A dual-cavity rotary compressor and air conditioner

Abstract

The present application relates to the field of air conditioners, in particular to a double-cavity rotor compressor and an air conditioner; the double-cavity rotor compressor comprises: an inner cylinder having an outer peripheral wall surface; an outer cylinder having an inner peripheral wall surface, the outer cylinder being coaxially sleeved outside the inner cylinder; a ring wall being sleeved outside the inner cylinder and located inside the outer cylinder, the ring wall comprising an inner ring surface and an outer ring surface; the inner peripheral wall surface is tangent to the outer ring surface, and an outer compression cavity is formed between the inner peripheral wall surface and the outer ring surface; the outer peripheral wall surface is tangent to the inner ring surface, and an inner compression cavity is formed between the outer peripheral wall surface and the inner ring surface; a sliding vane is arranged between the inner peripheral wall surface and the outer peripheral wall surface and passes through the ring wall, the sliding vane comprising an outer end and an inner end, the outer end being in sealed sliding contact with the inner peripheral wall surface, and the inner end being in sealed sliding contact with the outer peripheral wall surface; the sliding vane can rotate with the ring wall and can slide radially in the ring wall, so as to solve the technical problem of separation of the sliding vane from the cylinder during operation of the sliding vane compressor.

Description

TECHNICAL FIELD

[0001] The present application relates to the field of air conditioners, in particular to a double-cavity rotor compressor and an air conditioner. BACKGROUND

[0002] At present, small and medium-sized refrigeration compressors mainly include reciprocating piston compressors, rolling piston compressors, scroll compressors and sliding vane compressors. In the most common rolling piston compressor structure, the eccentric structure separates the suction and discharge chambers, and the piston is rotated by the eccentric part to complete compression. However, when the tail pressure is insufficient during startup, or the rotation speed is too high and the action is delayed, or liquid is sucked, the head of the sliding vane will be separated from the piston, resulting in cold leakage, noise and vibration caused by sliding vane impact, and work stability problems. Integrating the sliding vane with the piston to solve the above problems makes the process of the parts worse, the cost higher, the processing difficulty greater, and the yield lower.

[0003] The sliding vane compressor has simple parts, no eccentric structure, stable torque, and small vibration. The main shaft drives the sliding vane to rotate, the head of the sliding vane abuts against the inner wall of the cylinder, and the tail is supported by back pressure or spring force. The sliding vane compressor will also have the problems of the rolling piston compressor mentioned above, and the number of sliding vanes is larger, which has a greater impact. In some sliding vane compressors, the sliding vane is pushed out by the refrigeration oil pressure of the tail of the sliding vane. When the high pressure is not stable, the sliding vane is easy to separate, and the same problems of cold leakage, noise and vibration caused by sliding vane impact, and work stability problems as the rolling piston compressor occur.

[0004] At present, there is no good solution to effectively prevent the sliding vane of the sliding vane compressor from separating from the cylinder. SUMMARY

[0005] To solve the technical problem of separation of the sliding vane from the cylinder during the operation of the sliding vane compressor, a double-cavity rotor compressor and an air conditioner are provided.

[0006] In one aspect, the present application provides a double-cavity rotor compressor, comprising:

[0007] An inner cylinder having an outer peripheral wall surface;

[0008] An outer cylinder having an inner peripheral wall surface, the outer cylinder being coaxially sleeved outside the inner cylinder;

[0009] A ring wall sleeved outside the inner cylinder and located inside the outer cylinder, the ring wall comprising an inner ring surface and an outer ring surface; the inner peripheral wall surface is sealingly tangent to the outer ring surface, and an outer compression chamber is formed between the inner peripheral wall surface and the outer ring surface; the inner ring surface is sealingly tangent to the outer peripheral wall surface, and an inner compression chamber is formed between the outer peripheral wall surface and the inner ring surface;

[0010] A slide is arranged between the inner peripheral wall surface and the outer peripheral wall surface of the ring wall, the slide comprising an outer end and an inner end, the outer end being in sealing sliding contact with the inner peripheral wall surface, and the inner end being in sealing sliding contact with the outer peripheral wall surface; the slide being capable of rotating with the ring wall and being capable of sliding radially in the ring wall.

