CN116085257A - Rotary compressor and air conditioning system thereof - Google Patents
Rotary compressor and air conditioning system thereof Download PDFInfo
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- CN116085257A CN116085257A CN202211674699.0A CN202211674699A CN116085257A CN 116085257 A CN116085257 A CN 116085257A CN 202211674699 A CN202211674699 A CN 202211674699A CN 116085257 A CN116085257 A CN 116085257A
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- 238000004378 air conditioning Methods 0.000 title claims abstract description 23
- 230000006835 compression Effects 0.000 claims description 96
- 238000007906 compression Methods 0.000 claims description 96
- 238000004891 communication Methods 0.000 claims description 39
- 238000005192 partition Methods 0.000 claims description 33
- 239000003507 refrigerant Substances 0.000 claims description 33
- 230000001502 supplementing effect Effects 0.000 claims description 25
- 230000009977 dual effect Effects 0.000 claims description 3
- 230000006698 induction Effects 0.000 claims 1
- 238000006073 displacement reaction Methods 0.000 abstract description 8
- 238000000034 method Methods 0.000 description 6
- 230000000694 effects Effects 0.000 description 3
- 238000012986 modification Methods 0.000 description 3
- 230000004048 modification Effects 0.000 description 3
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 3
- 238000010586 diagram Methods 0.000 description 2
- 238000005516 engineering process Methods 0.000 description 1
- 238000010438 heat treatment Methods 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 238000005057 refrigeration Methods 0.000 description 1
- 230000000153 supplemental effect Effects 0.000 description 1
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
- F04C23/001—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids of similar working principle
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
- F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
- F04C18/356—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
- F04C29/124—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston pumps
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B1/00—Compression machines, plants or systems with non-reversible cycle
- F25B1/04—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B31/00—Compressor arrangements
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B49/00—Arrangement or mounting of control or safety devices
- F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
- F25B49/022—Compressor control arrangements
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
Abstract
The invention provides a rotary compressor and an air conditioning system thereof, and belongs to the technical field of air conditioning. The invention can ensure that the compressor displacement in the single-stage mode is approximately equal to the compressor displacement in the double-stage mode, ensure the comprehensive energy efficiency of the compressor, ensure that the high-pressure slide vane can more quickly respond to the double-stage mode, and ensure that the compressor has higher energy efficiency.
Description
Technical Field
The invention belongs to the technical field of air conditioning, and particularly relates to a rotary compressor and an air conditioning system thereof.
Background
In summer hot winter cold area and northern cold area, when using ordinary domestic air conditioner and heat pump water heater, the air conditioner product generally has the low problem that low temperature heating effect, high temperature refrigeration are slow and the energy efficiency is low, and domestic heat pump water heater low temperature heats the problem that hot water effect is poor. The two-stage enthalpy-increasing technology solves the problems. The two-stage enthalpy-increasing compressor is used for the working conditions with high load and has high pressure ratio, and the pressure ratio can be effectively distributed by adopting the two-stage compression, so that the air conditioning system can be operated efficiently, the exhaust temperature is reduced, and the reliability of the compressor is improved; in the prior art, when the single-stage and double-stage switching is performed in the variable-capacity compression part, the sliding vane cannot be switched into place in a short time due to small or even no pressure difference between the head part and the tail part of the sliding vane, and at the moment, the head part of the sliding vane is not contacted with the corresponding roller although the sliding vane is unlocked, so that the compressor does not actually operate in the double-stage mode, but the double-stage mode of the compressor is really operated after the pressure difference between the head part and the tail part of the sliding vane is established, and the energy efficiency is low.
Disclosure of Invention
Therefore, the invention provides a rotary compressor and an air conditioning system thereof, which can solve the technical problems that in the prior art, when a single-stage mode of a double-stage enthalpy-increasing compressor is switched to a double-stage mode, the pressure difference between two ends of a sliding vane in a variable-capacity compression part is small or even no pressure difference exists, so that the compressor does not really operate in the double-stage mode, and the energy efficiency is low.
