Rotary compressor and air conditioning system thereof

Abstract

The application provides a rotary compressor and an air conditioning system thereof, and belongs to the technical field of air conditioning. The compressor comprises a pump body assembly, the pump body assembly comprises a low-pressure stage compression part and a high-pressure stage compression part, the high-pressure stage compression part comprises a high-pressure stage sliding vane and a pin assembly, the pin has a locking position and an unlocking position, a pressure relief channel is arranged between a suction port of the high-pressure stage compression part and a tail of the pin, in a single-stage mode, the pin is in the locking position and the pressure relief channel is blocked by the pin, in a two-stage mode, the pin is in the unlocking position and the pressure relief channel is blocked by the high-pressure stage sliding vane, and during switching of the pin between the two positions, the pressure relief channel is communicated with the tail of the pin and the suction port. The application can ensure that the displacement of the compressor in the single-stage mode is substantially equal to the displacement of the compressor in the two-stage mode, thereby ensuring the comprehensive energy efficiency of the compressor, the high-pressure stage sliding vane can respond to the two-stage mode more quickly, and the compressor has high energy efficiency.

Description

TECHNICAL FIELD

[0001] The present application belongs to the technical field of air conditioning, and particularly relates to a rotary compressor and an air conditioning system thereof. BACKGROUND

[0002] In hot summer and cold winter areas and northern cold areas, when using ordinary household air conditioners and heat pump water heaters, the air conditioning products generally have the problems of poor low-temperature heating effect, slow high-temperature refrigeration and low energy efficiency, and the household heat pump water heater has the problem of poor low-temperature hot water effect. The emergence of double-stage enthalpy-increasing technology solves these problems. The double-stage enthalpy-increasing compressor is used in these high-load heavy working conditions, and has a large pressure ratio. The double-stage compression can effectively distribute the pressure ratio, enable the air conditioning system to operate efficiently, reduce the exhaust temperature and improve the reliability of the compressor. In the double-stage enthalpy-increasing compressor in the prior art, when switching between single-stage and double-stage in the variable-volume compression part, the pressure difference between the head and the tail of the slide is very small or even zero, so that the slide cannot be switched in place in a short time. At this time, although the slide has been unlocked, the head of the slide does not contact the corresponding roller, so that the compressor does not actually operate in double-stage mode, but the pressure difference between the head and the tail of the slide is established before the compressor actually operates in double-stage mode, and the energy efficiency of the compressor is low. SUMMARY

[0003] Therefore, the present application provides a rotary compressor and an air conditioning system thereof, which can solve the technical problem that the double-stage enthalpy-increasing compressor in the prior art has a small or zero pressure difference between the two ends of the slide in the variable-volume compression part when switching from single-stage mode to double-stage mode, so that the compressor does not actually operate in double-stage mode, and the energy efficiency of the compressor is low.

[0004] In order to solve the above problems, the present application provides a rotary compressor, which comprises a shell and a motor assembly and a pump body assembly in the shell, the pump body assembly comprises a low-pressure stage compression part and a high-pressure stage compression part, the high-pressure stage compression part comprises a high-pressure stage slide and a pin assembly corresponding to the high-pressure stage slide, the pin assembly comprises a pin, the pin has a locking position for locking the high-pressure stage slide and an unlocking position for unlocking the high-pressure stage slide, and a pressure relief channel is provided between the suction port of the high-pressure stage compression part and the tail of the pin. When the rotary compressor operates in single-stage mode, the pin is in the locking position and the pressure relief channel is blocked by the pin, and when the rotary compressor operates in double-stage mode, the pin is in the unlocking position and the pressure relief channel is blocked by the high-pressure stage slide. During the switching process of the pin between the locking position and the unlocking position, the pressure relief channel communicates the tail of the pin and the suction port.

[0005] In some embodiments, the pin includes a shaft body, a head of the pin is at a first end of the shaft body, the tail is at a second end of the shaft body, a ring groove extending around the circumference of the shaft body is configured on the shaft body, a lower flange is connected to the bottom end of the high-pressure stage compression part, a pin hole is configured in the lower flange, the pin is assembled in the pin hole, and the pin assembly further includes a spring, the spring is at the tail, and when the pin is in the locked position, the groove opening of the ring groove seals the hole wall of the pin hole, and when the pin is in the unlocked position, the groove opening of the ring groove is in communication with the first port of the pressure relief channel.