[0011] Preferably, the double-cavity rotary compressor further comprises a rotating shaft, the rotating shaft being provided with a central portion, one end surface of the central portion being formed with an annular groove, and a side wall of the annular groove constituting the ring wall.

[0012] Preferably, the annular groove has a bottom wall; the slide further comprises a guide portion in the axial direction of the inner cylinder, the guide portion protruding the inner end in the radial direction.

[0013] The central portion is provided with a sliding groove, the sliding groove penetrating the ring wall, the slide being located in the sliding groove, and the guide portion being opposite to the bottom wall in the axial direction.

[0014] Preferably, the double-cavity rotary compressor further comprises an upper flange, the upper flange having an upper mating surface facing the outer cylinder, the upper mating surface being provided with an oil groove, and each end portion of the sliding groove facing the rotating shaft axis being in communication with the oil groove.

[0015] Preferably, the double-cavity rotary compressor further comprises a lower flange, the inner cylinder being arranged on the lower flange, the lower flange being provided with a first through hole axially penetrating the inner cylinder and the lower flange, and the upper flange being provided with a second through hole penetrating the upper flange; the first through hole and the second through hole being coaxial and being eccentrically arranged relative to the inner cylinder.

[0016] One end of the rotating shaft penetrates the first through hole, and the other end penetrates the second through hole.

[0017] Preferably, an axial depth of the annular groove is h1, an axial height of the central portion is h, 0.2h≤h1≤0.6h, a radius of the inner annular surface is r1, a radius of the outer annular surface is r2, and 0.4h≤(r2-r1)≤0.8h.

[0018] Preferably, a roller is arranged on the outer peripheral wall surface of the inner cylinder; when the slide rotates, the inner end of the slide can drive the roller to rotate.

[0019] Preferably, a radius of the inner peripheral wall surface of the outer cylinder is R1, a radius of an outer circular surface of the roller is R2, an outer end surface of the slide is a circular surface, and a diameter d1 of the outer end surface of the slide is R1-R2; an inner end surface of the slide is a circular surface, and a diameter d2 of the inner end surface of the slide is R1-R2.

[0020] Preferably, the intake hole and the exhaust hole of the double-cylinder rotary compressor are arranged on the lower flange.

[0021] In another aspect, the application also provides an air conditioner comprising the double-cylinder rotary compressor.

[0022] The application limits the rotation of the vane between the outer peripheral wall surface of the inner cylinder and the inner peripheral wall surface of the outer cylinder, so that the vane does not separate from the inner peripheral wall surface of the outer cylinder and the outer peripheral wall surface of the inner cylinder due to centrifugal force, back pressure change, and pressure in the compression chamber, thereby avoiding leakage of the compressed gas (refrigerant), reducing vibration and noise caused by the collision between the vane and the inner cylinder and the outer cylinder. BRIEF DESCRIPTION OF DRAWINGS

[0023] Figure 1 It is an exploded view of the double-cylinder rotary compressor of the embodiment of the application;

[0024] Figure 2 It is a sectional view of the double-cylinder rotary compressor of the embodiment of the application;

[0025] Figure 3 It is a schematic view of the lower flange of the embodiment of the application;

[0026] Figure 4 It is a schematic view of the upper flange of the embodiment of the application;

[0027] Figure 5 It is a schematic view of the rotating shaft of the embodiment of the application;

[0028] Figure 6 It is a schematic view of the vane structure of the embodiment of the application;

[0029] Figure 7 It is a sectional view of the embodiment of the application in A-A direction; Figure 2

[0030] It is a schematic view of the embodiment of the application when the vane is in the initial position; Figure 8 Figure 7 It is a schematic view of the embodiment of the application when the vane is rotated clockwise by 90°;

[0031] Figure 9 Figure 8 It is a schematic view of the embodiment of the application when the vane is rotated clockwise by 90° on the basis of the;

[0032] Figure 10 It is a schematic view of the embodiment of the application when the vane is rotated clockwise by 90° on the basis of the; Figure 9

[0033] It is a schematic view of the embodiment of the application when the vane is rotated clockwise by 90° on the basis of the; Figure 11 Figure 10 It is a schematic view of the embodiment of the application when the vane is rotated clockwise by 90° on the basis of the;​​​

[0034] Figure 12 Fig. 2 is a schematic view of the slide clockwise rotating 90° on the basis of Fig. 1; Figure 11

[0035] Figure 13 Fig. 4 is a schematic view of the slide clockwise rotating 90° on the basis of Fig. 3; Figure 12

[0036] Figure 14 Fig. 6 is a schematic view of the embodiment of the present application provided with three slides;

[0037] Figure 15 Fig. 8 is a schematic view of the embodiment of the present application provided with four slides.