In order to solve the problems, the invention provides a rotary compressor, which comprises a shell, a motor assembly and a pump body assembly, wherein the motor assembly and the pump body assembly are arranged 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 sliding sheet and a pin assembly which is arranged corresponding to the high-pressure stage sliding sheet, the pin assembly comprises a pin, the pin is provided with a locking position for locking the high-pressure stage sliding sheet and an unlocking position for unlocking the high-pressure stage sliding sheet, a pressure release channel is arranged between an air suction port of the high-pressure stage compression part and the tail part of the pin, when the rotary compressor operates in a single-stage mode, the pin is positioned in the locking position and the pressure release channel is in pin cutting-off communication, and when the rotary compressor operates in a double-stage mode, the pin is positioned in the unlocking position and the pressure release channel is in pin cutting-off communication with the high-pressure stage sliding sheet, and in the switching process between the locking position and the unlocking position.
In some embodiments, the pin comprises a shaft body, the head of the pin is at the first end of the shaft body, the tail is at the second end of the shaft body, a ring groove extending circumferentially around the shaft body is formed in the shaft body, a lower flange is connected to the bottom end of the high-pressure stage compression part, a pin hole is formed in the lower flange, the pin is assembled in the pin hole, the pin assembly further comprises a spring, the spring is located at the tail, when the pin is in the locking position, the notch of the ring groove is sealed by the wall of the pin hole, and when the pin is in the unlocking position, the notch of the ring groove is communicated with the first port of the pressure release channel.
In some embodiments, the second port of the pressure relief channel is in a vane slot of the high pressure stage vane, and the high pressure stage vane seals the second port after the head of the high pressure stage vane contacts a high pressure stage roller; and/or the bottom side wall of the high-pressure-stage sliding blade is provided with a locking hole, and the wall of one side of the locking hole far away from the high-pressure-stage roller is provided with a guide surface.
In some embodiments, the low-pressure stage compression part is located between the high-pressure stage compression part and the motor assembly, an upper flange exhaust cavity is formed on one side, away from the high-pressure stage compression part, of the low-pressure stage compression part, a partition plate middle cavity is formed between the low-pressure stage compression part and the high-pressure stage compression part, the low-pressure stage compression part is in controllable communication with the upper flange exhaust cavity through a first exhaust valve and in controllable communication with the partition plate middle cavity through a second exhaust valve, the upper flange exhaust cavity is in controllable communication with the shell cavity through a third exhaust valve, a lower flange exhaust cavity is formed on one side, away from the low-pressure stage compression part, of the high-pressure stage compression part through a fourth exhaust valve and in controllable communication with the lower flange exhaust cavity, the lower flange exhaust cavity is in communication with the shell cavity, and the enthalpy increasing part is in communication with the partition plate middle cavity.
In some embodiments, the bulkhead intermediate chamber is in communication with the upper flange exhaust chamber via a communication line.
In some embodiments, the low-pressure stage compression part comprises a low-pressure stage cylinder, a gas supplementing channel communicated with the middle cavity of the partition plate is formed on the low-pressure stage cylinder, a gas supplementing one-way valve is arranged in the gas supplementing channel, and the gas supplementing one-way valve allows the flow of the gas supplementing air flow towards the middle cavity of the partition plate to be reversely blocked.
In some embodiments, the head of the pin is in communication with the interior cavity of the housing and the tail of the pin is in communication with the control passage.
In some embodiments, the pump body assembly is provided with an exhaust passage extending along the axial direction of the pump body assembly, one end of the exhaust passage is communicated with the lower flange exhaust cavity, and the other end of the exhaust passage is communicated with the inner cavity of the shell where the motor assembly is located.
The invention also provides an air conditioning system, which comprises the two-stage enthalpy-increasing compressor, wherein the two-stage enthalpy-increasing compressor is the rotary compressor.
In some embodiments, the air conditioning system further comprises a condenser, an evaporator, and a flash evaporator positioned between the condenser and the evaporator pipeline, and further comprises a pin control component, wherein 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.
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 air 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 air supplementing port of the flash evaporator is controlled to be communicated with the enthalpy-increasing component.
