EP4008973B1 - Klimaanlage - Google Patents

Klimaanlage Download PDF

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Publication number
EP4008973B1
EP4008973B1 EP20882824.4A EP20882824A EP4008973B1 EP 4008973 B1 EP4008973 B1 EP 4008973B1 EP 20882824 A EP20882824 A EP 20882824A EP 4008973 B1 EP4008973 B1 EP 4008973B1
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EP
European Patent Office
Prior art keywords
port
pipe
piping
refrigerant
heat exchanger
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP20882824.4A
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English (en)
French (fr)
Other versions
EP4008973A4 (de
EP4008973A1 (de
Inventor
Junjie LEI
Hao Zhang
Shunquan LI
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Midea Group Co Ltd
GD Midea Air Conditioning Equipment Co Ltd
Original Assignee
Midea Group Co Ltd
GD Midea Air Conditioning Equipment Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from CN201921830849.6U external-priority patent/CN211177490U/zh
Priority claimed from CN201911034323.1A external-priority patent/CN112797658A/zh
Application filed by Midea Group Co Ltd, GD Midea Air Conditioning Equipment Co Ltd filed Critical Midea Group Co Ltd
Publication of EP4008973A1 publication Critical patent/EP4008973A1/de
Publication of EP4008973A4 publication Critical patent/EP4008973A4/de
Application granted granted Critical
Publication of EP4008973B1 publication Critical patent/EP4008973B1/de
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Classifications

    • 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
    • F25B13/00—Compression machines, plants or systems, with reversible cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F3/00—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems
    • F24F3/06—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the arrangements for the supply of heat-exchange fluid for the subsequent treatment of primary air in the room units
    • 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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
    • 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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/40—Fluid line 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/023—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units
    • F25B2313/0233—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units in parallel 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
    • F25B2313/0272—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using bridge circuits of one-way valves
    • 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
    • F25B2400/00—Component parts or details not otherwise provided for in this subclass
    • F25B2400/13—Economisers
    • 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
    • F25B2500/00—Problems to be solved
    • F25B2500/12—Sound
    • 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
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2509—Economiser valves
    • 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
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2515—Flow valves

Definitions

  • the present invention relates to the technical field of air conditioning, and in particular to an air conditioner.
  • the enhanced vapor injection refrigerant system is more and more widely used, especially applications to the coal-to-electricity conversion and multi-split air conditioners in northern China.
  • many systems are provided with secondary subcoolers to reduce pipeline pressure loss and indoor machine throttling noise.
  • an economizer may be shared.
  • EP 2 357 427 A1 discloses an air conditioner according to the preamble of claim 1.
  • a main objective of the present invention is to provide an air conditioner which aims to enable the air conditioner to have a high heating capacity in low-temperature environments while having a thermostatic dehumidification function.
  • the air conditioner provided in the present invention is defined in claim 1. It includes an outdoor unit and an indoor unit, where the outdoor unit includes an enhanced vapor compression mechanism and an outdoor heat exchanger, and the indoor unit includes a first heat exchanger and a first throttle regulator; the air conditioner further includes: a discharge pipe connected to a discharge side of the compression mechanism, a low-pressure suction pipe connected to a low-pressure suction side of the compression mechanism, a first piping connecting the discharge pipe, the outdoor heat exchanger, the first throttle regulator, and the first heat exchanger in sequence, and a second piping connecting the first heat exchanger and the low-pressure suction pipe, thus forming a refrigerant circuit; the outdoor unit further includes a first switching device, the first switching device being capable of switching between a first switching state of the first switching device and a second switching state of the first switching device, where in the first switching state the first switching device causes the first piping to communicate with the suction pipe and the second piping to communicate with the discharge pipe, and in the second switching state
  • the refrigerant bridge has a first port, a second port, and a refrigerant passage that causes the first port to communicate with the second port, and the refrigerant bridge is connected to the first piping through the first port and the second port.
