Compressor and refrigeration cycle device

Abstract

The application discloses a compressor and a refrigeration cycle device, and the compressor comprises a shell and a compression mechanism part, the shell is internally provided with an inner cavity, the shell is provided with a suction port communicated with the inner cavity, the shell is provided with an exhaust pipe, the compression mechanism part is arranged in the inner cavity, and the compression mechanism part comprises a cylinder assembly, the cylinder assembly is provided with a compression cavity, the compression cavity is provided with an air inlet and an exhaust port, the air inlet is communicated with the inner cavity, a middle partition plate is arranged, the middle partition plate is provided with a first exhaust passage, each exhaust port is communicated with the first exhaust passage, at least one cylinder assembly is provided with a second exhaust passage, the second exhaust passage is communicated with the first exhaust passage and the exhaust pipe. Compared with the technical scheme that the inner cavity of the shell is high pressure, the compressor effectively reduces the enclosed amount of refrigerant in the refrigeration cycle device, is favorable for improving the safety of the refrigeration cycle device, and the exhaust path of the compression mechanism part is shorter, so that the compression mechanism part is convenient for exhausting.

Description

TECHNICAL FIELD

[0001] The present application relates to the field of compressor device, in particular to a compressor and a refrigeration cycle device. BACKGROUND

[0002] In recent years, more and more air conditioners use refrigerant R290 from the point of view of improving global warming. However, since the refrigerant R290 is highly flammable, in order to ensure the safety of the air conditioner, it is necessary to limit the amount of refrigerant sealed into the air conditioner. SUMMARY

[0003] The present application aims to at least solve one of the technical problems existing in the prior art. To this end, the present application provides a compressor, which effectively reduces the amount of refrigerant sealed in the refrigeration cycle device compared to the technical solution in which the inside of the casing is high pressure, which is beneficial to improve the safety of the refrigeration cycle device, and the exhaust path of the compression mechanism part of the present application is shorter, facilitating the exhaust of the compression mechanism part.

[0004] The present application also provides a refrigeration cycle device comprising the above-mentioned compressor.

[0005] The compressor according to the embodiment of the present application comprises a casing and a compression mechanism part, the casing is provided with an inner cavity, the casing is provided with a suction port in communication with the inner cavity, the casing is provided with an exhaust pipe, the compression mechanism part is arranged in the inner cavity, the compression mechanism part comprises a cylinder assembly, the cylinder assembly is provided with a compression chamber, the compression chamber is provided with an air inlet and an exhaust port, the air inlet is in communication with the inner cavity, a middle partition plate is provided, the middle partition plate is provided with a first exhaust passage, each exhaust port is in communication with the first exhaust passage, at least one cylinder assembly is provided with a second exhaust passage, the second exhaust passage is in communication with the first exhaust passage and the second exhaust passage is in communication with the exhaust pipe.

[0006] The compressor according to the embodiment of the present application has low pressure inside the shell, and compared with the technical solution that the shell has high pressure, the present application effectively reduces the refrigerant sealing amount in the refrigeration cycle device, and is beneficial to improve the safety of the refrigeration cycle device. When the compression mechanism of the present application discharges, the high pressure gas in the plurality of compression chambers is discharged to the first discharge passage, and then discharged to the discharge pipe through the second discharge passage on the certain cylinder. The discharge mode makes the discharge path of the compression mechanism shorter, and is beneficial to the discharge of the compression mechanism. Moreover, the compressor provided by the present application is a multi-cylinder compressor, compared with a single-cylinder compressor, the compressor of the present application can operate at a speed of 10-90 rps or a wider range, and can increase the refrigeration capacity of the refrigeration cycle device. In addition, since the pressure inside the shell of the present application is low, the refrigeration cycle device does not need to be provided with a liquid accumulator, which is beneficial to reduce the refrigerant sealing amount and the cost of the refrigeration cycle device.

[0007] In some embodiments, each of the cylinder assemblies comprises a cylinder having a cavity therein, a piston eccentrically rotatable disposed in the cavity, and a sliding vane reciprocally movable disposed in the cylinder and having a leading end abutting against the piston.

[0008] In some embodiments, one of the cylinder assemblies is provided with the second discharge passage, and the sliding vane of the remaining cylinder assemblies is provided with an elastic member.

[0009] In some embodiments, the compression mechanism comprises an intake passage penetrating through the cylinder assemblies and the partition plate, the intake passage being in communication with the inner cavity, and each of the intake ports being in communication with the intake passage.

[0010] In some embodiments, the compressor further comprises a first bearing and a first muffler, one side of one of the cylinder assemblies away from the partition plate is provided with the first bearing, the first muffler is disposed with the first bearing to define a muffling cavity, the first bearing is provided with a low pressure gas hole, the muffling cavity is provided with a gas inlet, and the intake passage is in communication with the inner cavity through the low pressure gas hole, the muffling cavity and the gas inlet.