According to the rotary compressor and the air conditioning system thereof, on one hand, unlike the traditional mode that the low-pressure stage compression part is of a variable-volume structure, the high-pressure stage compression part is of a variable-volume structure, namely, when the compressor runs in a single-stage mode, the high-pressure stage compression part idles, and the low-pressure stage compression part compresses a refrigerant into high pressure and discharges the refrigerant, so that the compressor displacement in the single-stage mode is approximately equal to the compressor displacement in the double-stage mode, and the comprehensive energy efficiency of the compressor is ensured; on the other hand, the pump body component is internally provided with a pressure release channel, the pressure release channel is communicated with the tail part of the pin and the air suction port in the switching process of the pin between the locking position and the unlocking position, so when the compressor is controlled to be switched from the single-stage mode to the double-stage mode, high-pressure refrigerant in the high-pressure stage compression part flows from the pressure release channel part to the tail part of the pin, namely, the head part of the high-pressure stage sliding vane is released, the tail part of the high-pressure stage sliding vane is maintained at the exhaust pressure of the compressor, therefore, the tail pressure of the high-pressure stage sliding vane is far higher than the head pressure, the high-pressure stage sliding vane is rapidly close to the high-pressure stage roller and is contacted with the outer side wall surface of the high-pressure stage roller, the compression of the high-pressure stage compression part is realized, namely, the high-pressure stage sliding vane can rapidly respond to the double-stage mode, and the compressor is ensured to have higher energy efficiency.
Drawings
Fig. 1 is a schematic view showing an external structure of a rotary compressor according to an embodiment of the present invention;
FIG. 2 is a schematic view of the internal structure of FIG. 1;
FIG. 3 is a schematic cross-sectional view of the pump body assembly of FIG. 1;
FIG. 4 is a schematic illustration of the flow of air (arrows in the figure indicate flow direction) when the compressor of the present invention is in a dual stage mode;
FIG. 5 is a schematic illustration of the flow of air (arrows showing flow direction) when the compressor of the present invention is in a single stage mode;
FIG. 6 is a schematic illustration of the high and low pressure control flow at the pin when the compressor of the present invention is in a dual stage mode;
FIG. 7 is a schematic representation of the high pressure control flow at the pin when the compressor of the present invention is in a single stage mode;
FIG. 8 is a schematic view of the pin of FIG. 2;
FIG. 9 is a schematic view of the high pressure stage slider of FIG. 2;
FIG. 10 is a schematic diagram illustrating airflow through a compressor in a dual-stage air-supplementing enthalpy-increasing state in an air conditioning system according to another embodiment of the present invention;
fig. 11 is a schematic airflow diagram of a compressor in an air conditioning system according to another embodiment of the present invention in a single-stage non-supplemental air enthalpy state.
The reference numerals are expressed as:
1. a motor assembly; 2. a pump body assembly; 21. a low-pressure stage compression section; 211. a first exhaust valve; 212. a second exhaust valve; 213. a low pressure stage cylinder; 214. a low pressure stage slide; 22. a high-pressure stage compression section; 221. a fourth exhaust valve; 222. a high pressure stage slide; 2221. a locking hole; 2222. a guide surface; 223. a pin; 224. a spring; 225. a control channel; 23. an exhaust passage; 24. a high pressure stage cylinder; 31. an upper flange exhaust cavity; 311. a third exhaust valve; 32. an upper flange; 33. an upper cover plate; 41. a baffle middle cavity; 411. an air supplementing one-way valve; 42. an upper partition plate; 43. a lower partition plate; 51. a lower flange exhaust chamber; 52. a lower flange; 53. a lower cover plate; 6. an enthalpy increasing member; 7. a pressure relief channel; 71. a ring groove; 10. a housing; 100. a two-stage enthalpy-increasing compressor; 101. a condenser; 102. an evaporator; 103. a flash evaporator; 104. a pin control part; 1051. a first on-off valve; 1052. a second on-off valve; 106. a knockout; 1071. a primary throttling element; 1072. a secondary throttling element.
Detailed Description
Referring to fig. 1 to 11 in combination, according to an embodiment of the present invention, there is provided a rotary compressor including a housing 10, a motor assembly 1 and a pump body assembly 2 disposed in the housing 10, the pump body assembly 2 including a low-pressure stage compression portion 21 and a high-pressure stage compression portion 22, the high-pressure stage compression portion 22 including a high-pressure stage slide 222 and a pin assembly disposed corresponding to the high-pressure stage slide 222, the pin assembly including a pin 223, the pin 223 having a locked position for locking the high-pressure stage slide 222 and an unlocked position for unlocking the high-pressure stage slide 222, a pressure release passage 7 disposed between an air suction port of the high-pressure stage compression portion 22 and a tail portion of the pin 223, the pin 223 being in the locked position and the pressure release passage 7 being in cut-off communication with the pin 223 when the rotary compressor is operated in the two-stage mode, the pin 223 being in the unlocked position and the pressure release passage 7 being in cut-off communication with the high-pressure stage slide 222, and the tail portion of the pin 223 being in communication with the air suction port, and the tail cavity of the high-pressure stage slide 222 being in communication with an inner cavity 10 of the housing when the rotary compressor is operated in the two-stage mode.
