Rotary compressor and refrigeration cycle system

Abstract

The present invention discloses a rotary compressor and a refrigeration cycle system, wherein the rotary compressor comprises a casing, a motor and a compression assembly, wherein the motor is arranged in the casing and has a crankshaft, the compression assembly is arranged in the casing and driven by the crankshaft, the compression assembly comprises a cylinder, a piston, a first sealing ring, a second sealing ring and a vane, the cylinder comprises a cylinder chamber and a vane groove, the vane can reciprocate in the vane groove and the front end of the vane can abut against the outer peripheral surface of the piston, the piston comprises a first piston and a second piston, at least one end face of the first piston in the axial direction of the crankshaft is provided with a first annular groove, at least one end face of the second piston in the axial direction of the crankshaft is provided with a second annular groove, the first sealing ring is arranged in the first annular groove, and the second sealing ring is arranged in the second annular groove. The rotary compressor of the present invention can reduce the amount of high-pressure gas leaking from the piston end face to the compression chamber, avoid the reduction of refrigeration capacity, and improve compression reliability.

Description

Technical Field

[0001] The present invention belongs to the technical field of compressors, and in particular, relates to a rotary compressor and a refrigeration cycle system. Background Art

[0002] A rotary compressor generally includes a casing, a motor assembly and a compression assembly, wherein a vane of the compression assembly reciprocates in a vane groove of a cylinder, a spring is provided at the rear end of the vane, and the spring presses the vane, whereby the front end of the vane abuts against the outer circumferential surface of the piston in the compression chamber. Summary of the invention

[0003] The present invention is based on the inventor's discovery and understanding of the following facts and problems:

[0004] In the related art, most household air conditioners use a double-cylinder rotary compressor with a variable frequency motor.

[0005] After research, the inventor found that the high-pressure gas on the inner periphery of the piston is easy to leak from the two end faces of the piston into the compression chamber. Compared with the single-cylinder rotary compressor, the double-cylinder rotary compressor has two pistons, and the two pistons have four piston end faces. The high-pressure gas is easy to leak from the four piston end faces into the compression chamber, resulting in a reduction in cooling capacity.

[0006] To this end, one aspect of the present invention provides a rotary compressor that can reduce the amount of high-pressure gas leaking from the piston end face to the compression chamber, avoid a reduction in refrigeration capacity, and improve compression reliability.

[0007] Another aspect of the present invention provides a refrigeration cycle system.

[0008] The rotary compressor according to the embodiment of the first aspect of the present invention comprises: a casing having lubricating oil therein; a motor, the motor being arranged in the casing and having a crankshaft, the crankshaft comprising a first eccentric portion, a second eccentric portion and a connecting portion connected between the first eccentric portion and the second eccentric portion; and a compression assembly, the compression assembly being arranged in the casing and driven by the crankshaft, the compression assembly comprising: a cylinder, the cylinder comprising a first cylinder and a second cylinder, the first cylinder having a first cylinder chamber and a first vane groove, the second cylinder having a second cylinder chamber and a second vane groove, the first cylinder and the second cylinder being arranged at intervals in the axial direction of the crankshaft, and a partition being arranged between the first cylinder and the second cylinder, the partition being provided with a central cavity penetrating the partition along the axial direction of the crankshaft, the connecting portion being fitted in the central cavity; a piston, the piston comprising a first piston and a second piston, the first eccentric portion The eccentric portion is fitted in the first piston to drive the first piston to rotate eccentrically in the first cylinder chamber, and the second eccentric portion is fitted in the second piston to drive the second piston to rotate eccentrically in the second cylinder chamber, at least one of the two end faces of the first piston in the axial direction of the crankshaft is provided with a first annular groove, and at least one of the two end faces of the second piston in the axial direction of the crankshaft is provided with a second annular groove; a first sealing ring and a second sealing ring, the first sealing ring is arranged in the first annular groove, and the second sealing ring is arranged in the second annular groove; a sliding plate, the sliding plate includes a first sliding plate and a second sliding plate, the first sliding plate can reciprocate in the first sliding plate groove, the front end portion of the first sliding plate can abut against the outer peripheral surface of the first piston, the second sliding plate can reciprocate in the second sliding plate groove, and the front end portion of the second sliding plate can abut against the outer peripheral surface of the second piston.

[0009] According to the rotary compressor of the embodiment of the present invention, a first annular groove is provided on at least one of the two end faces of the first piston on the axial direction of the crankshaft, a second annular groove is provided on at least one of the two end faces of the second piston on the axial direction of the crankshaft, and a first sealing ring is provided in the first annular groove, and a second sealing ring is provided in the second annular groove. The sealing ring can be used to improve the sealing effect between the end face of the piston and the end face of a structural member (such as a partition) that cooperates with it, reduce the amount of high-pressure gas leaking from the end face of the piston to the compression chamber, avoid a reduction in refrigeration capacity, and improve compression reliability.