[0006] In some embodiments, the second port of the pressure relief channel is in the sliding vane groove of the high-pressure stage sliding vane, and when the head of the high-pressure stage sliding vane is in contact with the high-pressure stage roller, the high-pressure stage sliding vane seals the second port; and / or, the locking hole on the bottom side wall of the high-pressure stage sliding vane has a guide surface on the side hole wall away from the high-pressure stage roller.

[0007] In some embodiments, the low-pressure stage compression part is between the high-pressure stage compression part and the motor assembly, an upper flange exhaust cavity is configured on the side of the low-pressure stage compression part away from the high-pressure stage compression part, a partition plate intermediate cavity is configured between the low-pressure stage compression part and the high-pressure stage compression part, the low-pressure stage compression part is controllably communicated with the upper flange exhaust cavity through a first exhaust valve, controllably communicated with the partition plate intermediate cavity through a second exhaust valve, the upper flange exhaust cavity is controllably communicated with the inner cavity of the shell through a third exhaust valve, the high-pressure stage compression part is configured with a lower flange exhaust cavity on the side away from the low-pressure stage compression part, and the high-pressure stage compression part is controllably communicated with the lower flange exhaust cavity through a fourth exhaust valve, the lower flange exhaust cavity is communicated with the inner cavity of the shell, and further includes an enthalpy increasing component, the enthalpy increasing component is communicated with the partition plate intermediate cavity.

[0008] In some embodiments, the partition plate intermediate cavity and the upper flange exhaust cavity are communicated through a communication pipeline.

[0009] In some embodiments, the low-pressure stage compression part includes a low-pressure stage cylinder, a supplementary air passage is configured on the low-pressure stage cylinder and communicated with the partition plate intermediate cavity, a supplementary air one-way valve is arranged in the supplementary air passage, and the supplementary air one-way valve allows the flow of supplementary air to flow towards the partition plate intermediate cavity and is reverse blocked.

[0010] In some embodiments, the head of the pin is always communicated with the inner cavity of the shell, and the tail of the pin is communicated with the control channel.

[0011] In some embodiments, an exhaust passage is configured on the pump body assembly and extends axially, one end of the exhaust passage is in communication with the lower flange exhaust cavity, and the other end of the exhaust passage is in communication with an inner cavity of the housing where the motor assembly is located.

[0012] The application also provides an air conditioning system comprising a two-stage enthalpy-increasing compressor, which is the rotary compressor described above.

[0013] In some embodiments, the air conditioning system further comprises a condenser, an evaporator, and a flash evaporator between the condenser and the evaporator pipeline, and further comprises a pin control component, a first inlet of the pin control component is controllably communicated with a refrigerant outlet of the evaporator through a first on-off valve, a second inlet of the pin control component is controllably communicated with an exhaust pipe of the two-stage enthalpy-increasing compressor through a second on-off valve, an outlet of the pin control component is communicated with the control channel, and a gas supplementing port of the flash evaporator is controllably communicated with an inlet of the enthalpy-increasing component.

[0014] In some embodiments, when the two-stage enthalpy-increasing compressor operates in a single-stage mode, the first on-off valve is controlled to be cut off, the second on-off valve is controlled to be communicated, and the gas supplementing port of the flash evaporator is controlled to be cut off from the enthalpy-increasing component; or when the two-stage enthalpy-increasing compressor operates in a two-stage mode, the first on-off valve is controlled to be communicated, the second on-off valve is controlled to be cut off, and the gas supplementing port of the flash evaporator is controlled to be communicated with the enthalpy-increasing component.

[0015] The rotary compressor and the air conditioning system thereof provided by the application have the following advantages: on the one hand, different from the traditional mode in which the low-pressure stage compression part is of a variable-volume structure, the high-pressure stage compression part in the application is also of a variable-volume structure, that is, when the compressor operates in a single-stage mode, the high-pressure stage compression part is idle, and the low-pressure stage compression part compresses the refrigerant from low pressure to high pressure and discharges the refrigerant, so that the displacement of the compressor in the single-stage mode is substantially equal to the displacement of the compressor in the two-stage mode, and the overall energy efficiency of the compressor is ensured; on the other hand, a pressure relief passage is configured in the pump body assembly, the pressure relief passage communicates the tail of the pin with the suction port during the switching of the pin between the locked position and the unlocked position, so that when the compressor is controlled to switch from the single-stage mode to the two-stage mode, the high-pressure refrigerant in the high-pressure stage compression part flows to the tail position of the pin through the pressure relief passage, that is, the head of the high-pressure stage sliding vane is relieved of pressure, and the tail of the high-pressure stage sliding vane is maintained at the exhaust pressure of the compressor, so that the pressure of the tail of the high-pressure stage sliding vane is much greater than the pressure of the head of the high-pressure stage sliding vane, the high-pressure stage sliding vane quickly approaches the high-pressure stage roller and contacts the outer sidewall surface of the high-pressure stage roller, and the compression of the high-pressure stage compression part is realized, that is, the high-pressure stage sliding vane can respond to the two-stage mode more quickly, and the compressor has high energy efficiency. BRIEF DESCRIPTION OF DRAWINGS