[0011] In some embodiments, the crankshaft penetrates through the first muffler, the first bearing, the cylinder assemblies and the partition plate, the crankshaft drives the piston of the cylinder assemblies to rotate, and the inner wall of the first muffler and the outer peripheral wall of the crankshaft are spaced apart to define the gas inlet.

[0012] In some embodiments, the compressor further comprises a gas-liquid separation cylinder fixed to the motor rotor to rotate synchronously with the crankshaft, the gas inlet is in communication with a separation space in the gas-liquid separation cylinder, and the separation space has a gas outlet in communication with the inner cavity.

[0013] In some embodiments, the gas-liquid separation cylinder is sleeved outside the gas inlet, and a bottom wall of the gas-liquid separation cylinder is open.

[0014] In some embodiments, the piston adjacent to the first bearing is a first piston, an inner wall of the first piston and an outer wall of the crankshaft have an internal space therebetween, and the first bearing is provided with a communication hole for communicating the sound attenuation cavity and the internal space.

[0015] The refrigeration cycle device according to the embodiment of the present application comprises the compressor described in the technical solution.

[0016] Additional aspects and advantages of the present application will be set forth in part in the description that follows, and in part will become apparent to those skilled in the art upon examination of the following description and drawings or can be learned by practice of the present application. BRIEF DESCRIPTION OF DRAWINGS

[0017] The above and / or additional aspects and advantages of the present application will become apparent and be readily understood by considering the following description, taken in conjunction with the accompanying drawings, in which:

[0018] Figure 1 is a structural schematic diagram of a refrigeration cycle device according to an embodiment of the present application;

[0019] Figure 2 is a structural schematic diagram of a compression mechanism of a double-cylinder compressor according to the present application;

[0020] Figure 3 is a sectional view of a symbol X-ray of Figure 2

[0021] Figure 4 is a sectional view of a symbol Y-ray of Figure 2

[0022] ​​Reference numerals: 1, compressor; 2, casing; 3, motor; 3A, stator; 3B, rotor; 4, gas-liquid separation cylinder; 5, compression mechanism; 6, intake passage; 7, lubricating oil; 8, first bearing; 8A, first silencer; 8B, low-pressure gas hole; 8C, communication hole; 9, suction port; 10, first cylinder; 10A, first compression chamber; 10C, first intake port; 10D, second discharge passage; 10E, discharge pipe; 10F, external discharge pipe; 10R, first piston; 12A, first vane; 12B, second vane; 12b, elastic member; 13, crankshaft; 13A, main shaft; 13B, first eccentric portion; 13M, intermediate shaft; 13C, second eccentric portion; 13D, sub shaft; 13E, shaft hole; 13F, oil supply pipe; 15, partition; 15A, first discharge passage; 15a, first discharge port; 15b, second discharge port; 15C, high-pressure via; 15V1, first discharge valve; 15V2, second discharge valve; 20, second cylinder; 20A, second compression chamber; 20C, second intake port; 20R, second piston; 25, second bearing; 30, condenser; 31, expansion device; 32, evaporator. DETAILED DESCRIPTION

[0023] Embodiments of the present application are described in detail below with reference to examples illustrated in the accompanying drawings, in which like or similar elements or elements having the same or similar functions are denoted by the same or similar reference numerals throughout the drawings. The embodiments described below by reference to the drawings are exemplary and are intended only for the purpose of explaining the present application, and should not be understood as limiting the present application.

[0024] In the description of the present application, it should be understood that the terms "center", "longitudinal", "transverse", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "clockwise", "counterclockwise", "axial", "radial", "circumferential" and the like indicate the orientation or positional relationship based on the orientation or positional relationship shown in the drawings, and are only for the purpose of facilitating the description of the present application and simplifying the description, and therefore should not be understood as indicating or implying that the devices or elements referred to must have a particular orientation, be constructed and operated in a particular orientation, and therefore should not be understood as limiting the present application. In addition, features defined with "first", "second" can explicitly or implicitly include one or more of the features. In the description of the present application, unless otherwise stated, the meaning of "a plurality of" is two or more.

[0025] In the description of the present application, it should be noted that unless otherwise explicitly specified and limited, the terms "mounting", "connecting", "connection" should be understood in a broad sense, for example, can be fixed connection, can also be detachable connection, or integrally connected; can be mechanical connection, can also be electrical connection; can be directly connected, can also be indirectly connected through an intermediate medium, can be the communication inside two elements. For those skilled in the art, the specific meaning of the above terms in the present application can be understood according to the specific circumstances.

[0026] The compressor 1 according to the embodiments of the present application will be described below with reference to Figures 1-4 The compressor 1 according to the embodiments of the present application will be described below with reference to

[0027] The compressor 1 according to the embodiments of the present application will be described below with reference to Figure 1 、 Figure 2 and Figure 3 The compressor 1 according to the embodiments of the present application will be described below with reference to

[0028] The compressor 1 according to the embodiments of the present application will be described below with reference to

[0029] The compressor 1 according to the embodiments of the present application will be described below with reference to

[0030] The compressor 1 according to the embodiments of the present application will be described below with reference to

[0031] When the compressor 1 of the embodiment of the present application is in operation, low-pressure refrigerant enters the inner chamber through the suction port 9 on the casing 2, so that the pressure inside the casing 2 is low. The compression mechanism 5 works to suck the low-pressure refrigerant in the inner chamber into the compression chamber through the intake port, and then the high-pressure refrigerant after compression enters the first exhaust passage 15A through the exhaust port, and then flows to the exhaust pipe 10E through the second exhaust passage 10D, and finally is discharged from the compressor 1.