[0010] In some embodiments, the first piston is provided with the first annular groove on one end face adjacent to the partition, the first sealing ring is provided in the first annular groove, the first sealing ring is in contact with the end face of the partition adjacent to the first piston and is slidable relative to the partition, and the second piston is provided with the second annular groove on one end face adjacent to the partition, the second sealing ring is provided in the second annular groove, the second sealing ring is in contact with the end face of the partition adjacent to the second piston and is slidable relative to the partition.

[0011] In some embodiments, the compression assembly further includes a first bearing and a second bearing, the first bearing being disposed on a side of the first cylinder away from the second cylinder, the second bearing being disposed on a side of the second cylinder away from the first cylinder, and the crankshaft being rotatably supported by the first bearing and the second bearing.

[0012] In some embodiments, the first piston is provided with the first annular groove on one end face adjacent to the first bearing, the first sealing ring is provided in the first annular groove, the first sealing ring is in contact with the first bearing and can slide relative to the first bearing, and the second piston is provided with the second annular groove on one end face adjacent to the second bearing, the second sealing ring is provided in the second annular groove, the second sealing ring is in contact with the second bearing and can slide relative to the second bearing.

[0013] In some embodiments, each of the first piston and the second piston includes a first section and a second section arranged opposite to each other in the axial direction of the crankshaft and a middle section located between the first section and the second section, the inner diameter of the middle section is smaller than the inner diameter of the first section, and the inner diameter of the middle section is smaller than the inner diameter of the second section.

[0014] In some embodiments, the diameter of the central cavity is smaller than the inner diameter of the first segment or the second segment and is greater than or equal to the inner diameter of the middle segment.

[0015] In some embodiments, a gap is provided between the first sealing ring and a bottom surface of the first annular groove, and a gap is provided between the second sealing ring and the second annular groove.

[0016] In some embodiments, the first annular groove is spaced apart from the central cavity in a radial direction of the central cavity, and the second annular groove is spaced apart from the central cavity in a radial direction of the central cavity.

[0017] In some embodiments, the first sealing ring is an elastic member, and / or the second sealing ring is an elastic member.

[0018] In some embodiments, one of the first cylinder and the second cylinder may be switched between a cylinder deactivated state and a cylinder deactivated state to control the capacity of the compression assembly.

[0019] A refrigeration cycle system according to an embodiment of another aspect of the present invention includes a compressor, a condenser, an expansion valve, an evaporator and a liquid accumulator, wherein the compressor is a rotary compressor as described in any one of the above.

[0020] According to the refrigeration cycle system of an embodiment of the present invention, the rotary compressor thereof can reduce the amount of high-pressure gas leaking from the piston end face to the compression chamber and avoid a reduction in refrigeration capacity by providing an annular groove on the end face of the piston and installing a sealing ring in the annular groove. BRIEF DESCRIPTION OF THE DRAWINGS

[0021] Figure 1 is a schematic diagram of a refrigeration cycle system according to an embodiment of the present invention, which shows a longitudinal section of a rotary compressor according to an embodiment of the present invention.

[0022] Figure 2 is a cross-sectional view of a rotary compressor according to an embodiment of the present invention.

[0023] Figure 3 4 is a partial structural cross-sectional view of a rotary compressor according to an example of the present invention.

[0024] Figure 4 is a schematic cross-sectional view of a rotary compressor according to an embodiment of the present invention.

[0025] Reference numerals:

[0026] Rotary compressor 1, casing 2, motor 4, crankshaft 30, first eccentric portion 30A, second eccentric portion 30B, connecting portion 30C, compression assembly 5, first cylinder 10, first cylinder chamber 10A, second cylinder 20, second cylinder chamber 20B, partition 12, central cavity 12a, first piston 15, first through hole 15b, second through hole 15d, first annular groove 15e, first sealing ring 18, second piston 25, second annular groove 25e, second sealing ring 18a, sliding surface 15c, first vane 13, first vane groove 13a, second vane 23, exhaust pipe 3, first bearing 26, first exhaust hole 26a, second bearing 28, second exhaust hole 28b, first air intake pipe 6a, second air intake pipe 6b, lubricating oil 8, first muffler 27, second muffler 29, condenser 50, expansion valve 51, evaporator 52, liquid reservoir 40. DETAILED DESCRIPTION

[0027] Embodiments of the present invention are described in detail below, and examples of the embodiments are shown in the accompanying drawings. The embodiments described below with reference to the accompanying drawings are exemplary and intended to be used to explain the present invention, but should not be understood as limiting the present invention.