In the technical scheme, on one hand, unlike the traditional mode that the low-pressure stage compression part is of a variable-volume structure, the high-pressure stage compression part 22 is of a variable-volume structure, namely, when the compressor runs in a single-stage mode, the high-pressure stage compression part 22 idles, and the low-pressure stage compression part 21 compresses a refrigerant with low pressure into high pressure and discharges the refrigerant, so that the displacement of the compressor in the single-stage mode is approximately equal to the displacement of the compressor in the double-stage mode, and the comprehensive energy efficiency of the compressor is ensured; on the other hand, the pump body assembly is internally provided with a pressure release channel 7, and the pressure release channel 7 communicates the tail part of the pin 223 with the air suction port in the process of switching the pin 223 between the locking position and the unlocking position, so when the compressor is controlled to be switched from the single-stage mode to the double-stage mode, the high-pressure refrigerant in the high-pressure stage compression part 22 flows from the pressure release channel 7 to the tail part of the pin 223, namely, the head part of the high-pressure stage sliding blade 222 is released, and the tail part is maintained at the exhaust pressure of the compressor, therefore, the tail pressure of the high-pressure stage sliding blade 222 is far greater than the head pressure, the high-pressure stage sliding blade 222 is rapidly close to the high-pressure stage roller and is contacted with the outer side wall surface of the high-pressure stage roller, the compression of the high-pressure stage compression part 22 is realized, namely, the high-pressure stage sliding blade 222 can rapidly respond to the double-stage mode, and the compressor is ensured to have higher energy efficiency.
Referring specifically to fig. 8, in a specific embodiment, the pin 223 includes a shaft body, the head of the pin 223 is located at a first end of the shaft body, the tail is located at a second end of the shaft body, a ring groove 71 extending circumferentially around the shaft body is configured on the shaft body, a lower flange 52 is connected to the bottom end of the high-pressure stage compression portion 22, a pin hole (not labeled in the drawing) is configured in the lower flange 52, the pin 223 is assembled in the pin hole, the pin assembly further includes a spring 224, the spring 224 is located at the tail, when the pin 223 is located at the locking position, the notch of the ring groove 71 is sealed with the wall of the pin hole, when the pin 223 is located at the unlocking position, the notch of the ring groove 71 is communicated with the first port (i.e. the lower ports of fig. 6 and 7) of the pressure release channel 7, i.e. at this time, the on-off control of the pressure release channel 7 is achieved through the positional relationship of the ring groove 71 relative to the outlet of the pressure release channel 7, meanwhile, the second port (i.e., the upper port in fig. 6 and 7) of the pressure relief channel 7 is located in the sliding vane groove of the high pressure stage sliding vane 222, and after the head of the high pressure stage sliding vane 222 contacts with the high pressure stage roller, the high pressure stage sliding vane 222 seals the second port, it can be understood that after the compressor is switched from the single stage mode to the double stage mode and the high pressure stage sliding vane 222 slides in place (i.e., contacts with the high pressure stage roller), the upper port of the pressure relief channel 7 is completely sealed in the top view projection of the high pressure stage sliding vane 222, at this time, it is not important whether the lower port of the pressure relief channel 7 is on or off, while during the process of switching the compressor from the double stage mode to the single stage mode, the ring groove 71 is in communication with the pressure relief channel 7 for a certain period of time, but since the high pressure stage compression portion 22 will eventually no longer exhaust at this time, the communication in 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 release channel 7 is completely opened, but because the ring groove 71 of the pin 223 rises and is staggered with the lower port of the pressure release channel 7, the hole wall of the pin hole will seal the ring groove 71, and the refrigerant in the high-pressure stage compression part 22 will not communicate with the tail area of the pin 223 via the pressure release channel 7 in this state.
Referring to fig. 9, the bottom side wall of the high-voltage stage slide 222 has a locking hole 2221, and a side wall of the locking hole 2221 away from the high-voltage stage roller has a guide surface 2222, and the guide surface 2222 can guide the head of the pin 223 to be smoothly inserted into the locking hole 2221, and more importantly, the guide surface 2222 can guide the high-voltage stage slide 222 to slide further away from the high-voltage stage roller side.