[0038] Figure 16 Fig. 10 is a schematic view of the embodiment of the present application provided with four slides.

[0039] The signs in the drawings represent:

[0040] 1, inner cylinder; 2, outer cylinder; 3, rotating shaft; 301, center part; 302, annular groove; 303, ring wall; 3031, inner ring surface; 3032, outer ring surface; 304, bottom wall; 305, sliding groove; 401, outer compression cavity; 402, inner compression cavity; 5, slide; 501, guide part; 6, upper flange; 601, oil groove; 7, lower flange; 701, air inlet hole; 702, air outlet hole; 8, roller. DETAILED DESCRIPTION

[0041] In order to make the purpose, technical scheme and advantages of the embodiments of the present application clearer, the technical scheme of the embodiments of the present application will be described clearly and completely below in conjunction with the drawings in the embodiments of the present application. Obviously, the described embodiments are some embodiments of the present application, rather than all the embodiments of the present application. Based on the embodiments in the present application, all other embodiments obtained by those skilled in the art without creative labor fall within the protection scope of the present application.

[0042] The terms used in the embodiments of the present application are merely for the purpose of describing specific embodiments, and are not intended to limit the present application. The singular forms "a", "an" and "the" used in the embodiments of the present application and the appended claims are also intended to include the plural forms, unless the context clearly indicates otherwise. "Plural" generally contains at least two, but does not exclude the case of containing at least one.

[0043] ​​It should be understood that the term "and / or" as used herein merely describes an associated relationship between associated objects, and can represent three relationships, for example, A and / or B can represent three cases of A existing alone, A and B existing simultaneously, and B existing alone. In addition, the character " / " in the text generally represents that the front and rear associated objects have an "or" relationship; "first", "second" in the text are only used to distinguish different technical features, and do not have a sequence; "upper", "lower", "front" and "rear" in the text are only used to more conveniently illustrate the positional relationship of the technical features, and have certain significance only in combination with the actual use situation or the specific position description in the preceding text, and are not absolute positional relationships.

[0044] It should also be noted that the terms "comprising", "containing", or any other variant thereof are intended to cover non-exclusive inclusion, so that a product or system including a series of elements not only includes those elements, but also includes other elements not explicitly listed, or includes elements inherent to such product or system. Without more limitations, the element defined by the statement "comprising a" does not exclude the existence of another identical element in the product or system comprising the element.

[0045] The present application relates to the field of air conditioners, in particular to a double-cavity rotor compressor and an air conditioner; At present, small and medium-sized refrigeration compressors mainly include reciprocating piston compressors, rolling piston compressors, scroll compressors and sliding vane compressors, the most common rolling piston compressor structure has an eccentric structure separating the suction and discharge chambers by a sliding vane, and the piston is rotated by the eccentric part to complete compression; However, when starting, the tail pressure is insufficient, or the rotation speed is too high, the action is delayed, or the suction is liquid, the sliding vane head will be separated from the piston, resulting in cold leakage, noise and vibration caused by sliding vane impact and work stability problems; The above problems are solved by integrating the sliding vane with the piston, which makes the process of the part worse, the cost is higher, the processing difficulty is increased, and the yield is low; The sliding vane compressor has the problems of simple parts, no eccentric structure, stable torque, small vibration, the main shaft drives the sliding vane to rotate, the sliding vane head abuts against the inner wall of the cylinder, and the tail is supported by back pressure or spring force. The sliding vane compressor also has the problems of the rolling piston compressor, and the number of sliding vanes is larger, which has a greater impact; In some sliding vane compressors, the sliding vane is pushed out by the refrigeration oil pressure of the sliding vane tail, and when the high pressure is not stable, the sliding vane is easy to separate, and the same problems of cold leakage, noise and vibration caused by sliding vane impact and work stability problems as the rolling piston compressor occur.