[0028] The following describes a rotary compressor and a refrigeration cycle system according to embodiments of the present invention with reference to the accompanying drawings.

[0029] like Figure 1-Figure 4 As shown, the rotary compressor 1 according to the embodiment of the first aspect of the present invention comprises a casing 2, a motor 4 and a compression assembly 5. The motor 4 and the compression assembly 5 are both arranged in the casing 2, and the bottom of the casing 2 has lubricating oil 8.

[0030] The motor 4 has a crankshaft 30, and the crankshaft 30 includes a first eccentric portion 30A, a second eccentric portion 30B, and a connecting portion 30C connected between the first eccentric portion 30A and the second eccentric portion 30B. Figure 1 and Figure 2 As shown, the housing 2 has an installation cavity, the motor 4 is arranged in the installation cavity, the motor 4 has a crankshaft 30 extending in the up and down directions, the outer peripheral wall of the crankshaft 30 is provided with a first eccentric portion 30A and a second eccentric portion 30B, the first eccentric portion 30A is located above the second eccentric portion 30B, and the first eccentric portion 30A and the second eccentric portion 30B are connected by a connecting portion 30C.

[0031] The compression assembly 5 is driven by a crankshaft 30, as Figure 1 As shown, the compression assembly 5 is fixed on the inner circumference of the casing 2. The compression assembly 5 includes a cylinder, a piston, a first sealing ring 18, a second sealing ring 18a and a sliding vane.

[0032] The cylinder includes a first cylinder 10 and a second cylinder 20. The first cylinder 10 has a first cylinder chamber 10A and a first vane groove 13a. The second cylinder 20 has a second cylinder chamber 20B and a second vane groove. The first cylinder 10 and the second cylinder 20 are spaced apart in the axial direction of the crankshaft 30, and a partition plate 12 is provided between the first cylinder 10 and the second cylinder 20. The partition plate 12 is provided with a central cavity 12a that passes through the partition plate 12 along the axial direction of the crankshaft 30, and the connecting portion 30C is fitted in the central cavity 12a.

[0033] In other words, the first cylinder 10 and the second cylinder 20 can be put into operation at the same time to increase the operating efficiency of the compression assembly 5. In order to realize the connection between the crankshaft 30 and the first cylinder 10 and the second cylinder 20, a partition 12 is provided between the first cylinder 10 and the second cylinder 20, and a central cavity 12a is provided on the partition 12. The central cavity 12a is suitable for the crankshaft 30 to pass through, so as to realize the assembly of the crankshaft 30 with the first cylinder 10, the partition 12 and the second cylinder 20. Figure 1As shown, the compression assembly 5 is located below the motor 4, the first cylinder 10 and the second cylinder 20 are separated in the up and down directions in the casing 2, the first cylinder 10 is located above the second cylinder 20, the lower end of the crankshaft 30 passes through the first cylinder 10, the partition 12 and the second cylinder 20 in sequence, and a central cavity 12a that passes through from top to bottom is provided at the position of the partition 12 corresponding to the crankshaft 30, and the intermediate shaft is passed through the central cavity 12a.

[0034] The piston includes a first piston 15 and a second piston 25. The first eccentric portion 30A is fitted in the first piston 15 to drive the first piston 15 to rotate eccentrically in the first cylinder chamber 10A. The second eccentric portion 30B is fitted in the second piston 25 to drive the second piston 25 to rotate eccentrically in the second cylinder chamber 20B. The first piston 15 is provided with a first annular groove 15e on at least one of the two end surfaces in the axial direction of the crankshaft 30. The second piston 25 is provided with a second annular groove 25e on at least one of the two end surfaces in the axial direction of the crankshaft 30. The first sealing ring 18 is arranged in the first annular groove 15e, and the second sealing ring 18a is arranged in the second annular groove 25e.

[0035] like Figure 1 , Figure 2 and Figure 4 As shown, the first eccentric portion 30A is disposed in the first piston 1512 and connected to the inner circumference of the first piston 1512, and the second eccentric portion 30B is disposed in the second piston 2522 and connected to the inner circumference of the second piston 2522. A first annular groove 15e is provided on the upper end surface and the lower end surface of the first piston 15, and a second annular groove 25e is provided on the upper end surface and the lower end surface of the second piston 25.