In some embodiments, the low-pressure stage compression part 21 is located between the high-pressure stage compression part 22 and the motor assembly 1, an upper flange exhaust cavity 31 is configured on the side, away from the high-pressure stage compression part 22, of the low-pressure stage compression part 21, a partition middle 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, controllably communicated with the partition middle 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 sucked in through the partition middle cavity 41, a lower flange exhaust cavity 51 is configured on the side, away from the low-pressure stage compression part 21, 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 enthalpy increasing component 6 is further communicated with the partition middle cavity 41. It can be understood that the enthalpy increasing component 6 is controllably communicated with the medium pressure gaseous refrigerant at the flash of the air supplementing component such as the flash evaporator 103 of the air conditioning system, the enthalpy increasing component 6 is communicated with the partition plate middle cavity 41, the high pressure stage compression part 22 is of a variable capacity structure, that is, the high pressure stage sliding vane 222 of the high pressure stage compression part 22 in the single stage mode is locked to be separated from contact with the high pressure stage roller, at this time, the high pressure stage compression part 22 idles without compressing the refrigerant, and the high pressure stage sliding vane 222 in the double stage mode is locked to be contacted with the high pressure stage roller, at this time, the high pressure stage compression part 22 performs two-stage compression on the refrigerant discharged from the low pressure stage compression part 21. In this technical scheme, when the compressor or the air conditioning system operates in the single-stage mode, the high-pressure stage compression portion 22 does not compress the refrigerant secondarily, the high-pressure refrigerant formed by compression of the low-pressure stage compression portion 21 is discharged to the inner cavity of the casing 10 through the first exhaust valve 211 and the upper flange exhaust cavity 31, and then discharged out of the compressor, and the part of the refrigerant does not enter the high-pressure stage compression portion 22 to be compressed again, and is directly discharged out of the low-pressure stage compression portion 21, so that the compressor has a larger exhaust capacity (the exhaust capacity of the high-pressure stage compression portion 22 is smaller than that of the low-pressure stage compression portion 21, which is known in the industry), that is, the compressor displacement in the single-stage mode is consistent with the compressor displacement in the double-stage mode, and the comprehensive energy efficiency of the compressor is improved.
In some embodiments, the middle partition chamber 41 communicates with the upper flange exhaust chamber 31 through a communication pipeline (not shown and not labeled in the drawings), specifically, the communication channel may be a pipeline component independent from the pump body component 2, so long as the communication between the two chambers is achieved, and more preferably, the communication channel is configured in the corresponding partition plate and the low-pressure stage cylinder 213, so that the pump body component is more compact, at this time, it can be understood that, because the middle partition plate chamber 41 communicates with the upper flange exhaust chamber 31 through the communication channel, in the single-stage mode, a part of the exhaust gas of the low-pressure stage compression part 21 directly enters the upper flange exhaust chamber 31 through the first exhaust valve 211 and is exhausted to the inner cavity of the casing 10 through the third exhaust valve 311, and the other part enters the middle partition plate chamber 41 through the second exhaust valve 212 and flows into the upper flange exhaust chamber 31 again through the communication channel to be exhausted, so that the exhaust gas amount in the single-stage mode is far greater than that of the exhaust gas of the high-pressure stage compression part 22.
Referring to fig. 4, when the pump body assembly 2 is operated in the two-stage mode, the low-pressure refrigerant sucked by the low-pressure stage compression part 21 is compressed in the low-pressure stage compression part 21 for the first time to form a medium-pressure refrigerant, one part of the medium-pressure refrigerant enters the upper flange exhaust cavity 31 through the first exhaust valve 211 and enters the partition plate middle cavity 41 through the communication channel, the other part of the medium-pressure refrigerant directly enters the partition plate middle cavity 41 through the second exhaust valve 212, and the partition plate middle cavity 41 is communicated with the air suction port of the high-pressure stage compression part 22, so that the medium-pressure refrigerant discharged by the low-pressure stage compression part 21 enters the high-pressure stage compression part 22 for the second compression to form a high-pressure refrigerant under the action of the high-pressure stage compression part 22, 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 out of the compressor through the compressor exhaust pipe, and the low-pressure suction and high-pressure discharge of the refrigerant under the two-stage mode is realized. Since the back pressure of the third exhaust valve 311 in the upper flange exhaust chamber 31 is the pressure of the inner cavity of the casing 10, and is the high-pressure exhaust of the high-pressure stage compression part 22, the third exhaust valve 311 is in a closed state in this mode, and cannot exhaust. It should be noted that, in this mode, the exhaust gas of the flash evaporator 103 in the corresponding air conditioning system should be communicated with the inlet of the enthalpy increasing component 6, so as to synchronously realize the effect of air supplementing and enthalpy increasing for the compressor.