[0046] To solve the technical problem of separation of the sliding vane and the cylinder during the operation of the sliding vane compressor, a double-cavity rotor compressor and an air conditioner are provided.

[0047] On the one hand, as Figures 1-16As shown, the double-cavity rotary compressor provided by the application comprises: an inner cylinder 1 having an outer peripheral wall surface; an outer cylinder 2 having an inner peripheral wall surface, the outer cylinder 2 being coaxially sleeved outside the inner cylinder 1; a ring wall 303 being sleeved outside the inner cylinder 1 and located inside the outer cylinder 2, the ring wall 303 comprising an inner ring surface 3031 and an outer ring surface 3032; the inner peripheral wall surface being sealingly tangent to the outer ring surface 3032, and an outer compression cavity 401 being formed between the inner peripheral wall surface and the outer ring surface 3032; the outer peripheral wall surface being sealingly tangent to the inner ring surface 3031, and an inner compression cavity 402 being formed between the outer peripheral wall surface and the inner ring surface 3031; and a sliding vane 5 being arranged between the inner peripheral wall surface and the outer peripheral wall surface and comprising an outer end and an inner end, the outer end being sealingly sliding with the inner peripheral wall surface, and the inner end being sealingly sliding with the outer peripheral wall surface; the sliding vane 5 being capable of rotating with the ring wall 303 and radially sliding in the ring wall 303.

[0048] The inner cylinder 1 and the outer cylinder 2 are coaxially arranged, the ring wall 303 is eccentrically arranged relative to the inner cylinder 1 and the outer cylinder 2, the outer end of the sliding vane 5 is sealingly sliding with the inner peripheral wall surface, the inner end of the sliding vane 5 is sealingly sliding with the outer peripheral wall surface, and when the ring wall 303 rotates to drive the sliding vane 5 to rotate, the ring wall 303 and the sliding vane 5 periodically change the volume of the inner compression cavity 402 and the outer compression cavity 401 to realize compression of the gas; since the sliding vane 5 is driven to rotate by the ring wall 303 and the inner cylinder 1 and the outer cylinder 2 are fixed, the rotation of the sliding vane 5 is limited between the outer peripheral wall surface of the inner cylinder 1 and the inner peripheral wall surface of the outer cylinder 2, the sliding vane 5 will not be separated from the inner peripheral wall surface of the outer cylinder 2 and the outer peripheral wall surface of the inner cylinder 1 due to factors such as centrifugal force, back pressure change and pressure in the compression cavity, thereby avoiding leakage of the gas (refrigerant) to be compressed and reducing problems, and avoiding vibration and noise caused by collision between the sliding vane 5 and the inner cylinder 1 and the outer cylinder 2. Compared with arranging multiple compression cavities in the axial direction, the present application only arranges the inner compression cavity 402 in the middle of the radial direction, thereby avoiding problems such as increase in the length of the crankshaft and easy variability of the load length of the crankshaft caused by the length of the crankshaft being too long.

[0049] The number of the sliding vanes 5 can be single, two or more; for example, Figures 14-16 As shown, when the number of the sliding vanes 5 is single, two rotations of the rotating shaft 3 complete a complete working cycle, which is equivalent to the working cycle of the rolling piston compressor and is more balanced than the rolling piston compression cavity, and a balance block is not needed; when the number of the sliding vanes 5 is two or more, it is beneficial to improve the displacement of the pump body of the same size, and the working process of the pump body is more balanced in stress, which is beneficial to improve the stability of the work. The inner compression cavity 402 and the outer compression cavity 401 are two independent compression cavities; the inner compression cavity 402 and the outer compression cavity 401 can simultaneously compress the gas to be compressed or alternately compress the gas to be compressed, depending on the circumferential relative position of the inner compression cavity 402 and the outer compression cavity 401.

[0050] Preferably, as shown, Figure 5As shown, the double-cavity rotary compressor further comprises a rotating shaft 3, and the rotating shaft 3 is provided with a center part 301, and the end face of one end of the center part 301 is formed with an annular groove 302, and the side wall of the annular groove 302 constitutes a ring wall 303.