[0036] like Figure 2 As shown, the upper end face and the lower end face of the first piston 15 are both fitted with the end faces of other structural parts to form sliding surfaces 15c at the upper and lower ends of the first piston 15, and the first sealing ring 18 disposed in the first annular groove 15e can fit with the end face of the structural part that matches the first piston 15 to improve the sealing performance of the sliding surface 15c. For example, the lower end face of the first piston 15 fits with the upper end face of the partition 12, and a first annular groove 15e is formed on the lower end face of the first piston 15, and the lower end face of the first sealing ring 18 disposed in the first annular groove 15e fits with the upper end face of the partition 12.

[0037] The upper end surface and the lower end surface of the second piston 25 are also fitted with the end surfaces of other structural parts to form sliding surfaces 15c at the upper and lower ends of the second piston 25. The second sealing ring 18a disposed in the second annular groove 25e can fit with the end surface of the mechanism matched with the second piston 25 to improve the sealing performance of the sliding surface 15c. For example, the upper end surface of the second piston 25 fits with the lower end surface of the partition 12, the upper end surface of the second piston 25 has a second annular groove 25e, and the upper end surface of the second sealing ring 18a disposed in the second annular groove 25e fits with the lower end surface of the partition 12.

[0038] The sliding vane includes a first sliding vane 13 and a second sliding vane 23. The first sliding vane 13 can reciprocate in the first sliding vane groove 13a, and the front end of the first sliding vane 13 can abut against the outer peripheral surface of the first piston 15. The second sliding vane 23 can reciprocate in the second sliding vane groove, and the front end of the second sliding vane 23 can abut against the outer peripheral surface of the second piston 25.

[0039] like Figure 2 and Figure 4 As shown, the first sliding plate groove 13a extends in the radial direction of the housing 2, and the first sliding plate 13 is away from the end of the first piston 15 (such as Figure 2 The outer end of the first sliding plate 13 in the middle) is received in the first sliding plate groove 13a, and the end of the first sliding plate 13 close to the first piston 15 (such as Figure 2 The inner end of the first sliding plate 13 abuts against the outer peripheral surface of the first piston 15, and a sliding space is provided between the outer end of the first sliding plate 13 and the bottom wall of the first sliding plate groove 13a, so that the first sliding plate 13 can reciprocate in the first sliding plate groove 13a.

[0040] The second sliding plate groove (not shown) extends in the radial direction of the housing 2, and the second sliding plate 23 is away from the end of the second piston 25 (such as Figure 2 The outer end of the second sliding plate 23 in the middle) is received in the second sliding plate groove, and the end of the second sliding plate 23 close to the second piston 25 (such as Figure 2 The inner end of the second sliding plate 23 abuts against the outer circumferential surface of the second piston 25, and a sliding space is provided between the outer end of the second sliding plate 23 and the bottom wall of the second sliding plate groove, so that the second sliding plate 23 can reciprocate in the second sliding plate groove.

[0041] According to the rotary compressor of the embodiment of the present invention, a first annular groove is provided on at least one of the two end faces of the first piston on the axial direction of the crankshaft, a second annular groove is provided on at least one of the two end faces of the second piston on the axial direction of the crankshaft, and a first sealing ring is provided in the first annular groove, and a second sealing ring is provided in the second annular groove. The sealing ring can be used to improve the sealing effect between the end face of the piston and the end face of a structural member (such as a partition) that cooperates with it, reduce the amount of high-pressure gas leaking from the end face of the piston to the compression chamber, avoid a reduction in refrigeration capacity, and improve compression reliability.

[0042] In some embodiments, Figure 2 As shown, the compression assembly 5 also includes a first bearing 26 and a second bearing 28. The first bearing 26 is arranged on a side of the first cylinder 10 away from the second cylinder 20, and the second bearing 28 is arranged on a side of the second cylinder 20 away from the first cylinder 10. The crankshaft 30 is rotatably supported by the first bearing 26 and the second bearing 28.

[0043] like Figure 1 and Figure 2 As shown, the first bearing 26 and the second bearing 28 are both sleeved on the crankshaft 30, the first bearing 26 is connected to the upper surface of the first cylinder 10 to seal the compression chamber of the first cylinder 10, and the second bearing 28 is connected to the lower surface of the second cylinder 20 to seal the compression chamber of the second cylinder 20.

[0044] In some embodiments, Figure 2 As shown, a first annular groove 15 e is formed on an end surface of the first piston 15 adjacent to the first bearing 26 . A first sealing ring 18 is formed in the first annular groove 15 e . The first sealing ring 18 contacts the first bearing 26 and is slidable relative to the first bearing 26 .