[0016] Figure 1Fig. 1 is a schematic diagram of the external structure of a rotary compressor according to an embodiment of the present application;

[0017] Figure 2 Fig. 2 is a schematic diagram of the internal structure of the rotary compressor according to an embodiment of the present application; Figure 1

[0018] Figure 3 Fig. 3 is a schematic diagram of the sectional structure of a pump body assembly in the rotary compressor according to an embodiment of the present application; Figure 1

[0019] Figure 4 Fig. 4 is a schematic diagram of the gas flow circulation in the rotary compressor according to an embodiment of the present application when the compressor is in a two-stage mode (the arrows in the figure indicate the flow direction);

[0020] Figure 5 Fig. 5 is a schematic diagram of the gas flow circulation in the rotary compressor according to an embodiment of the present application when the compressor is in a single-stage mode (the arrows in the figure indicate the flow direction);

[0021] Figure 6 Fig. 6 is a schematic diagram of the state of the high and low pressure control gas flow at the pin in the rotary compressor according to an embodiment of the present application when the compressor is in a two-stage mode;

[0022] Figure 7 Fig. 7 is a schematic diagram of the state of the high pressure control gas flow at the pin in the rotary compressor according to an embodiment of the present application when the compressor is in a single-stage mode;

[0023] Figure 8 Fig. 8 is a schematic diagram of the structure of the pin in the rotary compressor according to an embodiment of the present application; Figure 2

[0024] Figure 9 Fig. 9 is a schematic diagram of the structure of the high pressure stage vane in the rotary compressor according to an embodiment of the present application; Figure 2

[0025] Figure 10 Fig. 10 is a schematic diagram of the gas flow circulation in the compressor in an air conditioning system according to another embodiment of the present application when the compressor is in a two-stage gas supplementing and enthalpy increasing state;

[0026] Figure 11 Fig. 11 is a schematic diagram of the gas flow circulation in the compressor in an air conditioning system according to another embodiment of the present application when the compressor is in a single-stage non-gas supplementing and enthalpy increasing state.

[0027] The reference signs are as follows:

[0028] ​​​​1, motor assembly; 2, pump body assembly; 21, low-pressure stage compression part; 211, first exhaust valve; 212, second exhaust valve; 213, low-pressure stage cylinder; 214, low-pressure stage vane; 22, high-pressure stage compression part; 221, fourth exhaust valve; 222, high-pressure stage vane; 2221, locking hole; 2222, guide surface; 223, pin; 224, spring; 225, control channel; 23, exhaust channel; 24, high-pressure stage cylinder; 31, upper flange exhaust cavity; 311, third exhaust valve; 32, upper flange; 33, upper cover plate; 41, partition middle cavity; 411, air supplement one-way valve; 42, upper partition; 43, lower partition; 51, lower flange exhaust cavity; 52, lower flange; 53, lower cover plate; 6, enthalpy increasing part; 7, pressure relief channel; 71, ring groove; 10, shell; 100, two-stage enthalpy increasing compressor; 101, condenser; 102, evaporator; 103, flash evaporator; 104, pin control part; 1051, first on-off valve; 1052, second on-off valve; 106, distributor; 1071, primary throttling element; 1072, secondary throttling element. DETAILED DESCRIPTION

[0029] BRIEF DESCRIPTION OF DRAWINGS Figures 1 to 11 As shown, according to the embodiment of the present application, a rotary compressor is provided, which comprises a shell 10 and a motor assembly 1 and a pump body assembly 2 in the shell 10, the pump body assembly 2 comprising a low-pressure stage compression part 21 and a high-pressure stage compression part 22, the high-pressure stage compression part 22 comprising a high-pressure stage vane 222 and a pin assembly corresponding to the high-pressure stage vane 222, the pin assembly comprising a pin 223, the pin 223 having an upper locking position for locking the high-pressure stage vane 222 and an unlocking position for unlocking the high-pressure stage vane 222, and a pressure relief channel 7 between an air inlet of the high-pressure stage compression part 22 and a tail of the pin 223, when the rotary compressor operates in a single-stage mode, the pin 223 is in the upper locking position and the pressure relief channel 7 is blocked by the pin 223, when the rotary compressor operates in a two-stage mode, the pin 223 is in the unlocking position and the pressure relief channel 7 is blocked by the high-pressure stage vane 222, and in the process of switching the pin 223 between the upper locking position and the unlocking position, the pressure relief channel 7 connects the tail of the pin 223 and the air inlet, and a tail cavity of the high-pressure stage vane 222 and an inner cavity of the shell 10 are connected.