[0051] By arranging the annular groove 302, the ring wall 303 is formed by the side wall of the annular groove 302. On the one hand, the rotation of the rotating shaft 3 can well drive the rotation of the ring wall 303 through the center part 301. On the other hand, by making the ring wall 303 part of the center part 301, the rigidity and strength of the ring wall 303 can be improved, which is beneficial to the high-speed rotation of the ring wall 303.

[0052] Preferably, as shown in the drawings, Figure 5 As shown, the annular groove 302 has a bottom wall 304; the sliding vane 5 further comprises a guide part 501 in the axial direction of the inner cylinder 1, and the inner end of the guide part 501 protrudes in the radial direction; the center part 301 is provided with a sliding groove 305, the sliding groove 305 penetrates the ring wall 303, the sliding vane 5 is located in the sliding groove 305, and the guide part 501 is opposite to the bottom wall 304 in the axial direction.

[0053] The inner end of the guide part 501 of the sliding vane 5 protrudes in the radial direction, which prolongs the matching distance of the center part 301 in the radial direction. The guide part 501 opposite to the bottom wall 304 can improve the guiding effect of the sliding groove 305 on the guide part 501, which is beneficial to the smooth sliding of the sliding vane 5 in the radial direction and avoids the jamming of the sliding vane 5 in the sliding groove 305.

[0054] Preferably, as shown in the drawings, Figure 1 and Figure 4 As shown, the double-cavity rotary compressor further comprises an upper flange 6, the upper flange 6 has an upper matching surface facing the outer cylinder 2, and the upper matching surface is provided with an oil groove 601; and one end of each sliding groove 305 facing the axis of the rotating shaft 3 is in communication with the oil groove 601.

[0055] When the sliding vane 5 slides in the sliding groove 305, the space size of the tail part (one end close to the axis of the rotating shaft 3) of the sliding groove 305 is in a continuous change; the sliding grooves 305 are communicated through the oil groove 601, and the gas in the tail part of the sliding groove 305 flows relative to each other when the sliding vane 5 slides, which reduces the gas resistance of the sliding vane 5 in the sliding groove 305 and reduces the power consumption.

[0056] Preferably, as shown in the drawings, Figure 2 and Figure 3 As shown, the double-cavity rotary compressor further comprises a lower flange 7, and the inner cylinder 1 is arranged on the lower flange 7; the lower flange 7 is provided with a first through hole axially penetrating the inner cylinder 1 and the lower flange 7; the upper flange 6 is provided with a second through hole penetrating the upper flange 6; the first through hole and the second through hole are coaxial and are eccentric relative to the inner cylinder 1; one end of the rotating shaft 3 is arranged in the first through hole, and the other end is arranged in the second through hole.

[0057] The inner cylinder 1 is mounted on the lower flange 7, which helps to reduce the number of parts, simplify the overall structure, and reduce production costs. At the same time, the more compact arrangement in the axial direction helps to reduce the length of the rotating shaft 3, which in turn helps to reduce the deflection of the rotating shaft 3. The two ends of the rotating shaft 3 pass through the upper flange 6 and the lower flange 7 respectively. The upper flange 6 and the lower flange 7 provide radial support for the rotating shaft 3, reducing the deflection of the rotating shaft 3 in the length direction, making the output torque of the rotating shaft 3 stable, which is conducive to the high-speed rotation of the rotating shaft 3.

[0058] Preferred, such as Figure 5 As shown, the axial depth of the annular groove 302 is h1, and the axial height of the central part 301 is h, so 0.2h≤h1≤0.6h; the radius of the inner annular surface 3031 is r1, and the radius of the outer annular surface 3032 is r2, so 0.4h≤(r2-r1)≤0.8h.

[0059] By ensuring that 0.2h≤h1≤0.6h and 0.4h≤(r2-r1)≤0.8h, the size of the inner compression cavity 402 is guaranteed, as well as the strength of the rotating shaft 3, especially the strength and rigidity of the central part 301.

[0060] Preferred, such as Figures 7-16 As shown, a roller 8 is fitted on the outer peripheral wall of the inner cylinder 1; when the slide 5 rotates, the inner end of the slide 5 can drive the roller 8 to rotate.