[0045] like Figure 2 As shown, the upper end surface of the first piston 15 is provided with a first annular groove 15e, and the upper end surface of the first sealing ring 18 provided in the first annular groove 15e contacts the lower end surface of the first bearing 26. It can be understood that the first piston 15 can slide along the lower end surface of the first bearing 26 relative to the first bearing 26, and during this process, the first sealing ring 18 slides with the first piston 15 and always keeps in contact with the lower end surface of the first bearing 26, so as to reduce the leakage of the high-pressure gas in the first piston 15 during the movement of the first piston 15.

[0046] A second annular groove 25 e is formed on one end surface of the second piston 25 adjacent to the second bearing 28 . A second sealing ring 18 a is disposed in the second annular groove 25 e . The second sealing ring 18 a contacts the second bearing 28 and is slidable relative to the second bearing 28 .

[0047] like Figure 2 As shown, the lower end surface of the second piston 25 is provided with a second annular groove 25e, and the lower end surface of the second sealing ring 18a provided in the second annular groove 25e is in contact with the upper end surface of the second bearing 28. It can be understood that the second piston 25 can slide along the upper end surface of the second bearing 28 relative to the second bearing 28. During this process, the second sealing ring 18a slides with the second piston 25 and always keeps in contact with the upper end surface of the second bearing 28, thereby reducing the leakage of high-pressure gas in the second piston 25 during the movement of the second piston 25.

[0048] In some embodiments, Figure 2 and Figure 3 As shown, each of the first piston 15 and the second piston 25 includes a first section and a second section arranged opposite to each other in the axial direction of the crankshaft 30 and a middle section located between the first section and the second section, the inner diameter of the middle section is smaller than the inner diameter of the first section, and the inner diameter of the middle section is smaller than the inner diameter of the second section.

[0049] like Figure 2 and Figure 3 As shown, taking the first piston 15 as an example, the first section is located above the middle section, and the second section is located below the middle section. The middle section has a first through hole 15b for the crankshaft 30 to pass through, and the first section and the second section both have a second through hole 15d for the crankshaft 30 to pass through, and the inner diameter of the middle section (the inner diameter D2 of the first through hole 15b) is smaller than the inner diameter of the first section or the second section (the inner diameter D3 of the second through hole 15d).

[0050] Furthermore, if Figure 2 As shown, the diameter of the central cavity 12 a is greater than or equal to the inner diameter of the middle section, thereby ensuring that the crankshaft 30 can pass through the central cavity 12 a to achieve the connection between the second cylinder 20 and the crankshaft 30 .

[0051] In addition, the diameter of the central cavity 12a is smaller than the inner diameter of the first section or the second section. Figure 2 As shown, taking the first piston 15 as an example, the second through hole 15d is connected to the central cavity 12a, and the lower end surface of the second section is in contact with the upper end surface of the partition 12. Therefore, by setting the inner diameter D3 of the second through hole to be larger than the diameter D1 of the central cavity, when the first piston moves in a large range in the radial direction of the crankshaft, it is possible to avoid the outer wall of the first piston and the partition from generating a misalignment gap in the radial direction of the crankshaft, thereby preventing the leakage of high-pressure gas in the first piston.

[0052] In some embodiments, Figure 1 As shown, there is a gap between the first sealing ring 18 and the bottom surface of the first annular groove 15e, and there is a gap between the second sealing ring 18a and the second annular groove 25e. Therefore, the pressure difference between the first cylinder chamber or the second cylinder chamber and the gap can press the first sealing ring and the second sealing ring, so that when the first piston and the second piston move at high speed, the first sealing ring can always fit with the partition and the first bearing, and the second sealing ring can always fit with the partition and the second bearing, so as to minimize the sliding gap, thereby improving the reliability of the first sealing ring and the second sealing ring, and preventing the high-pressure gas in the piston from leaking into the compression chamber.

[0053] Furthermore, the first sealing ring 18 is an elastic member, and / or the second sealing ring 18a is an elastic member. In other words, one of the first sealing ring 18 and the second sealing ring 18a is an elastic member, or both of the first sealing ring 18 and the second sealing ring 18a are elastic members. Thus, the first sealing ring and / or the second sealing ring have elastic deformation capability, so that when the first piston and / or the second piston move at high speed, the first sealing ring and / or the second sealing ring can ensure the sealing between the first piston and / or the second piston and other structural members (such as the first bearing, the second bearing and the partition). For example, when the partition 12 vibrates up and down, the first sealing ring 18 and the second sealing ring 18a will not separate from the surface of the partition 12 under the action of their elastic force.