Referring to fig. 5, the pump body assembly 2 is operated in the single stage mode at this time, the low pressure refrigerant sucked by the low pressure stage compression part 21 is compressed in the low pressure stage compression part 21 for the first time to form a high pressure refrigerant, one part of the high pressure refrigerant enters the upper flange exhaust chamber 31 through the first exhaust valve 211 and is discharged to the inner cavity of the shell 10 through the third exhaust valve 311, the other part of the high pressure refrigerant directly enters the baffle middle chamber 41 through the second exhaust valve 212 and flows into the upper flange exhaust chamber 31 through the communication channel and is discharged to the inner cavity of the shell 10 through the third exhaust valve 311, and finally enters the inner cavity of the shell 10 to be discharged out of the compressor through the compressor exhaust pipe, so that the low pressure suction and high pressure discharge of the refrigerant in the single stage mode are realized. At this time, the third exhaust valve 311 is in an open state in this mode, and it should be noted that in this mode, the exhaust gas of the flash evaporator 103 in the corresponding air conditioning system should be in cut-off communication with the inlet of the enthalpy increasing part 6.
In some embodiments, the low-pressure stage compression part 21 includes a low-pressure stage cylinder 213, a gas supplementing channel (not labeled in the figure) communicating with the middle cavity 41 of the partition board is configured on the low-pressure stage cylinder 213, a gas supplementing one-way valve 411 is arranged in the gas supplementing channel, and the gas supplementing one-way valve 411 allows the flow of the gas supplementing air flow to the middle cavity 41 of the partition board to be reversely blocked, so that the reverse flow of the high-pressure refrigerant air flow in the process of supplementing the gas and increasing the enthalpy is prevented from reducing the energy efficiency of the compressor.
In some embodiments, the head of the pin 223 is always communicated with the inner cavity of the shell 10, the tail of the pin 223 is communicated with the control channel 225, that is, the head pressure of the pin 223 is always the exhaust pressure of the compressor, and the tail of the pin 223 is communicated with the control channel 225, so that the position switching of the pin assembly can be realized by controlling the gas pressure in the control channel 225, the change of the pressure difference between the head and the tail of the pin 223 can be realized, and the switching of the two-stage mode and the single-stage mode of the compressor can be further realized. Referring to fig. 6, at this time, low-pressure gas (specifically, may be communicated with a refrigerant outlet of the evaporator 102 of the air conditioning system) is introduced into the control channel 225, that is, the tail portion of the pin 223 is low-pressure, and the head portion of the pin 223 is high-pressure, so that under the action of the high-pressure of the head portion of the pin 223, the pin 223 descends and escapes from the pin hole of the high-pressure slide sheet 222, thereby realizing unlocking, and at this time, the high-pressure compression portion 22 compresses the refrigerant, and the compressor operates in a two-stage mode; referring to fig. 7, high-pressure gas (specifically, may be communicated with an exhaust pipe of the compressor) is introduced into the control channel 225 at this time, that is, the tail portion of the pin 223 is high-pressure, and the head portion of the pin 223 is also high-pressure, so that under the action of the elastic force of the spring 224, the pin 223 is inserted into the pin hole of the high-pressure slide sheet 222 in an upward direction, so as to lock the high-pressure slide sheet 222, and at this time, the high-pressure compression portion 22 does not compress the refrigerant, so that the compressor operates in a single-stage mode.
Referring to fig. 5, the pump body assembly 2 is provided with an exhaust channel 23 extending along the axial direction, one end of the exhaust channel 23 is communicated with the lower flange exhaust cavity 51, the other end of the exhaust channel 23 is communicated with the inner cavity of the housing 10 where the motor assembly 1 is located, the exhaust channel 23 is specifically formed by through holes at corresponding positions on the lower flange 52, the high-pressure cylinder 24, the lower partition plate 43, the upper partition plate 42, the upper flange 32 and the upper cover plate 33 together, no separate pipeline is needed, and the structure is simple and compact.