[0061] The rotation of the vane 5 drives the roller 8 to rotate, which changes the sliding friction between the vane 5 and the outer peripheral wall of the inner cylinder 1 into rolling friction between the roller 8 and the outer peripheral wall of the inner cylinder 1. This reduces power consumption and wear on the vane 5. The reduced wear on the vane 5 helps to ensure the sealing of the compression chamber and improves the service life of the dual-chamber rotor compressor.

[0062] Preferred, such as Figure 7 As shown, the radius of the inner circumferential wall of the outer cylinder 2 is R1, the radius of the outer arc surface of the roller 8 is R2, the outer end face of the slide 5 is an arc surface with a diameter d1=R1-R2; the inner end face of the slide 5 is an arc surface with a diameter d2=R1-R2.

[0063] By designing the diameters of the outer end face and the inner end face of the slide vane 5 to be R1-R2, it is beneficial to improve the sealing performance between the slide vane 5 and the inner circumferential wall of the outer cylinder 2, and also to improve the sealing performance between the slide vane 5 and the outer arc surface of the roller 8.

[0064] Preferred, such as Figure 3 As shown, the air inlet 701 and exhaust port 702 of the dual-chamber rotary compressor are both located on the lower flange 7.

[0065] Since the vane 5 needs to rotate relative to the outer cylinder 2, the outer end face of the vane 5 needs to slide in a sealed manner with the inner circumferential wall of the outer cylinder 2. Setting the inlet port 701 and the exhaust port 702 on the lower flange 7, compared to setting them on the outer cylinder 2, avoids the phenomenon of high friction and uneven force when the vane 5 passes through the inlet port 701 and the exhaust port 702; this helps ensure the working life of the vane 5 and the lifespan of the dual-chamber rotor compressor. The inlet port 701 and the exhaust port 702 of the inner compression chamber 402 and the outer compression chamber 401 are set independently.

[0066] On the other hand, the present invention also provides an air conditioner including the above-described dual-chamber rotary compressor.

[0067] The working process of a dual-chamber rotary compressor is described below; for ease of explanation, as follows: Figures 8-13 As shown, double slider 5 is set. Figure 8 Based on the position of the middle slide 5, the ring wall 303 rotates clockwise. The cavity behind the slide 5 is described as the compression cavity in the direction of rotation of the ring wall 303.

[0068] Figure 8 In the middle, the inner compression chamber 402 and the outer compression chamber 401 have no refrigerant, and the annular wall 303 rotates 90° to... Figure 9 The location shown is from Figures 8 to 9 As the sliding vane 5 rotates, the volumes of both the outer compression chamber 401 and the inner compression chamber 402 increase, allowing refrigerant to enter both chambers. Figures 9 to 10 The inner compression chamber 402 and the outer compression chamber 401 continue to expand, and refrigerant continues to enter; from Figures 10 to 11 The inner compression chamber 402 and the outer compression chamber 401 continue to increase in size. Figure 11 As shown in the position of the slider 5, the volumes of the inner compression chamber 402 and the outer compression chamber 401 reach their maximum; the annular wall 303 continues to rotate clockwise, from... Figure 11 Rotate to Figure 12 The volumes of the inner compression chamber 402 and the outer compression chamber 401 begin to decrease, and the refrigerant begins to be compressed; from Figures 12 to 13 The refrigerant is further compressed. Whether the refrigerant will be compressed to this point depends on the required amount of compression, for example, in... Figure 12 When in position, vent 702 opens, refrigerant is discharged, and there is no... Figure 13 At this step; the annular wall 303 continues to rotate from Figures 13 to 8 Complete the loop.

[0069] The above merely describes preferred embodiments of the present application and is not used to limit the present application, and any modification, equivalent replacement and improvement made within the spirit and principle of the present application shall be included in the protection scope of the present application. The above merely describes preferred embodiments of the present application and is not used to limit the present application, and any modification, equivalent replacement and improvement made within the spirit and principle of the present application shall be included in the protection scope of the present application.

