotatably inserted into the inner hole (11a), and the balancing sleeve (11) is rotatably inserted into the movable scroll bearing seat (6a). In the sleeve matching hole (8a), the center of the outer circle (11b) coincides with the rotation center of the crankshaft (13), and the center of the inner hole (11a) does not coincide with the center of the outer circle (11b); the axial end face of the balancing sleeve (11) facing the movable scroll (6) is a first axial end face, and a first sealing ring (111) is provided on the first axial end face; a radial inner area of ​​the first sealing ring (111) has a refrigerant of a first pressure, and a radial outer area of ​​the first sealing ring (111) has a refrigerant of a second pressure, and the first pressure is greater than the second pressure.

2. The scroll compressor floating back pressure structure according to claim 1, It is characterized in that The refrigerant of the second pressure is introduced from the intermediate compression chamber (S) formed between the fixed scroll (5) and the movable scroll (6).

3. The scroll compressor floating back pressure structure according to claim 2, It is characterized in that The stationary scroll (5) is provided with a stationary disk medium-pressure flow channel, and the stationary disk medium-pressure flow channel is connected to the intermediate compression chamber (S); the movable scroll (6) is provided with a movable disk medium-pressure flow channel, and the movable disk medium-pressure flow channel is connected to the radial outer area of ​​the sealing ring (111), and the movable disk medium-pressure flow channel can be connected to the stationary disk medium-pressure flow channel.

4. The scroll compressor floating back pressure structure according to claim 3, It is characterized in that The static disk medium-pressure flow channel has a static disk drainage outlet, and the static disk drainage outlet forms a countersunk hole (5f). The dynamic disk medium-pressure flow channel has a dynamic disk drainage inlet (6c). With the orbital and translational movement of the dynamic scroll (6), the dynamic disk drainage inlet (6c) can be connected to or cut off from the countersunk hole (5f).

5. The scroll compressor floating back pressure structure according to claim 1, It is characterized in that A sleeve sealing ring groove (11c) is configured on the first axial end surface, and the first sealing ring (111) is installed in the sleeve sealing ring groove (11c).

6. The scroll compressor floating back pressure structure according to claim 1, It is characterized in that The axial end face of the balancing sleeve (11) facing away from the movable scroll (6) is a second axial end face, and a second sealing ring (112) is provided on the second axial end face. The radial inner area of ​​the second sealing ring (112) has a refrigerant at a first pressure, and the radial outer area of ​​the second sealing ring (112) has a refrigerant at a second pressure.

7. The scroll compressor floating back pressure structure according to claim 6, It is characterized in that The first sealing ring (111) and / or the second sealing ring (112) have an oil-passing cutout (111a), and the oil-passing cutout (111a) can allow lubricating oil to flow between the radial inner side and the radial outer side of the first sealing ring (111) and / or the second sealing ring (112).

8. The scroll compressor floating back pressure structure according to claim 6, It is characterized in that The first pressure is Pd, the second pressure is Pm, the self-weight of the balancing sleeve (11) is G, the area covered by the outer circumference of the first sealing ring (111) is S1, the area covered by the outer circumference of the second sealing ring (112) is S2, and (S1-S2)*(Pd-Pm)=G.

9. A scroll compressor, It is characterized in that The invention comprises the scroll compressor floating back pressure structure according to any one of claims 1 to 8.

10. An air conditioner, It is characterized in that Includes the scroll compressor as described in claim 9.

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