[0030] In the technical solution, on the one hand, different from the traditional low-pressure stage compression part in a variable volume structure, the high-pressure stage compression part 22 in the application is also in a variable volume structure, that is, when the compressor is in a single-stage mode, the high-pressure stage compression part 22 idles, and the low-pressure stage compression part 21 realizes compression of the refrigerant from low pressure to high pressure and discharges, so as to ensure that the compressor displacement in the single-stage mode is approximately equal to the compressor displacement in the double-stage mode, thereby ensuring the overall energy efficiency of the compressor; on the other hand, the pump body assembly is internally structured with a pressure relief channel 7, which communicates the tail of the pin 223 with the suction port during switching of the pin 223 between the locked position and the unlocked position. In this way, when the compressor is switched from the single-stage mode to the double-stage mode, the high-pressure refrigerant in the high-pressure stage compression part 22 will flow to the tail position of the pin 223 through the pressure relief channel 7, that is, the head of the high-pressure stage sliding vane 222 is relieved of pressure, and the tail is maintained at the exhaust pressure of the compressor. Therefore, the pressure of the tail of the high-pressure stage sliding vane 222 will be much greater than the pressure of the head, and the high-pressure stage sliding vane 222 will quickly approach the high-pressure stage roller and contact the outer sidewall surface thereof, thereby realizing compression of the high-pressure stage compression part 22. That is, the high-pressure stage sliding vane 222 can respond more quickly to the double-stage mode, thereby ensuring high energy efficiency of the compressor.

[0031] Specifically referring to Figure 8 the figure, in a specific embodiment, the pin 223 includes a shaft body, the head of the pin 223 is at the first end of the shaft body, the tail is at the second end of the shaft body, the shaft body is structured with a ring groove 71 extending around the circumference thereof, the bottom end of the high-pressure stage compression part 22 is connected with a lower flange 52, the lower flange 52 is internally structured with a pin hole (not labeled in the figure), the pin 223 is assembled in the pin hole, and the pin assembly further includes a spring 224, the spring 224 is at the tail, and when the pin 223 is in the locked position, the groove opening of the ring groove 71 seals the hole wall of the pin hole, and when the pin 223 is in the unlocked position, the groove opening of the ring groove 71 communicates with the first port of the pressure relief channel 7 (also the lower port of Figure 6 and Figure 7 ), that is, at this time, the position relationship of the ring groove 71 with respect to the outlet of the pressure relief channel 7 realizes on-off control of the pressure relief channel 7, and at the same time, the second port of the pressure relief channel 7 (also the upper port of Figure 6 and Figure 7the upper port of the pressure relief passage 7 is completely sealed within the plan view projection of the high-pressure stage vane 222, at this time, whether the lower port of the pressure relief passage 7 is open or not is not important, and during the process of switching the compressor from the two-stage mode to the single-stage mode, the ring groove 71 is lowered and the pressure relief passage 7 is connected for a certain period of time, but since the high-pressure stage compression part 22 will not discharge at this time, the connection during this process will not reduce the energy efficiency of the compressor, and when the pin 223 is finally in the locked position, the upper port of the pressure relief passage 7 is completely open, but since the ring groove 71 of the pin 223 is raised and offset from the lower port of the pressure relief passage 7, the pin hole wall at this time will seal the ring groove 71, and under this state, the refrigerant in the high-pressure stage compression part 22 will not be connected to the tail region of the pin 223 through the pressure relief passage 7.

[0032] Referring to Figure 9 As shown, the bottom side wall of the high-pressure stage vane 222 has a locking hole 2221, and the side hole wall away from the high-pressure stage roller has a guide surface 2222, which can guide the head of the pin 223 to smoothly insert into the locking hole 2221, and more importantly, the guide surface 2222 can guide the high-pressure stage vane 222 to further slide away from the side of the high-pressure stage roller.