  • the refrigerant bridge has a third port and a fourth port, and the two ends of the first refrigerant flow path are connected to the third port and the fourth port, respectively;
  • the first port communicates with the third port through a first bridge section, the first bridge section allowing unidirectional fluid flow from the first port to the third port;
  • the third port communicates with the second port through a second bridge section, the second bridge section allowing unidirectional fluid flow from the second port to the third port;
  • the second port communicates with the fourth port through a third bridge section, the third bridge section allowing unidirectional fluid flow from the fourth port to the second port;
  • the fourth port communicates with the first port through a fourth bridge section, the fourth bridge section allowing unidirectional fluid flow from the fourth port to the first port.
  • the refrigerant bridge has a third port and a fourth port, and the two ends of the first refrigerant flow path are connected to the third port and the fourth port, respectively;
  • the first port communicates with the third port through a first bridge section, the first bridge section allowing unidirectional fluid flow from the third port to the first port;
  • the third port communicates with the second port through a second bridge section, the second bridge section allowing unidirectional fluid flow from the third port to the second port;
  • the second port communicates with the fourth port through a third bridge section, the third bridge section allowing unidirectional fluid flow from the second port to the fourth port;
  • the fourth port communicates with the first port through a fourth bridge section, the fourth bridge section allowing unidirectional fluid flow from the first port to the fourth port.
  • the first bridge section, the second bridge section, the third bridge section, and the fourth bridge section are each provided with a one-way valve.
  • the liquid pickup pipe is provided with a liquid pickup throttle valve.
  • the return pipe includes a return pipe body, a first communication pipe, and a second communication pipe; one end of the first communication pipe communicates with the return pipe body and the other end communicates with the medium-pressure suction port of the compressor; the return pipe body or the first communication pipe is provided with a first control valve; and one end of the second communication pipe communicates with the return pipe body and the other end communicates with the suction pipe, and the second communication pipe is provided with a second control valve.
  • an inflow end of the liquid pickup pipe communicates with the first piping between the economizer and the outdoor side heat exchanger, or an inflow end of the liquid pickup pipe communicates with the first piping between the economizer and the first indoor throttle regulator.
  • an inflow end of the liquid pickup pipe has a liquid pickup port at a junction with the first piping, the liquid pickup port being located below the first piping around the liquid pickup port.
  • the air conditioner further includes a liquid pickup structure having a liquid pickup chamber and a first refrigerant port, a second refrigerant port, and a liquid pickup port that communicate with the liquid pickup chamber, the liquid pickup port being located below the first refrigerant port and the second refrigerant port.
  • the air conditioner further includes a second heat exchanger, a second throttle regulator, a third piping, and a branch pipe branching off from the discharge pipe, the third piping connecting a first intersection point of the first piping, the second throttle regulator, the second heat exchanger, and the branch pipe in sequence, where the first intersection point is located between the first throttle regulator and the outdoor heat exchanger, and the economizer is located on the first piping between the first intersection point and the outdoor heat exchanger.
  • the third piping communicates with the branch pipe, and a third control valve is provided on the branch pipe to control the opening and closing of the branch pipe; and the third piping communicates with the low-pressure suction pipe or with the second piping through a coupling pipe, and a fourth control valve is provided on the coupling pipe to control the opening and closing of the coupling pipe.
  • the air conditioner further includes a second switching device, the second switching device being capable of switching between a third switching state and a fourth switching state of the second switching device, where in the third switching state, the second switching device causes the third piping to communicate with the branch pipe, and in the fourth switching state, the second switching device causes the third piping to communicate with the suction pipe.
  • the air conditioner further includes an outdoor side throttle regulator, the outdoor side throttle regulator being located on the first piping between the economizer and the outdoor side heat exchanger.
  • the air conditioner further includes: a first connection pipe branching off from a second intersection point of the first piping and a second connection pipe branching off from the second piping, the second intersection point being located between the first throttle regulator and the outdoor heat exchanger, and the air conditioner further includes multiple indoor units, the multiple indoor units being connected in parallel to the first connection pipe and the second connection pipe.
  • the economizer includes a plate heat exchanger or a double-pipe heat exchanger having a first end and a second end provided opposite each other, where the first refrigerant flow path enters through the first end and exits through the second end and the second refrigerant flow path enters through the second end and exits through the first end; or the first refrigerant flow path enters through the second end and exits through the first end and the second refrigerant flow path enters through the first end and exits through the second end.