[0032] According to the compressor 1 of the embodiment of the present application, the pressure inside the casing 2 is low, which effectively reduces the amount of refrigerant enclosed in the refrigeration cycle device, and is beneficial to improve the safety of the refrigeration cycle device. Moreover, when the compression mechanism 5 of the present application is in exhaust, the high-pressure gas in the plurality of compression chambers is discharged to the first exhaust passage 15A, and then is discharged to the exhaust pipe 10E through the second exhaust passage 10D on the certain cylinder. This exhaust mode makes the exhaust path of the compression mechanism 5 shorter, which is beneficial to the exhaust of the compression mechanism. The compressor 1 provided by the present application is a multi-cylinder compressor 1, which can operate at a speed of, for example, 10-90 rps or a wider range, and can increase the refrigeration capacity of the refrigeration cycle device. In addition, since the pressure inside the casing 2 of the present application is low, the refrigeration cycle device does not need to be provided with a liquid accumulator, which is beneficial to reduce the amount of refrigerant enclosed and the cost of the refrigeration cycle device.

[0033] Referring to Figure 2 , Figure 3 and Figure 4 , in some embodiments, the compression mechanism 5 is further provided with bearings, and each cylinder assembly comprises a cylinder, and the cylinder is provided with a cavity. When the number of cylinders in the compressor 1 is two, the cylinder is arranged between the adjacent bearings and the intermediate plate 15, and the inner wall of the cavity, the adjacent bearings and the intermediate plate 15 jointly define the compression chamber. When the number of cylinders in the compressor 1 is more than two, part of the cylinders are arranged between the adjacent bearings and the adjacent intermediate plates 15, and the inner wall of the cavity, the adjacent bearings and the adjacent intermediate plates 15 jointly define the compression chamber, and the other part of the cylinders are arranged between the adjacent two intermediate plates 15, and the inner wall of the cavity and the adjacent two intermediate plates 15 jointly define the compression chamber.

[0034] Each cylinder assembly further comprises a piston and a sliding vane, the piston is eccentrically rotatable arranged in the cavity, and the sliding vane is reciprocally movable arranged in the cylinder, and the leading end of the sliding vane abuts against the piston. When the piston is eccentrically rotated, the sliding vane reciprocally moves on the cylinder, and the sliding vane always abuts against the piston.

[0035] The tail end of the at least one sliding vane extends into the second exhaust passage 10D. Since the second exhaust passage 10D is used for passing high-pressure refrigerant, the tail end of the sliding vane extending into the second exhaust passage 10D, the high-pressure refrigerant can push the sliding vane against the corresponding piston, ensuring that the compression mechanism 5 can normally compress the refrigerant. In some embodiments, a sliding vane cavity for reciprocating movement of the sliding vane is provided on the cylinder, and the tail end of the sliding vane cavity is the second exhaust passage 10D, that is, the tail end of the sliding vane cavity is respectively communicated with the first exhaust passage 15A and the exhaust pipe 10E.

[0036] Through the above technical solution, when the compression mechanism 5 of the present application exhausts, the high-pressure refrigerant in the plurality of compression chambers is discharged through the respective exhaust ports to the first exhaust passage 15A, and is finally discharged through the second exhaust passage 10D at the tail end of the sliding vane cavity and the exhaust pipe 10E. The present application can directly discharge through the sliding vane cavity, thereby reducing the cost of the compression mechanism 5.

[0037] In some further embodiments, one of the cylinders is provided with the second exhaust passage 10D, and the corresponding sliding vane is configured to be stopped against the piston by the pressure difference; the sliding vane of the remaining cylinder is provided with the elastic member 12b, and the sliding vane is stopped against the piston by the force applied by the elastic member 12b. That is, the second exhaust passage 10D is not provided with the elastic member 12b, thereby reducing the resistance of the refrigerant passing through the second exhaust passage 10D.

[0038] Through the above technical solution, when the compressor 1 works, when the motor 3 starts, in the cylinder provided with the elastic member 12b, the sliding vane is stopped against the piston under the action of the elastic member 12b, and after the motor 3 starts for a period of time, in the cylinder provided with the second exhaust passage 10D, the sliding vane is stopped against the piston under the pushing of the high-pressure refrigerant in the second exhaust passage 10D.