In some embodiments, the partition middle chamber 41 is formed by buckling an upper partition 42 and a lower partition 43 with each other; and/or, the upper flange exhaust cavity 31 is formed by buckling an upper flange 32 and an upper cover plate 33 with each other; and/or, the lower flange exhaust cavity 51 is formed by buckling the lower flange 52 and the lower cover plate 53 with each other, so as to facilitate the manufacturing process of each cavity.
The high pressure, the medium pressure and the low pressure are all relatively speaking, and the specific pressure value is reasonably selected according to the design requirement of the compressor.
According to an embodiment of the present invention, there is further provided an air conditioning system, including a dual-stage enthalpy-increasing compressor 100, where the dual-stage enthalpy-increasing compressor 100 is the rotary compressor described above, as shown in fig. 10 and 11, the air conditioning system further includes a condenser 101, an evaporator 102, and a flash evaporator 103 located between the pipelines of the condenser 101 and the evaporator 102, and further includes a pin control unit 104, where a first inlet of the pin control unit 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 unit 104 is controllably communicated with an exhaust pipe of the dual-stage enthalpy-increasing compressor 100 through a second on-off valve 1052, an outlet of the pin control unit 104 is communicated with a control channel 225, and a gas supplementing port of the flash evaporator 103 is controllably communicated with an inlet of the enthalpy-increasing unit 6. The pin control part 104 comprises a housing and three pipes independently communicated with the inner space of the housing, and the first on-off valve 1051 and the second on-off valve 1052 can be electromagnetic valves, so that the pin control part 104 forms a three-way controllable valve body. Specifically, when the two-stage enthalpy-increasing compressor 100 operates in the 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 supply port of the flash evaporator 103 is controlled to be cut off from the enthalpy-increasing part 6; alternatively, when the two-stage enthalpy-increasing compressor 100 is operated in the two-stage mode, the first on-off valve 1051 is controlled to be connected and the second on-off valve 1052 is controlled to be blocked, and the gas supply port of the flash evaporator 103 is controlled to be connected to the enthalpy-increasing member 6.
Those skilled in the art will readily appreciate that the advantageous features of the various aspects described above may be freely combined and stacked without conflict.
The foregoing description of the preferred embodiments of the invention is not intended to be limiting, but rather is intended to cover all modifications, equivalents, and alternatives falling within the spirit and principles of the invention. The foregoing is merely a preferred embodiment of the present invention, and it should be noted that it will be apparent to those skilled in the art that modifications and variations can be made without departing from the technical principles of the present invention, and these modifications and variations should also be regarded as the scope of the invention.
Claims (11)
1. The utility model provides a rotary compressor, includes casing (10) and is in motor element (1), pump body subassembly (2) in casing (10), its characterized in that, pump body subassembly (2) include low pressure level compression portion (21) and high pressure level compression portion (22), high pressure level compression portion (22) include high pressure level gleitbretter (222) and with pin subassembly that high pressure level gleitbretter (222) correspond the setting, pin subassembly includes pin (223), pin (223) have locking high pressure level gleitbretter (222) locking position and release to the unblock position of locking of high pressure level gleitbretter (222), have pressure release passageway (7) between the induction port of high pressure level compression portion (22) with the afterbody of pin (223), when rotary compressor operation single-stage mode, pin (223) are in locking position and pressure release passageway (7) are pin (223) intercommunication, when rotary compressor operation double-stage mode, pin (223) are in locking position and pressure release passageway (223) are in pressure release passageway (223) intercommunication.
2. The rotary compressor of claim 1, wherein the pin (223) comprises a shaft body, the head of the pin (223) is positioned at the first end of the shaft body, the tail is positioned at the second end of the shaft body, a ring groove (71) extending circumferentially around the shaft body is formed on the shaft body, a lower flange (52) is connected to the bottom end of the high-pressure stage compression part (22), a pin hole is formed in the lower flange (52), the pin (223) is assembled in the pin hole, the pin assembly further comprises a spring (224), the spring (224) is positioned at the tail, and when the pin (223) is positioned at the locking position, the notch of the ring groove (71) is sealed with the wall of the pin hole, and when the pin (223) is positioned at the unlocking position, the notch of the ring groove (71) is communicated with the first port of the pressure release channel (7).