  • the refrigerant flow directions in the first refrigerant flow path and the second refrigerant flow path are always opposite (whether in the heating mode where the refrigerant flows from the indoor heat exchanger to the outdoor heat exchanger, or in the cooling mode where the refrigerant flows from the outdoor heat exchanger to the indoor heat exchanger).
  • the temperature difference between refrigerants in the first refrigerant flow path and the second refrigerant flow path is adequately maintained, so that the heat exchange effect between the first refrigerant flow path and the second refrigerant flow path can be ensured, which is conducive to ensuring the air replenishment effect of the economizer on the compressor in the heating mode, thus ensuring the heating capacity of the air conditioner in low-temperature environments; and which, at the same time, is conducive to ensuring the liquefaction effect (exhaust effect) of the economizer on the refrigerant in the cooling mode, ensuring that the refrigerant entering the indoor throttle device is in the liquid state, thus eliminating the abnormal sound generated in the indoor throttling process.
  • the air conditioner includes an outdoor unit 100 and an indoor unit 200, where the outdoor unit 100 includes a compression mechanism and an outdoor side heat exchanger 141, and the indoor unit 200 includes a first heat exchanger 220 and a first throttle regulator 240; the air conditioner further includes: a discharge pipe 111 connected to a discharge side of the compression mechanism, a low-pressure suction pipe 113 connected to a low-pressure suction side of the compression mechanism, a first piping 140 connecting the discharge pipe 111, the outdoor side heat exchanger 141, the first throttle regulator 240, and the first heat exchanger 220 in sequence, and a second piping 150 connecting the first heat exchanger 220 and the low-pressure suction pipe 113, thus forming a refrigerant circuit; the outdoor unit 100 further includes a first switching device 131, the first switching device 131 being capable of switching between a first switching state of the first switching device 131
  • the air conditioner in the first switching state the air conditioner is in the heating state, i.e., the first heat exchanger 220 is in the heating operation.
  • the air conditioner In the second switching state, the air conditioner is in the cooling state.
  • the first switching device 131 may be a four-way valve.
  • the air conditioner further includes an economizer 143, where the economizer 143 is provided on the first piping 140 between the outdoor side heat exchanger 141 and the first throttle device; a first refrigerant flow path 143a and a second refrigerant flow path 143b are provided in the economizer 143, the first refrigerant flow path 143a being connected to the first piping 140 through a refrigerant bridge 600; and one end of the second refrigerant flow path 143b communicates with the first piping 140 through a liquid pickup pipe 145 and the other end communicates with both a medium-pressure suction port of the compressor 110 and the suction pipe through a return pipe 146, so that refrigerant flow directions in the first refrigerant flow path 143a and the second refrigerant flow path 143b are opposite.
  • the first switching device 131 in the heating mode, is in the first state, in which case the discharge pipe 111 communicates with the second piping 150, so that the high-temperature and high-pressure refrigerant passes through the discharge pipe 111 and the second piping 150 and then enters the first heat exchanger 220 for heating, and then flows into the refrigerant bridge 600 through the first piping 140, and after being subject to the action of the refrigerant bridge 600, flows into the first refrigerant flow path 143a of the economizer 143, and flows back to the first piping 140 after passing through the first refrigerant flow path 143a, and passes through the outdoor throttle valve and the outdoor side heat exchanger 141, and then flows back to the compressor 110 through the suction pipe from the low-pressure suction port.
  • the second refrigerant flow path 143b of the economizer 143 after liquid pickup and passing through the plate heat exchanger to exchange heat with the first refrigerant flow path 143a, flows through the return pipe 146 back to the medium-pressure suction pipe of the compressor 110. At the same time, the communication between the return pipe 146 and the suction pipe is cut off, so as to replenish air to the compressor 110, thus improving the heating capacity of the compressor 110 in low-temperature environments.