[0039] Referring to Figure 2 , Figure 3 and Figure 4 , in some embodiments, the cylinder assembly is provided with two and is respectively a first cylinder assembly and a second cylinder assembly, that is, the compressor 1 is a double-cylinder compressor 1, the first cylinder assembly includes a first cylinder 10, a first piston 10R and a first sliding vane 12A; the second cylinder assembly includes a second cylinder 20, a second piston 20R and a second sliding vane 12B. The first cylinder 10 is provided with the second exhaust passage 10D, and the tail end of the first sliding vane 12A extends into the second exhaust passage 10D. The second cylinder 20 is provided with the elastic member 12b, the elastic member 12b is arranged at the tail end of the sliding vane cavity of the second cylinder 20, and the elastic member 12b is stopped against the tail end of the second sliding vane 12B to push the second sliding vane 12B and the second piston 20R to stop. The elastic member 12b can be a coil spring.

[0040] Referring to Figure 2 ,Figure 3 And Figure 4 In some specific embodiments, the partition plate 15 is provided with a high-pressure via 15C, and the first exhaust passage 15A communicates with the second exhaust passage 10D through the high-pressure via 15C.

[0041] In some embodiments, the compression mechanism 5 includes an intake passage 6 extending through the cylinder assembly and the partition plate 15, the intake passage 6 communicating with the inner cavity, and each intake port communicates with the intake passage 6.

[0042] Through the above technical solution, when the compressor 1 is working, the low-pressure refrigerant in the inner cavity first enters the intake passage 6, and then is branched from the intake passage 6 to the plurality of intake ports to enter the plurality of compression chambers for compression.

[0043] Referring to Figure 2 , Figure 3 And Figure 4 In some specific embodiments, the compressor 1 is a double-cylinder compressor 1, the first cylinder assembly includes: a first compression chamber 10A, the first compression chamber 10A is provided with a first intake port 10C and a first exhaust port 15a, the first intake port 10C communicates with the intake passage 6, and the first exhaust port 15a communicates with the first exhaust passage 15A; the second cylinder assembly includes: a second compression chamber 20A, the second compression chamber 20A is provided with a second intake port 20C and a second exhaust port 15b, the second intake port 20C communicates with the intake passage 6, and the second exhaust port 15b communicates with the first exhaust passage 15A.

[0044] Through the above technical solution, when the compressor 1 is working, the low-pressure refrigerant in the inner cavity first enters the intake passage 6, part of the refrigerant in the intake passage 6 enters the first compression chamber 10A through the first intake port 10C, and the other part of the refrigerant enters the second compression chamber 20A through the second intake port 20C, the compressed refrigerant in the first compression chamber 10A enters the first exhaust passage 15A through the first exhaust port 15a, the compressed refrigerant in the second compression chamber 20A enters the first exhaust passage 15A through the second exhaust port 15b, and the refrigerant in the first exhaust passage 15A merges to enter the second exhaust passage 10D, and is discharged from the compressor 1 through the exhaust pipe 10E.

[0045] Referring to Figure 2 , Figure 3 And Figure 4In some embodiments, the partition plate 15 is further provided with a first exhaust valve 15V1 for controlling opening and closing of the first exhaust port 15a and a second exhaust valve 15V2 for controlling opening and closing of the second exhaust port 15b. When the gas pressure in the first compression chamber 10A reaches a set value, the first exhaust valve 15V1 opens the first exhaust port 15a, so that the high-pressure gas can enter the first exhaust passage 15A through the first exhaust port 15a; when the gas pressure in the second compression chamber 20A reaches a set value, the second exhaust valve 15V2 opens the second exhaust port 15b, so that the high-pressure gas can enter the first exhaust passage 15A through the second exhaust port 15b.

[0046] In some embodiments, the first cylinder 10 is further provided with an exhaust pipe 10E in communication with the second exhaust passage 10D, the exhaust pipe 10E being in communication with an external exhaust pipe 10F adapted to communicate with a high-pressure side of a refrigeration cycle device.

[0047] With reference to Figure 2 , Figure 3 and Figure 4 In some embodiments, the compression mechanism 5 further comprises a first bearing 8 and a first muffler 8A, one side of one cylinder assembly away from the partition plate 15 is provided with the first bearing 8, the first muffler 8A is arranged on the first bearing 8 to define a muffling chamber, the first bearing 8 is provided with a low-pressure gas hole 8B, and the first muffler 8A is provided with a gas inlet, and the intake passage 6 is in communication with the inner cavity through the low-pressure gas hole 8B, the muffling chamber and the gas inlet.

[0048] Through the above technical solution, when the compressor 1 is working, the low-pressure refrigerant in the inner cavity first enters the muffling chamber through the gas inlet, reduces the noise generated when the refrigerant flows through the muffling chamber, and then enters the intake passage 6 through the low-pressure gas hole 8B.

[0049] With reference to Figure 2 , Figure 3 and Figure 4 In some specific embodiments, the compressor 1 is a double-cylinder compressor 1, and the compression mechanism 5 comprises a first bearing 8, a first muffler 8A and a second bearing 25. The first cylinder assembly is arranged between the first bearing 8 and the partition plate 15, and the inner wall of the cavity of the first cylinder 10, the first bearing 8 and the partition plate 15 jointly define the first compression chamber 10A; the second cylinder assembly is arranged between the second bearing 25 and the partition plate 15, and the inner wall of the cavity of the second cylinder 20, the second bearing 25 and the partition plate 15 jointly define the second compression chamber 20A. The first muffler 8A is arranged on the side of the first bearing 8 away from the first cylinder 10, and the first muffler 8A and the first bearing 8 define a muffling chamber.