Claims

1. A dual-cavity rotary compressor, characterized by, The application relates to a double-cavity rotary compressor, which comprises the following parts: an inner cylinder (1) with an outer peripheral wall surface; an outer cylinder (2) with an inner peripheral wall surface, which is coaxially sleeved outside the inner cylinder (1); a ring wall (303) which is sleeved outside the inner cylinder (1) and located inside the outer cylinder (2), wherein the ring wall (303) comprises an inner ring surface (3031) and an outer ring surface (3032); the inner peripheral wall surface is tangent to the outer ring surface (3032) and an outer compression cavity (401) is formed between the inner peripheral wall surface and the outer ring surface (3032); the inner ring surface (3031) is tangent to the outer peripheral wall surface and an inner compression cavity (402) is formed between the outer peripheral wall surface and the inner ring surface (3031); a sliding sheet (5) which is arranged between the inner peripheral wall surface and the outer peripheral wall surface and passes through the ring wall (303), wherein the sliding sheet (5) comprises an outer end and an inner end, the outer end is in sealed sliding contact with the inner peripheral wall surface, and the inner end is in sealed sliding contact with the outer peripheral wall surface; the sliding sheet (5) can rotate with the ring wall (303) and can slide radially in the ring wall (303); the double-cavity rotary compressor further comprises a rotating shaft (3), the rotating shaft (3) is provided with a central part (301), the central part (301) is provided with a sliding groove (305), the sliding groove (305) passes through the ring wall (303), and the sliding sheet (5) is located in the sliding groove (305); the double-cavity rotary compressor further comprises an upper flange (6), the upper flange (6) has an upper matching surface which faces the outer cylinder (2), and the upper matching surface is provided with an oil groove (601); one end of each of the sliding grooves (305) which faces the axis of the rotating shaft (3) is in communication with the oil groove (601); the double-cavity rotary compressor further comprises a lower flange (7), an air inlet hole (701) and an air outlet hole (702) of the double-cavity rotary compressor are arranged on the lower flange (7), and the air inlet hole (701) and the air outlet hole (702) are arranged correspondingly for the outer compression cavity (401) and the inner compression cavity (402).

2. The dual-cavity rotary compressor of claim 1, wherein, One end of the central part (301) is provided with an annular groove (302), and a side wall of the annular groove (302) forms the ring wall (303).

3. The dual-cavity rotary compressor of claim 2, wherein, The annular groove (302) has a bottom wall (304); the sliding sheet (5) further comprises a guide part (501) in the axial direction of the inner cylinder (1), and the guide part (501) protrudes the inner end in the radial direction; the guide part (501) is opposite to the bottom wall (304) in the axial direction.

4. The dual-cavity rotary compressor of claim 3, wherein The inner cylinder (1) is arranged on the lower flange (7), the lower flange (7) is provided with a first through hole which axially penetrates the inner cylinder (1) and the lower flange (7), the upper flange (6) is provided with a second through hole which penetrates the upper flange (6); the first through hole and the second through hole are coaxial and are eccentrically arranged relative to the inner cylinder (1); one end of the rotating shaft (3) is arranged in the first through hole, and the other end is arranged in the second through hole.

5. The dual lumen rotary compressor of claim 2, wherein, An axial depth of the annular groove (302) is h1, an axial height of the center part (301) is h, then 0.2h≤h1≤0.6h; a radius of the inner annular surface (3031) is r1, a radius of the outer annular surface (3032) is r2, then, 0.4h≤r2-r1≤0.8h.

6. The dual lumen rotary compressor of claim 4, wherein, A roller (8) is sleeved on an outer peripheral wall surface of the inner cylinder (1); when the sliding vane (5) rotates, the inner end of the sliding vane (5) can drive the roller (8) to rotate.

7. The dual-cavity rotary compressor of claim 6, wherein A radius of an inner peripheral wall surface of the outer cylinder (2) is R1, a radius of an outer circular surface of the roller (8) is R2, an outer end surface of the sliding vane (5) is a circular surface, and a diameter d1=R1-R2; an inner end surface of the sliding vane (5) is a circular surface, and a diameter d2=R1-R2.

8. An air conditioner characterized by comprising: A double-cavity rotary compressor comprising the double-cavity rotary compressor according to any one of claims 1-7.

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