[0033] In some embodiments, the low-pressure stage compression part 21 is between the high-pressure stage compression part 22 and the motor assembly 1, the low-pressure stage compression part 21 is configured with an upper flange exhaust cavity 31 away from the high-pressure stage compression part 22, a partition intermediate cavity 41 is configured between the low-pressure stage compression part 21 and the high-pressure stage compression part 22, the low-pressure stage compression part 21 is controllably communicated with the upper flange exhaust cavity 31 through a first exhaust valve 211 and controllably communicated with the partition intermediate cavity 41 through a second exhaust valve 212, the upper flange exhaust cavity 31 is controllably communicated with the inner cavity of the shell 10 through a third exhaust valve 311, the high-pressure stage compression part 22 is configured with a lower flange exhaust cavity 51 away from the low-pressure stage compression part 21 and inhales through the partition intermediate cavity 41, the high-pressure stage compression part 22 is controllably communicated with the lower flange exhaust cavity 51 through a fourth exhaust valve 221, the lower flange exhaust cavity 51 is communicated with the inner cavity of the shell 10, and further comprising an enthalpy increasing component 6, the enthalpy increasing component 6 is communicated with the partition intermediate cavity 41. It can be understood that the enthalpy increasing component 6 is controllably communicated with the medium-pressure gaseous refrigerant at the flash evaporation of the flash evaporator 103 and other gas supplement components of the air conditioning system, the enthalpy increasing component 6 is communicated with the partition intermediate cavity 41, the high-pressure stage compression part 22 is of a variable capacity structure, that is, the high-pressure stage slide 222 of the high-pressure stage compression part 22 is locked and out of contact with the high-pressure stage roller in the single-stage mode, at this time the high-pressure stage compression part 22 idles without compressing the refrigerant, the high-pressure stage slide 222 is in contact and locked with the high-pressure stage roller in the double-stage mode, at this time the high-pressure stage compression part 22 performs two-stage compression on the refrigerant discharged by the low-pressure stage compression part 21. In this technical solution, when the compressor or air conditioning system operates in the single-stage mode, the high-pressure stage compression part 22 does not perform secondary compression on the refrigerant, the high-pressure refrigerant compressed by the low-pressure stage compression part 21 will be discharged to the inner cavity of the shell 10 through the first exhaust valve 211 and the upper flange exhaust cavity 31, and then discharged from the compressor, this part of the refrigerant will not enter the high-pressure stage compression part 22 for secondary compression, and because it is directly discharged from the low-pressure stage compression part 21, it has a larger exhaust capacity (as known in the art, the exhaust capacity of the high-pressure stage compression part 22 is less than that of the low-pressure stage compression part 21), that is, the compressor displacement in the single-stage mode is consistent with that in the double-stage mode, and the overall energy efficiency of the compressor is improved.

[0034] In some embodiments, the partition intermediate cavity 41 is communicated with the upper flange exhaust cavity 31 through a communication passage (not shown, not referenced), specifically, the communication passage can be a pipeline assembly independent of the pump body assembly 2, as long as the communication between the two cavities is achieved, and more preferably, the communication passage is configured in the corresponding partition and the low-pressure stage cylinder 213, so that the structure of the pump body assembly is more compact, and at this time it can be understood that, since the partition intermediate cavity 41 is communicated with the upper flange exhaust cavity 31 through the communication passage, in the single-stage mode, part of the exhaust gas of the low-pressure stage compression part 21 directly enters the upper flange exhaust cavity 31 through the first exhaust valve 211 and is discharged to the inner cavity of the shell 10 through the third exhaust valve 311, and the other part enters the partition intermediate cavity 41 through the second exhaust valve 212 and flows into the upper flange exhaust cavity 31 again through the communication passage, so that the exhaust amount in the single-stage mode is much larger than the exhaust amount of the high-pressure stage compression part 22.

[0035] Referring to Figure 4 shown, the pump body assembly 2 operates in the two-stage mode, the low-pressure refrigerant sucked by the low-pressure stage compression part 21 is compressed for the first time in the low-pressure stage compression part 21 to form medium-pressure refrigerant, part of which enters the upper flange exhaust cavity 31 through the first exhaust valve 211 and enters the partition intermediate cavity 41 through the communication passage, and the other part directly enters the partition intermediate cavity 41 through the second exhaust valve 212, since the partition intermediate cavity 41 is communicated with the suction port of the high-pressure stage compression part 22, therefore, under the action of the high-pressure stage compression part 22, the medium-pressure refrigerant discharged by the low-pressure stage compression part 21 enters the high-pressure stage compression part 22 to be compressed for the second time to form high-pressure refrigerant, and the high-pressure refrigerant enters the lower flange exhaust cavity 51 through the fourth exhaust valve 221, and finally enters the inner cavity of the shell 10 to be discharged from the compressor through the compressor exhaust pipe, so that the low-pressure suction and high-pressure discharge of the refrigerant in the two-stage mode are achieved. Since the back pressure of the third exhaust valve 311 on the upper flange exhaust cavity 31 is the inner cavity pressure of the shell 10, at this time it is the high-pressure exhaust of the high-pressure stage compression part 22, therefore, the third exhaust valve 311 is in a closed state and cannot exhaust in this mode. It should be noted that in this mode, the exhaust of the flash tank 103 in the corresponding air conditioning system should be communicated with the inlet of the enthalpy increasing component 6 to synchronously achieve the effect of supplementing and increasing the enthalpy of the compressor.