[0050] In some embodiments, the crankshaft 13 penetrates the first muffler 8A, the first bearing 8, the cylinder assembly and the middle partition plate 15, the crankshaft 13 drives the piston of the cylinder assembly to rotate, and the inner wall of the first muffler 8A and the outer peripheral wall of the crankshaft 13 are spaced apart to define the gas inlet, that is, the refrigerant in the inner cavity needs to pass through the space between the inner wall of the first muffler 8A and the outer peripheral wall of the crankshaft 13 to enter the muffling cavity.

[0051] With reference to Figure 2 , Figure 3 and Figure 4 In some specific embodiments, the compressor 1 is a double-cylinder compressor 1, and the crankshaft 13 penetrates the first muffler 8A, the first bearing 8, the first cylinder 10, the middle partition plate 15, the second cylinder 20 and the second bearing 25. The crankshaft 13 is in sliding fit with the first bearing 8 and the second bearing 25, respectively. The crankshaft 13 comprises a first eccentric portion 13B and a second eccentric portion 13C, the first eccentric portion 13B is connected with the first piston 10R to drive the first piston 10R to rotate eccentrically, and the second eccentric portion 13C is connected with the second piston 20R to drive the second piston 20R to rotate eccentrically.

[0052] With reference to Figure 2 , Figure 3 and Figure 4 In some specific embodiments, the crankshaft 13 comprises a main shaft 13A, a first eccentric portion 13B, an intermediate shaft 13M, a second eccentric portion 13C and a secondary shaft 13D connected in sequence. The main shaft 13A is connected with the motor 3, and the main shaft 13A is also in sliding fit with the first bearing 8, the first eccentric portion 13B is connected with the first piston 10R, the intermediate shaft 13M penetrates the middle partition plate 15, the second eccentric portion 13C is connected with the second piston 20R, and the secondary shaft 13D is in sliding fit with the second bearing 25.

[0053] In some embodiments, the motor 3 comprises a stator 3A and a rotor 3B, the compression mechanism 5 further comprises a gas-liquid separation cylinder 4, the gas-liquid separation cylinder 4 is fixed to the motor rotor 3B, the motor rotor 3B can drive the gas-liquid separation cylinder 4 to rotate synchronously with the crankshaft 13, the gas inlet of the first muffler 8A communicates with a separation space of the gas-liquid separation cylinder 4, and the separation space has a gas passage opening communicating with the inner cavity.

[0054] The refrigerant entering the inner cavity through the suction port 9 comprises low-pressure gaseous refrigerant and liquid refrigerant. When the compressor 1 is working, the crankshaft 13 drives the gas-liquid separation cylinder 4 to rotate, and under the action of centrifugal force, the liquid refrigerant in the inner cavity cannot enter the inner wall of the gas-liquid separation cylinder 4, and the gaseous refrigerant can enter the separation space through the gas passage opening and then enter the muffling cavity through the gas inlet. Through the above technical solution, the possibility of the liquid refrigerant entering the compression cavity is reduced.

[0055] With reference to Figure 2 , Figure 3 andFigure 4 In some further embodiments, the gas-liquid separation cylinder 4 is sleeved outside the gas inlet, and the bottom wall of the gas-liquid separation cylinder 4 is open. That is, the portion of the first muffler 8A provided with the gas inlet extends from below the gas-liquid separation cylinder 4 to the separation space.

[0056] Through the above technical solutions, the opening of the separation space is arranged downward, and when the gas-liquid separation cylinder 4 rotates, the liquid refrigerant is affected not only by the centrifugal force but also by the gravity, further reducing the possibility of liquid refrigerant entering the compression chamber.

[0057] Referring to Figure 2 , Figure 3 and Figure 4 In some embodiments, the bottom of the casing 2 is provided with a containing groove for containing lubricating oil 7, and the containing groove is in communication with the inner cavity. One end of the crankshaft 13 extends into the containing groove, and the one end of the crankshaft 13 located in the containing groove is provided with a shaft hole 13E extending along the axis direction of the crankshaft 13; the crankshaft 13 is also provided with a first oil supply hole in communication with the shaft hole 13E, and the first oil supply hole is in communication with the gap between the crankshaft 13 and the first bearing 8. The lubricating oil 7 in the containing groove can enter the gap between the crankshaft 13 and the first bearing 8 through the shaft hole 13E and the first oil supply hole, which is beneficial to the relative sliding of the crankshaft 13 and the first bearing 8.

[0058] In some specific embodiments, the compressor 1 is a double-cylinder compressor 1, and the crankshaft 13 is also provided with a second oil supply hole in communication with the shaft hole 13E, and the second oil supply hole is in communication with the gap between the crankshaft 13 and the second bearing 25. The lubricating oil 7 in the containing groove can enter the gap between the crankshaft 13 and the second bearing 25 through the shaft hole 13E and the second oil supply hole, which is beneficial to the relative sliding of the crankshaft 13 and the second bearing 25.