3. The rotary compressor of claim 2, wherein the second port of the pressure relief channel (7) is in a vane groove of the high pressure stage vane (222), and the high pressure stage vane (222) seals the second port after a head of the high pressure stage vane (222) is in contact with a high pressure stage roller; and/or, the bottom side wall of the high-pressure-stage sliding blade (222) is provided with a locking hole (2221), and the wall of the side of the locking hole (2221) away from the high-pressure-stage roller is provided with a guide surface (2222).
4. Rotary compressor according to claim 1, characterized in that the low-pressure stage compression part (21) is located between the high-pressure stage compression part (22) and the motor assembly (1), an upper flange exhaust chamber (31) is configured at the side of the low-pressure stage compression part (21) remote from the high-pressure stage compression part (22), a partition plate intermediate chamber (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 in controllable communication with the upper flange exhaust chamber (31) through a first exhaust valve (211), with the partition plate intermediate chamber (41) through a second exhaust valve (212), the upper flange exhaust chamber (31) is in controllable communication with the inner chamber of the housing (10) through a third exhaust valve (311), the high-pressure stage compression part (22) is configured with a lower flange exhaust chamber (51) at the side of the low-pressure stage compression part (21) remote from the partition plate intermediate chamber (41), the high-pressure stage compression part (22) is in controllable communication with the lower flange exhaust chamber (51) through a fourth exhaust valve (221), the high-pressure stage compression part (22) is in further communication with the partition plate intermediate chamber (51), the high-pressure stage compression part (6) is in enthalpy-increasing communication with the partition plate intermediate chamber (51).
5. The rotary compressor according to claim 4, characterized in that the diaphragm intermediate chamber (41) communicates with the upper flange exhaust chamber (31) through a communication line.
6. The rotary compressor according to any one of claims 1 to 5, characterized in that the low-pressure stage compression part (21) comprises a low-pressure stage cylinder (213), a gas supplementing channel communicated with the partition plate intermediate chamber (41) is formed on the low-pressure stage cylinder (213), a gas supplementing one-way valve (411) is arranged in the gas supplementing channel, and the gas supplementing one-way valve (411) allows the flow of the gas supplementing air flow towards the partition plate intermediate chamber (41) to be reversely blocked.
7. The rotary compressor according to claim 4, characterized in that the head of the pin (223) is in communication with the inner cavity of the housing (10), and the tail of the pin (223) is in communication with a control channel (225).
8. Rotary compressor according to claim 1, characterized in that the pump body assembly (2) is configured with an exhaust channel (23) extending in the axial direction thereof, one end of the exhaust channel (23) is communicated with the lower flange exhaust cavity (51), and the other end of the exhaust channel (23) is communicated with the inner cavity of the housing (10) where the motor assembly (1) is located.
9. An air conditioning system comprising a two-stage enthalpy-increasing compressor (100), characterized in that the two-stage enthalpy-increasing compressor (100) is a rotary compressor according to claim 7.
10. The air conditioning system according to claim 9, further comprising a condenser (101), an evaporator (102) and a flash evaporator (103) between the condenser (101) and the evaporator (102) piping, further comprising a pin control member (104), a first inlet of the pin control member (104) being in controllable communication with a refrigerant outlet of the evaporator (102) through a first on-off valve (1051), a second inlet of the pin control member (104) being in controllable communication with an exhaust pipe of the dual stage enthalpy increasing compressor (100) through a second on-off valve (1052), an outlet of the pin control member (104) being in controllable communication with the control channel (225), a make-up port of the flash evaporator (103) being in controllable communication with an inlet of the enthalpy increasing member (6).
11. The air conditioning system according to claim 10, characterized in that 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 air supplementing port of the flash evaporator (103) is controlled to be cut off from the enthalpy-increasing part (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 air supplementing port of the flash evaporator (103) is controlled to be communicated with the enthalpy-increasing component (6).
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| Application Number | Priority Date | Filing Date | Title |
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| CN202211674699.0A CN116085257A (en) | 2022-12-26 | 2022-12-26 | Rotary compressor and air conditioning system thereof |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202211674699.0A CN116085257A (en) | 2022-12-26 | 2022-12-26 | Rotary compressor and air conditioning system thereof |
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| CN116085257A true CN116085257A (en) | 2023-05-09 |
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| CN202211674699.0A Pending CN116085257A (en) | 2022-12-26 | 2022-12-26 | Rotary compressor and air conditioning system thereof |
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| CN (1) | CN116085257A (en) |
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- 2022-12-26 CN CN202211674699.0A patent/CN116085257A/en active Pending
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