[0054] In some embodiments, Figure 2 As shown, the first annular groove 15e is spaced apart from the central cavity 12a in the radial direction of the central cavity 12a, and the second annular groove 25e is spaced apart from the central cavity 12a in the radial direction of the central cavity 12a. Thus, neither the first annular groove nor the second annular groove is connected to the central cavity, thereby preventing the high-pressure gas in the central cavity from leaking into the compression cavity through the first annular groove or the second annular groove, and the sealing ring disposed in the annular groove does not contact the outer periphery of the central cavity, thereby preventing the sealing ring from being damaged.

[0055] In some embodiments, one of the first cylinder 10 and the second cylinder 20 can be switched between a cylinder deactivation state and a cylinder deactivation release state to control the capacity of the compression assembly 5. In other words, the first cylinder 10 and the second cylinder 20 can work at the same time, or one cylinder can work while the other cylinder does not work, so as to reasonably save power and maintain environmental comfort.

[0056] According to another aspect of the present invention, a refrigeration cycle system includes a compressor, a condenser 50, an expansion valve 51, an evaporator 52, and a liquid storage tank 40. The compressor is a rotary compressor 1 according to an embodiment of the present invention.

[0057] like Figure 1As shown, an exhaust pipe 3 is provided on the top of the casing 2, a first exhaust hole 26a which can be opened and closed by a first exhaust valve is provided on the first bearing 26, and a second exhaust hole 28b which can be opened and closed by a second exhaust valve is provided on the second bearing 28. The high-pressure gas is suitable for being discharged from the exhaust pipe 3 into the condenser 50 and becoming a liquid refrigerant in the condenser 50. The low-pressure refrigerant passing through the expansion valve 51 becomes a low-pressure gas in the evaporator 52 and flows into the liquid reservoir 40. The low-pressure gas sucked in from the first intake pipe connected to the liquid reservoir 40 is compressed into a high-pressure gas in the first cylinder 10, and the low-pressure gas sucked in from the second intake pipe 6b connected to the liquid reservoir 40 is compressed into a high-pressure gas in the second cylinder 20. The high-pressure gas discharged through the first exhaust hole 26a opened in the first bearing 26 and the second row of holes opened in the second bearing 28 is discharged to the interior of the casing 2 through the first muffler 27 and the second muffler 29.

[0058] Reference below Figure 1-Figure 4 A rotary compressor according to a specific example of the present invention is described.

[0059] like Figure 1-Figure 4 As shown, the rotary compressor includes a housing 2 , a crankshaft 30 , a motor 4 and a compression assembly 5 .

[0060] The motor 4, the crankshaft 30 and the compression assembly 5 are all arranged in the housing 2. The motor 4 is located above the compression assembly 5, and the motor 4 has a crankshaft 30 extending in the up-down direction, and the crankshaft 30 is connected to the compression assembly 5 to drive the compression assembly 5 to operate. The crankshaft 30 includes a first eccentric portion A and a second eccentric portion B spaced apart in the up-down direction, and a connecting portion 30C connected between the first eccentric portion A and the second eccentric portion B.

[0061] The compression assembly 5 includes a first cylinder 10 , a second cylinder 20 , a first piston 15 , a second piston 25 , a first sealing ring 18 , a second sealing ring 18 a , a first sliding vane 13 , a second sliding vane 23 , a first bearing 26 , a second bearing 28 and a partition plate 12 .

[0062] The first cylinder 10 and the second cylinder 20 are arranged at intervals in the up and down directions, and the partition 12 is located between the first cylinder 10 and the second cylinder 20. The partition 12 has a central cavity 12a for the crankshaft 30 to pass through, and the connecting portion 30C is fitted in the central cavity 12a. The first bearing 26 is connected to the upper surface of the first cylinder 10, and the second bearing 28 is connected to the lower surface of the second cylinder 20.

[0063] The first cylinder 10 includes a first cylinder chamber 10A and a first sliding vane groove 13a. The first piston 15 is located in the first cylinder chamber 10A. The first eccentric portion A is fitted in the first piston 15 to drive the first piston 15 to rotate eccentrically. The upper end surface and the lower end surface of the first piston 15 are both provided with a first annular groove 15e. The inner circumferential surface of the first annular groove 15e is spaced apart from the inner circumferential surface of the central cavity 12a in the radial direction of the crankshaft 30. The first sealing ring 18 is fitted in the first annular groove 15e. There is a gap between the first sealing ring 18 and the bottom wall of the first annular groove 15e. The first sealing ring 18 located on the upper end surface of the first piston 15 is in contact with the lower surface of the first bearing 26. The second sealing ring 18a located on the lower end surface of the first piston 15 is in contact with the upper surface of the partition 12.

[0064] The first piston 15 includes a first section, a second section and a middle section between the first section and the second section. The inner diameter of the middle section is smaller than the inner diameter of the first section or the second section, and the inner diameter of the middle section is greater than or equal to the diameter of the central cavity 12a.