[0059] Referring to Figure 2 , Figure 3 and Figure 4 In some embodiments, the inner wall of the first piston 10R and the outer wall of the crankshaft 13 have an internal space therebetween, and the first oil supply hole is in communication with the internal space, so that the lubricating oil 7 discharged from the first oil supply hole can also lubricate the first piston 10R.

[0060] In some further embodiments, the first bearing 8 is provided with a communication hole 8C for communicating the muffling cavity and the internal space.

[0061] By the above technical solution, the sound attenuation cavity, the internal space, the first oil supply hole and the shaft hole 13E are communicated, under the action of the pressure difference, the lubricating oil 7 in the holding groove can automatically enter the shaft hole 13E, and lubricate the gap between the crankshaft 13 and the first bearing 8 through the first oil supply hole. Then the lubricating oil 7 between the crankshaft 13 and the first bearing 8 can enter the internal space to lubricate the first piston 10R, and then the lubricating oil 7 in the internal space can enter the sound attenuation cavity through the communication hole 8C, enter the compression chamber together with the refrigerant, and finally enter the second exhaust passage 10D, that is, the slide cavity to lubricate the slide.

[0062] In some embodiments, the first exhaust passage 15A is in communication with the slide cavities of the first cylinder 10 and the second cylinder 20 respectively, so that the lubricating oil 7 can lubricate the first slide 12A and the second slide 12B respectively.

[0063] Referring to Figure 2 , Figure 3 and Figure 4 In some specific embodiments, the compressor 1 is a double-cylinder compressor 1, and the internal space is also formed between the inner wall of the second piston 20R and the outer wall of the crankshaft 13, and the internal space between the first piston 10R and the crankshaft 13 is communicated with the internal space between the second piston 20R and the crankshaft 13. The second bearing 25 is provided with a communication hole 8C for communicating the inner cavity and the internal space.

[0064] A specific embodiment of the present application is described below with reference to the accompanying Figures 1-4 drawings.

[0065] Referring to Figure 1 , the double-cylinder compressor of the present application has a variable frequency motor 3 composed of a stator 3A and a rotor 3B and a compression mechanism part 5 driven by the motor 3 in the upper part of the closed casing 2. The outer peripheral wall of the first cylinder 10 of the compression mechanism part 5 is fixed to the inner peripheral wall of the casing 2.

[0066] The compression mechanism part 5 includes a first bearing 8 fixed to the upper surface of the first cylinder 10, a partition plate 15 fixed to the lower surface of the first cylinder 10, a second cylinder 20 fixed to the lower surface of the partition plate 15, a second bearing 25 fixed to the lower surface of the second cylinder 20, a crankshaft 13 and lubricating oil 7. The crankshaft 13 is connected to the rotor 3B, the crankshaft 13 is in sliding fit with the first bearing 8 and the second bearing 25 respectively, the lubricating oil 7 can lubricate the sliding fit between the crankshaft 13 and the first bearing 8, and the lubricating oil 7 can lubricate the sliding fit between the crankshaft 13 and the second bearing 25.

[0067] In addition, the first cylinder 10 and the second cylinder 20 have a first compression chamber 10A and a second compression chamber 20A respectively, and the partition plate 15 has a first exhaust passage 15A as an exhaust passage for high-pressure gas.

[0068] Referring to Figure 2 and Figure 4 The intermediate plate 15 is provided with a first exhaust port 15a communicating with the first compression chamber 10A, a second exhaust port 15b communicating with the second compression chamber 20A, a first exhaust valve 15V1 provided at the first exhaust port 15a, a second exhaust valve 15V2 provided at the second exhaust port 15b, and a first exhaust passage 15A.

[0069] Figure 2 Detailed description of the compression mechanism 5 of the double-cylinder rotary compressor 1 of the present application is shown. The first cylinder 10 is fixed to the inner wall of the casing 2, and the first bearing 8 is connected to the upper surface of the first cylinder 10, and the intermediate plate 15 is connected to the lower surface of the first cylinder 10. Further, the second cylinder 20 is connected to the lower surface of the intermediate plate 15, and the second bearing 25 is connected to the lower surface of the second cylinder 20.

[0070] The crankshaft 13 driven by the rotation of the rotor 3B of the motor 3 comprises a main shaft 13A, a first eccentric portion 13B, an intermediate shaft 13M, a second eccentric portion 13C, and a secondary shaft 13D, and the main shaft 13A and the secondary shaft 13D are respectively slidably fitted in the first bearing 8 and the second bearing 25. Further, the crankshaft 13 has a shaft center hole 13E in the center, and the lubricating oil 7 sucked from the oil supply pipe 13F engaged with the lower end of the secondary shaft 13D flows into the shaft center hole 13E.