[0036] Referring to Figure 5As shown, at this time, the pump body assembly 2 operates in single-stage mode, the low-pressure refrigerant sucked by the low-pressure stage compression part 21 is compressed for the first time in the low-pressure stage compression part 21 to form high-pressure refrigerant, part of which enters the upper flange exhaust cavity 31 via the first exhaust valve 211 and is discharged to the inner cavity of the shell 10 via the third exhaust valve 311, and the other part directly enters the partition intermediate cavity 41 via the second exhaust valve 212 and flows to the upper flange exhaust cavity 31 via the communication passage and is discharged to the inner cavity of the shell 10 via the third exhaust valve 311, and finally enters the inner cavity of the shell 10 and is discharged from the compressor via the compressor exhaust pipe, realizing low-pressure suction and high-pressure discharge of the refrigerant in single-stage mode. At this time, the third exhaust valve 311 in this mode is in an open state, and it should be noted that in this mode, the exhaust of the flash tank 103 in the corresponding air conditioning system should be cut off from the inlet of the enthalpy increasing component 6.

[0037] In some embodiments, the low-pressure stage compression part 21 comprises a low-pressure stage cylinder 213, and a charge air passage (not labeled in the figure) is constructed on the low-pressure stage cylinder 213 and communicates with the partition intermediate cavity 41, and a charge air one-way valve 411 is arranged in the charge air passage, which allows the flow of charge air to the partition intermediate cavity 41 and is reverse cut-off, preventing the reverse flow of high-pressure refrigerant gas during the charge air enthalpy increasing process from reducing the energy efficiency of the compressor.

[0038] In some embodiments, the head of the pin 223 is always in communication with the inner cavity of the shell 10, and the tail of the pin 223 is in communication with the control passage 225, that is, the pressure at the head of the pin 223 is always the exhaust pressure of the compressor, and the tail of the pin 223 is in communication with the control passage 225, so that by controlling the gas pressure in the control passage 225, the size change of the pressure difference between the head and the tail of the pin 223 can be realized to switch the position of the pin assembly, and then the switching between the two-stage mode and the single-stage mode of the compressor can be realized. See Figure 6 As shown, at this time, low-pressure gas is introduced into the control passage 225 (specifically, it can be communicated with the refrigerant outlet of the evaporator 102 of the air conditioning system), that is, the tail of the pin 223 is low-pressure, and the head of the pin 223 is high-pressure, so under the action of the high pressure at the head of the pin 223, the pin 223 descends from the pin hole of the high-pressure stage sliding vane 222 to be unlocked, at this time, the high-pressure stage compression part 22 compresses the refrigerant, and the compressor operates in two-stage mode; see Figure 7 As shown, at this time, high-pressure gas is introduced into the control passage 225 (specifically, it can be communicated with the exhaust pipe of the compressor), that is, the tail of the pin 223 is high-pressure, and the head of the pin 223 is also high-pressure, so under the action of the elastic force of the spring 224, the pin 223 ascends and inserts into the pin hole of the high-pressure stage sliding vane 222 to lock the high-pressure stage sliding vane 222, at this time, the high-pressure stage compression part 22 does not compress the refrigerant, and the compressor operates in single-stage mode.

[0039] SeeFigure 5 As shown, the pump body assembly 2 is configured with an exhaust passage 23 extending along the axial direction thereof, one end of the exhaust passage 23 being in communication with the lower flange exhaust cavity 51, and the other end of the exhaust passage 23 being in communication with the inner cavity of the shell 10 in which the motor assembly 1 is located. The exhaust passage 23 is specifically formed by the through holes at the corresponding positions of the lower flange 52, the high-pressure stage cylinder 24, the lower partition plate 43, the upper partition plate 42, the upper flange 32, and the upper cover plate 33, and does not need to be separately provided with a pipeline, thus being simple and compact in structure.