[0065] The first slide groove 13a extends radially along the housing 2, the outer end of the first slide 13 is accommodated in the first slide groove 13, the inner end of the first slide 13 abuts against the outer peripheral surface of the first piston 15, and there is a slidable space between the outer end of the first slide 13 and the bottom wall of the first slide groove 13a.

[0066] The second cylinder 20 includes a second cylinder chamber 20B and a second sliding vane groove. The second piston 25 is arranged in the second cylinder chamber 20B. The second eccentric portion B is fitted in the second piston 25 to drive the second piston 25 to rotate eccentrically. The upper end surface and the lower end surface of the second piston 25 are both provided with a second annular groove 25e. The inner circumferential surface of the second annular groove 25e is spaced apart from the inner circumferential surface of the central cavity 12a in the radial direction of the crankshaft 30. The second sealing ring 18a is fitted in the second annular groove 25e. There is a gap between the second sealing ring 18a and the bottom wall of the second annular groove 25e. The second sealing ring 18a located on the upper end surface of the second piston 25 is in contact with the lower surface of the partition 12, and the second sealing ring 18a located on the lower end surface of the second piston 25 is in contact with the upper surface of the second bearing 28.

[0067] The second piston 25 includes a first section, a second section and a middle section between the first section and the second section. The inner diameter of the middle section is smaller than the inner diameter of the first section or the second section, and is greater than or equal to the diameter of the central cavity 12a.

[0068] The second slide groove (not shown) extends radially along the casing 2, and the outer end of the second slide 23 is accommodated in the second slide groove. The inner end of the second slide 23 abuts against the outer peripheral surface of the second piston 25. There is a sliding space between the outer end of the second slide 23 and the bottom wall of the second slide groove, so that the second slide 23 can reciprocate in the second slide groove.

[0069] In the description of the present invention, it is to be understood that the terms “center”, “longitudinal”, “lateral”, “length”, “width”, “thickness”, “up”, “down”, “front”, “back”, “left”, “right”, “vertical”, “horizontal”, “top”, “bottom”, “inside”, “outside”, “clockwise”, “counterclockwise”, “axial”, “radial”, “circumferential”, etc., indicating orientations or positional relationships based on the orientations or positional relationships shown in the accompanying drawings, are only for the convenience of describing the present invention and simplifying the description, and do not indicate or imply that the referred device or element must have a specific orientation, be constructed and operated in a specific orientation, and therefore should not be understood as limiting the present invention.

[0070] In addition, the terms "first" and "second" are used for descriptive purposes only and should not be understood as indicating or implying relative importance or implicitly indicating the number of the indicated technical features. Therefore, the features defined as "first" and "second" may explicitly or implicitly include at least one of the features. In the description of the present invention, the meaning of "plurality" is at least two, such as two, three, etc., unless otherwise clearly and specifically defined.

[0071] In the present invention, unless otherwise clearly specified and limited, the terms "installed", "connected", "connected", "fixed" and the like should be understood in a broad sense, for example, it can be a fixed connection, a detachable connection, or an integral one; it can be a mechanical connection, an electrical connection, or communication with each other; it can be a direct connection, or an indirect connection through an intermediate medium, it can be the internal connection of two elements or the interaction relationship between two elements, unless otherwise clearly defined. For ordinary technicians in this field, the specific meanings of the above terms in the present invention can be understood according to specific circumstances.

[0072] In the present invention, unless otherwise clearly specified and limited, a first feature being "above" or "below" a second feature may mean that the first and second features are in direct contact, or the first and second features are in indirect contact through an intermediate medium. Moreover, a first feature being "above", "above" or "above" a second feature may mean that the first feature is directly above or obliquely above the second feature, or simply means that the first feature is higher in level than the second feature. A first feature being "below", "below" or "below" a second feature may mean that the first feature is directly below or obliquely below the second feature, or simply means that the first feature is lower in level than the second feature.

[0073] In the present invention, the terms "one embodiment", "some embodiments", "examples", "specific examples", or "some examples" etc. mean that the specific features, structures, materials or characteristics described in conjunction with the embodiment or example are included in at least one embodiment or example of the present invention. In this specification, the schematic representations of the above terms do not necessarily refer to the same embodiment or example. Moreover, the described specific features, structures, materials or characteristics may be combined in any one or more embodiments or examples in a suitable manner. In addition, those skilled in the art may combine and combine the different embodiments or examples described in this specification and the features of the different embodiments or examples, without contradiction.