[0071] In the present embodiment, since the gas-liquid separation cylinder 4 is fixed to the lower surface of the high-speed rotating rotor 3B, the liquid refrigerant will not flow into the inside of the gas-liquid separation cylinder 4 due to the centrifugal force effect, and the gaseous refrigerant flows from the space above the first muffler 8A into the inside of the first muffler 8A. The liquid refrigerant can be prevented from entering the compression chamber for compression by the gas-liquid separation cylinder 4.

[0072] In addition, compared with the rotary compressor with high pressure in the casing 2, the large-volume casing 2 and the first muffler 8A can play the role of a liquid accumulator, and the compressor provided in the present embodiment has excellent function of preventing the mixing of liquid refrigerant into the suction gas.

[0073] However, in the rotary compressor with low pressure in the casing 2, the high-pressure gas outside the piston may leak into the internal space between the piston and the crankshaft, and further cause the risk of backflow of the lubricating oil outside the crankshaft to the oil supply passage inside the crankshaft. However, in the present embodiment, the communication hole 8C communicating with the internal space is provided in the first bearing 8 and the second bearing 25. By the above technical solution, the problem that the backflow of high-pressure gas of the two pistons to the crankshaft 13 causes the lubrication of the crankshaft 13 is solved. Moreover, the lubricating oil 7 lubricating the outer periphery of the first eccentric portion 13B can also flow to the first muffler 8A through the communication hole 8C.

[0074] The lubricating oil 7 flowing into the first muffler 8A mixes with the gaseous refrigerant in the first muffler 8A. The gaseous refrigerant in the first muffler 8A flows into the intake passage 6 from the low-pressure gas port 8B. Then, it flows into the first compression chamber 10A and the second compression chamber 20A from the first intake port 10C and the second intake port 20C respectively, becoming high-pressure gas. The lubricating oil 7 mixed with the high-pressure gas is discharged from the two first exhaust ports 15a and the second exhaust port 15b provided by the partition plate 15, and flows through the first exhaust passage 15A to the vane chambers of the first cylinder 10 and the second cylinder 20, respectively lubricating the first vane 12A and the second vane 12B.

[0075] Next, the high-pressure gas, having finished lubricating the two first vanes 12A and the second vane 12B, flows into the rear end of the vane chamber of the first cylinder 10. The rear end of the vane chamber of the first cylinder 10 forms the second exhaust passage 10D, and then flows out through the exhaust pipe 10E to the external discharge pipe 10F. Therefore, Figure 1 The refrigeration cycle shown is valid.

[0076] The present invention is characterized in that the rear end of the second slide 12B has an elastic element 12b constructed as a coil spring, but the elastic element is omitted in the first slide 12A. That is to say, the rear end of the slide cavity of the first cylinder 10 is not provided with an elastic element, which reduces the resistance when the high pressure gas flowing out of the first exhaust channel 15A flows out from the second exhaust channel 10D to the exhaust pipe 10E.

[0077] When the motor 3 is working, after the second vane 12B starts, the first vane 12A starts under the action of pressure difference a few seconds later.

[0078] Figure 3 yes Figure 2 The symbol represents an X-ray cross-section, showing the upper plane of the first cylinder 10. Low-pressure gas exiting the first muffler 8A can flow into the intake passage 6. Furthermore, Figure 3 by Figure 2 Based on the two first sliding vanes 12A and the second sliding vane 12B, the angle of the position of the intake passage 6 is approximately 30 degrees from the aforementioned sliding vanes.

[0079] The center of the partition 15 can be divided into two parts by horizontally dividing it: the first part located at the top and the second part located at the bottom. Figure 4 yes Figure 2 The diagram shows a cross-sectional view of the Y-line and a plan view of the first part. The first exhaust port 15a is connected to the first compression chamber 10A, and the first exhaust valve 15V1 controls the opening and closing of the first exhaust port 15a. High-pressure gas discharged from the first exhaust port 15a enters the first exhaust channel 15A, and then passes through the high-pressure through-hole 15C into… Figure 2The second exhaust passage 10D shown finally exhausts the gas to the external exhaust pipe 10F. In addition, as described above, the intake passage 6 is longitudinally bored through the first cylinder 10, the partition plate 15, and the second cylinder 20.

[0080] The partition plate 15 is a flat plate divided into two parts, a first part located above and a second part located below in the horizontal direction, and the first part is symmetrically arranged with the second part.

[0081] The refrigeration cycle device according to the embodiment of the present application includes a condenser 30, an expansion device 31, an evaporator 32, and the compressor 1 in the above technical solution.

[0082] The gas-liquid mixed low-pressure refrigerant sucked from the suction port 9 at the upper end of the casing 2 passes through the motor 3 and is separated due to the rotation of the gas-liquid separation cylinder 4 fixed at the lower end of the rotor 3B, and the gas refrigerant with light specific gravity flows into the inside of the first muffler 8A. Next, the gas of the first muffler 8A enters the intake passage 6 bored through the first cylinder 10, the partition plate 15, and the second cylinder 20 from the avoidance hole 8B provided on the first bearing 8, and the gas in the intake passage 6 is branched to the first compression chamber 10A and the second compression chamber 20A.