[0040] In some embodiments, the partition plate intermediate cavity 41 is formed by the upper partition plate 42 and the lower partition plate 43 being mutually buckled; and / or, the upper flange exhaust cavity 31 is formed by the upper flange 32 and the upper cover plate 33 being mutually buckled; and / or, the lower flange exhaust cavity 51 is formed by the lower flange 52 and the lower cover plate 53 being mutually buckled, facilitating the manufacturing process of each cavity.

[0041] The high pressure, the medium pressure, and the low pressure mentioned above are all relative, and the specific pressure values can be reasonably selected according to the design needs of the compressor.

[0042] According to the embodiments of the present application, an air conditioning system is also provided, which comprises the two-stage enthalpy-increasing compressor 100, the two-stage enthalpy-increasing compressor 100 being the rotary compressor described above, as shown in Figure 10 and Figure 11 As shown, the air conditioning system further comprises a condenser 101, an evaporator 102, and a flash evaporator 103 between the pipelines of the condenser 101 and the evaporator 102, and further comprises a pin control component 104, a first inlet of the pin control component 104 being controllably communicated with a refrigerant outlet of the evaporator 102 through a first on-off valve 1051, a second inlet of the pin control component 104 being controllably communicated with an exhaust pipe of the two-stage enthalpy-increasing compressor 100 through a second on-off valve 1052, an outlet of the pin control component 104 being communicated with the control passage 225, and a gas supplementing port of the flash evaporator 103 being controllably communicated with the inlet of the enthalpy-increasing component 6. The specific structure of the aforementioned pin control component 104, for example, comprises an outer shell, and three pipes respectively independently communicated with the inner space of the outer shell, and the first on-off valve 1051 and the second on-off valve 1052 can specifically be electromagnetic valves, so that the pin control component 104 forms a three-way controllable valve body. Specifically, when the two-stage enthalpy-increasing compressor 100 operates in a single-stage mode, the first on-off valve 1051 is controlled to be cut off, the second on-off valve 1052 is controlled to be communicated, and the gas supplementing port of the flash evaporator 103 is controlled to be cut off from the enthalpy-increasing component 6; or, when the two-stage enthalpy-increasing compressor 100 operates in a two-stage mode, the first on-off valve 1051 is controlled to be communicated, the second on-off valve 1052 is controlled to be cut off, and the gas supplementing port of the flash evaporator 103 is controlled to be communicated with the enthalpy-increasing component 6.

[0043] It is easy for those skilled in the art to understand that the advantageous technical features of the above-mentioned modes can be freely combined and superimposed without conflict.

[0044] The above merely provides the preferred embodiment of the present application and not intended to limit the present application. Any modification, equivalent replacement, and improvement made within the spirit and principle of the present application shall fall in the protection scope of the present application. The above merely provides the preferred embodiment of the present application and not intended to limit the present application. Any modification, equivalent replacement, and improvement made within the spirit and principle of the present application shall fall in the protection scope of the present application.

Claims

1. A rotary compressor comprising a housing (10) and a motor assembly (1), a pump body assembly (2) inside the housing (10), characterized in that, The pump body assembly (2) comprises a low-pressure stage compression part (21) and a high-pressure stage compression part (22), the high-pressure stage compression part (22) comprises a high-pressure stage sliding vane (222) and a pin assembly corresponding to the high-pressure stage sliding vane (222), the pin assembly comprises a pin (223), the pin (223) has a locking position for locking the high-pressure stage sliding vane (222) and an unlocking position for unlocking the high-pressure stage sliding vane (222), a pressure relief channel (7) is arranged between an air inlet of the high-pressure stage compression part (22) and a tail of the pin (223), when the rotary compressor operates in a single-stage mode, the pin (223) is in the locking position and the pressure relief channel (7) is blocked from the pin (223), when the rotary compressor operates in a two-stage mode, the pin (223) is in the unlocking position and the pressure relief channel (7) is blocked from the high-pressure stage sliding vane (222), and during switching of the pin (223) between the locking position and the unlocking position, the pressure relief channel (7) is in communication with the tail of the pin (223) and the air inlet.

2. The rotary compressor of claim 1, wherein The pin (223) comprises a shaft body, a head of the pin (223) is at a first end of the shaft body, the tail is at a second end of the shaft body, an annular groove (71) extending circumferentially around the shaft body is arranged on the shaft body, a lower flange (52) is connected to a bottom end of the high-pressure stage compression part (22), a pin hole is arranged in the lower flange (52), the pin (223) is assembled in the pin hole, and the pin assembly further comprises a spring (224), the spring (224) is at the tail, and when the pin (223) is in the locking position, a groove opening of the annular groove (71) seals a hole wall of the pin hole, and when the pin (223) is in the unlocking position, the groove opening of the annular groove (71) is in communication with a first port of the pressure relief channel (7).