[0074] Although the embodiments of the present invention have been shown and described above, it is to be understood that the above embodiments are exemplary and are not to be construed as limitations of the present invention. A person skilled in the art may change, modify, replace and vary the above embodiments within the scope of the present invention.

Claims

1. A rotary compressor, characterized in that: include: a casing, wherein lubricating oil is contained in the casing; A motor, the motor is arranged in the housing and has a crankshaft, the crankshaft includes a first eccentric portion, a second eccentric portion and a connecting portion connected between the first eccentric portion and the second eccentric portion; and A compression assembly, the compression assembly is arranged in the casing and driven by the crankshaft, the compression assembly comprising: A cylinder, the cylinder comprising a first cylinder and a second cylinder, the first cylinder having a first cylinder chamber and a first vane groove, the second cylinder having a second cylinder chamber and a second vane groove, the first cylinder and the second cylinder being spaced apart in the axial direction of the crankshaft, and a partition plate being provided between the first cylinder and the second cylinder, the partition plate being provided with a central cavity penetrating the partition plate along the axial direction of the crankshaft, and the connecting portion being fitted in the central cavity; A piston, the piston comprising a first piston and a second piston, the first eccentric portion being fitted in the first piston to drive the first piston to rotate eccentrically in the first cylinder chamber, the second eccentric portion being fitted in the second piston to drive the second piston to rotate eccentrically in the second cylinder chamber, the first piston being provided with a first annular groove on at least one of the two end surfaces in the axial direction of the crankshaft, and the second piston being provided with a second annular groove on at least one of the two end surfaces in the axial direction of the crankshaft; A first sealing ring and a second sealing ring, wherein the first sealing ring is disposed in the first annular groove, and the second sealing ring is disposed in the second annular groove, a gap is provided between the first sealing ring and a bottom surface of the first annular groove, and a gap is provided between the second sealing ring and the second annular groove, the first annular groove is spaced apart from the central cavity in a radial direction of the central cavity, and the second annular groove is spaced apart from the central cavity in a radial direction of the central cavity; The slide comprises a first slide and a second slide, the first slide can reciprocate in the first slide groove, the front end of the first slide can abut against the outer peripheral surface of the first piston, the second slide can reciprocate in the second slide groove, the front end of the second slide can abut against the outer peripheral surface of the second piston.

2. The rotary compressor according to claim 1, characterized in that: The first piston is provided with the first annular groove on one end surface adjacent to the partition plate, and the first sealing ring is provided in the first annular groove. The first sealing ring contacts the end surface of the partition plate adjacent to the first piston and is slidable relative to the partition plate. The second annular groove is provided on one end surface of the second piston adjacent to the partition plate. The second sealing ring is provided in the second annular groove. The second sealing ring contacts the end surface of the partition plate adjacent to the second piston and is slidable relative to the partition plate.

3. The rotary compressor according to claim 1, characterized in that: The compression assembly further includes a first bearing and a second bearing, wherein the first bearing is disposed on a side of the first cylinder away from the second cylinder, and the second bearing is disposed on a side of the second cylinder away from the first cylinder, and the crankshaft is rotatably supported by the first bearing and the second bearing.

4. The rotary compressor according to claim 3, characterized in that: The first piston is provided with a first annular groove on one end surface adjacent to the first bearing. The first sealing ring is provided in the first annular groove. The first sealing ring contacts the first bearing and is slidable relative to the first bearing. The second annular groove is provided on an end surface of the second piston adjacent to the second bearing. The second sealing ring is provided in the second annular groove. The second sealing ring contacts the second bearing and is slidable relative to the second bearing.

5. The rotary compressor according to claim 1, characterized in that: Each of the first piston and the second piston includes a first section and a second section arranged opposite to each other in the axial direction of the crankshaft and an intermediate section located between the first section and the second section, wherein the inner diameter of the intermediate section is smaller than the inner diameter of the first section, and the inner diameter of the intermediate section is smaller than the inner diameter of the second section.

6. The rotary compressor according to claim 5, characterized in that: The diameter of the central cavity is smaller than the inner diameter of the first section or the second section and is greater than or equal to the inner diameter of the middle section.

7. The rotary compressor according to any one of claims 1 to 6, characterized in that: The first sealing ring is an elastic member, and / or the second sealing ring is an elastic member.

8. The rotary compressor according to any one of claims 1 to 6, characterized in that: One of the first cylinder and the second cylinder may be switched between a cylinder deactivation state and a cylinder deactivation release state to control a capacity of the compression assembly.

9. A refrigeration cycle system, characterized in that: The invention comprises a compressor, a condenser, an expansion valve, an evaporator and a liquid storage device, wherein the compressor is a rotary compressor according to any one of claims 1 to 8.

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