[0083] The high-pressure gas compressed by the above two compression chambers is respectively exhausted to the first exhaust passage 15A through the two exhaust ports bored on the partition plate 15. Next, the high-pressure gas in the first exhaust passage 15A is exhausted to the external exhaust pipe 10F through the second exhaust passage 10D and the communication pipe 10E provided in the first cylinder 10. Next, the high-pressure refrigerant flowing out to the condenser 30 becomes a condensed refrigerant, and the condensed refrigerant passing through the expansion device 31 is evaporated to a gas refrigerant in the evaporator 32.

[0084] By the above technical solution, the amount of refrigerant enclosed in the refrigeration cycle device can be reduced. Therefore, the air conditioning refrigerating capacity of the air conditioner using R290 refrigerant can be increased. In addition, compared with the conventional single-cylinder, the double-cylinder rotary compressor 1 can operate at a wider range of rotational speeds, for example, 10-90 rps or more, and can expand and minimize the air conditioning refrigerating capacity. In addition, since the pressure in the casing is low, the refrigeration cycle device of the present application does not need a liquid accumulator, which is also beneficial to the refrigerant enclosed amount and the manufacturing cost.

[0085] In the description of the specification, reference to "one embodiment", "some embodiments", "an exemplary embodiment", "an example", "a specific example", or "some examples" means that a particular feature, structure, material, or characteristic being described is included in at least one embodiment or example of the application. The appearances of the phrases "in one embodiment", "in some embodiments", "in an exemplary embodiment", "an example", "a specific example", or "some examples" in various places in the specification are not necessarily referring to the same embodiment or example. Furthermore, the particular features, structures, materials, or characteristics can be combined in any suitable manner in one or more embodiments or examples.

[0086] Although embodiments of the application have been shown and described, it will be appreciated that those skilled in the art can make various changes, modifications, substitutions and alterations thereto without departing from the principles and scope of the application, which are defined by the claims and their equivalents.

Claims

1. A compressor, characterized in that, include: A housing and a compression mechanism, wherein the housing has an inner cavity, an air intake port communicating with the inner cavity, and an exhaust pipe; the compression mechanism is located within the inner cavity, and the compression mechanism includes: A cylinder assembly, wherein the cylinder assembly is provided with a compression chamber, the compression chamber is provided with an air inlet and an air outlet, and the air inlet is connected to the inner cavity; A partition plate, on both sides of which the cylinder assembly is provided, the partition plate is provided with a first exhaust passage, each exhaust port is connected to the first exhaust passage, and the cylinder assembly with the exhaust pipe is provided with a second exhaust passage, the second exhaust passage being connected to the first exhaust passage and also connected to the exhaust pipe; each cylinder assembly includes: A cylinder, wherein the cylinder has a cavity; A piston, which is eccentrically rotatable within the cavity; A sliding plate, wherein the sliding plate is reciprocally disposed on the cylinder and the tip of the sliding plate abuts against the piston; The tail end of the sliding vane cavity is the second exhaust passage, which is not equipped with an elastic element.

2. The compressor according to claim 1, characterized in that, One of the cylinders is provided with a second exhaust passage; The slide of the other cylinders is provided with an elastic element.

3. The compressor according to any one of claims 1-2, characterized in that, The compression mechanism includes an air intake channel that passes through the cylinder assembly and the partition plate. The air intake channel communicates with the inner cavity, and each air inlet communicates with the air intake channel.

4. The compressor according to claim 3, characterized in that, It also includes a first bearing and a first muffler, wherein the first bearing is provided on the side of one of the cylinder assemblies opposite to the middle partition, the first muffler is provided on the first bearing to define a muffler cavity, the first bearing is provided with a low-pressure gas hole, the muffler cavity is provided with a gas inlet, and the air intake channel communicates with the inner cavity through the low-pressure gas hole, the muffler cavity and the gas inlet.

5. The compressor according to claim 4, characterized in that, It also includes a crankshaft through which the first muffler, the first bearing, the cylinder assembly, and the partition plate pass. The crankshaft drives the piston of the cylinder assembly to rotate. The inner wall of the first muffler and the outer peripheral wall of the crankshaft are spaced apart to define the gas inlet.

6. The compressor according to claim 5, characterized in that, It also includes a gas-liquid separator, which is fixed to the motor rotor to rotate synchronously with the crankshaft. The gas inlet is connected to the separation space inside the gas-liquid separator, and the separation space has an air outlet connected to the inner cavity.

7. The compressor according to claim 6, characterized in that, The gas-liquid separator is fitted outside the gas inlet, and the bottom wall of the gas-liquid separator is open.

8. The compressor according to claim 5, characterized in that, The piston adjacent to the first bearing is the first piston. There is an internal space between the inner wall of the first piston and the outer wall of the crankshaft. The first bearing is provided with a connecting hole for connecting the silencing cavity and the internal space.

9. A refrigeration cycle device, characterized in that, include: The compressor according to any one of claims 1-8.

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