3. The rotary compressor of claim 2, wherein, A second port of the pressure relief channel (7) is in a sliding vane groove of the high-pressure stage sliding vane (222), and when a head of the high-pressure stage sliding vane (222) is in contact with a high-pressure stage roller, the high-pressure stage sliding vane (222) seals the second port; and / or, a locking hole (2221) is arranged on a bottom side wall of the high-pressure stage sliding vane (222), a guide surface (2222) is arranged on a side hole wall of the locking hole (2221) away from the high-pressure stage roller.

4. The rotary compressor of claim 1, wherein The low-pressure stage compression part (21) is between the high-pressure stage compression part (22) and the motor assembly (1), the low-pressure stage compression part (21) is configured with an upper flange exhaust cavity (31) away from the high-pressure stage compression part (22) side, a partition plate intermediate cavity (41) is configured between the low-pressure stage compression part (21) and the high-pressure stage compression part (22), the low-pressure stage compression part (21) is controllably communicated with the upper flange exhaust cavity (31) through a first exhaust valve (211) and controllably communicated with the partition plate intermediate cavity (41) through a second exhaust valve (212), the upper flange exhaust cavity (31) is controllably communicated with the inner cavity of the shell (10) through a third exhaust valve (311), the high-pressure stage compression part (22) is configured with a lower flange exhaust cavity (51) away from the low-pressure stage compression part (21) side and inhales air through the partition plate intermediate cavity (41), the high-pressure stage compression part (22) is controllably communicated with the lower flange exhaust cavity (51) through a fourth exhaust valve (221), the lower flange exhaust cavity (51) is communicated with the inner cavity of the shell (10), and the double-stage enthalpy-increasing compressor (100) further comprises an enthalpy-increasing component (6), the enthalpy-increasing component (6) is communicated with the partition plate intermediate cavity (41).

5. The rotary compressor of claim 4, wherein, The partition plate intermediate cavity (41) and the upper flange exhaust cavity (31) are communicated through a communication pipeline.

6. The rotary compressor of any one of claims 4 to 5, wherein, The low-pressure stage compression part (21) comprises a low-pressure stage cylinder (213), the low-pressure stage cylinder (213) is configured with a supplementary air passage communicated with the partition plate intermediate cavity (41), a supplementary air one-way valve (411) is arranged in the supplementary air passage, and the supplementary air one-way valve (411) allows the flow of supplementary air to be towards the partition plate intermediate cavity (41) and is reverse cut-off.

7. The rotary compressor of claim 4, wherein The head of the pin (223) is always communicated with the inner cavity of the shell (10), and the tail of the pin (223) is communicated with a control channel (225).

8. The rotary compressor of claim 4, wherein, The pump body assembly (2) is configured with an exhaust passage (23) extending in the axial direction thereof, one end of the exhaust passage (23) is communicated with the lower flange exhaust cavity (51), and the other end of the exhaust passage (23) is communicated with the inner cavity of the shell (10) where the motor assembly (1) is located.

9. An air conditioning system comprising a two-stage enthalpy boosting compressor (100), characterized in that, The double-stage enthalpy-increasing compressor (100) is the rotary compressor in claim 7.

10. The air conditioning system of claim 9, wherein, Further comprising a condenser (101), an evaporator (102), and a flash evaporator (103) between pipelines of the condenser (101) and the evaporator (102), further comprising a pin control component (104), a first inlet of the pin control component (104) is controllably communicated with a refrigerant outlet of the evaporator (102) through a first on-off valve (1051), a second inlet of the pin control component (104) is controllably communicated with an exhaust pipe of the double-stage enthalpy-increasing compressor (100) through a second on-off valve (1052), an outlet of the pin control component (104) is communicated with the control channel (225), and a supplementary air inlet of the flash evaporator (103) is controllably communicated with an inlet of the enthalpy-increasing component (6).

11. The air conditioning system of claim 10, wherein, When the double-stage enthalpy-increasing compressor (100) operates in a single-stage mode, the first on-off valve (1051) is controlled to be cut off, the second on-off valve (1052) is controlled to be communicated, and the air supplement port of the flash evaporator (103) is controlled to be cut off from the enthalpy-increasing component (6); or when the double-stage enthalpy-increasing compressor (100) operates in a double-stage mode, the first on-off valve (1051) is controlled to be communicated, the second on-off valve (1052) is controlled to be cut off, and the air supplement port of the flash evaporator (103) is controlled to be communicated with the enthalpy-increasing component (6).

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