  • the first switching device 131 is in the second state, in which case the discharge pipe 111 communicates with the first piping 140, and the high-temperature and high-pressure refrigerant passes through the discharge pipe 111 and the first piping 140, enters the outdoor side heat exchanger 141, then passes through the outdoor side heat exchanger 141 and then the outdoor throttle valve, and then enters the first refrigerant flow path 143a of the economizer 143 through the refrigerant bridge 600, and the first refrigerant flow path 143a passes through the plate heat exchanger and then flows back to the first piping 140, and then along the first piping 140 and through the first indoor throttle device, enters the first heat exchanger 220 for cooling; the inflow end of the second refrigerant flow path communicates with the first piping 140, and the refrigerant passes through the plate heat exchanger to exchange heat with the refrigerant in the first refrigerant flow path 143a (to perform heat exchange through the plate heat exchanger), and then flows through the return
  • the economizer 143 includes a plate heat exchanger or a double-pipe heat exchanger having a first end 510 and a second end 520 provided opposite each other, where the first refrigerant flow path 143a enters through the first end 510 and exits through the second end 520 and the second refrigerant flow path 143b enters through the second end 520 and exits through the first end 510; or the first refrigerant flow path 143a enters through the second end 520 and exits through the first end 510 and the second refrigerant flow path 143b enters through the first end 510 and exits through the second end 520.
  • the refrigerant in the first refrigerant flow path 143a and the refrigerant in the second refrigerant flow path 143b exchange heat through the plate heat exchanger or the double-pipe heat exchanger. Since the first refrigerant flow path 143a and the second refrigerant flow path 143b flow in opposite directions, the temperature difference between refrigerants in the first refrigerant flow path 143a and the second refrigerant flow path 143b is kept maximum, thus ensuring the heat exchange effect.
  • the refrigerant bridge 600 may be in various forms, as long as it enables, as the refrigerant passes through the first piping 140 (whether the refrigerant flows from the indoor heat exchanger to the outdoor side heat exchanger 141, or from the outdoor side heat exchanger 141 to the indoor heat exchanger), the refrigerant flow direction in the first refrigerant flow path 143a to be always opposite to the refrigerant flow direction in the second refrigerant flow path 143b so as to increase the temperature difference and thus ensure the heat exchange effect.
  • the refrigerant flow directions in the first refrigerant flow path 143a and the second refrigerant flow path 143b are always opposite (whether in the heating mode where the refrigerant flows from the indoor heat exchanger to the outdoor side heat exchanger 141, or in the cooling mode where the refrigerant flows from the outdoor side heat exchanger 141 to the indoor heat exchanger).
  • the temperature difference between refrigerants in the first refrigerant flow path 143a and the second refrigerant flow path 143b is adequately maintained, so that the heat exchange effect between the first refrigerant flow path 143a and the second refrigerant flow path 143b can be ensured, which is conducive to ensuring the air replenishment effect of the economizer 143 on the compressor 110 in the heating mode, thus ensuring the heating capacity of the air conditioner in low-temperature environments; and which, at the same time, is conducive to ensuring the liquefaction effect (exhaust effect) of the economizer 143 on the refrigerant in the cooling mode, ensuring that the refrigerant entering the indoor throttle device is in the liquid state, thus eliminating the abnormal sound generated in the indoor throttling process.
  • the conception of the present invention can be used not only for conventional air conditioners, but also for situations where multiple indoor heat exchangers are provided in the same one indoor unit 200, and also for situations where the refrigerant system has multiple indoor units 200.
  • the increase in the complexity of the structure of a single indoor unit 200 itself, or the increase in the number of indoor units 200, will increase the length of the refrigerant pipeline.
  • the effect of the present invention is to eliminate abnormal sound.
  • the indoor unit 200 further includes a second heat exchanger 210, a second throttle regulator 230, and a thermal circulation device for delivering heat or cold from the indoor unit 200 into the room.
  • the air conditioner further includes a third piping 160 and a branch pipe 112 branching off from the discharge pipe 111, the third piping 160 connecting a first intersection point 211 of the first piping 140, the second throttle regulator 230, the second heat exchanger 210, and the branch pipe 112 in sequence so as to form a refrigerant circuit, where the first intersection point 211 is located between the first throttle regulator 240 and the outdoor side heat exchanger 141; and the economizer 143 is located on the first piping 140 between the first intersection point 211 and the outdoor side heat exchanger 141.
  • the thermal circulation device may be a wind wheel, and the rotation of the wind wheel delivers to the room the air for which heat has been exchanged with an initial heat exchanger and the second heat exchanger 210.
  • the thermal circulation device may also be a water circulation device, where the first heat exchanger 220 and the second heat exchanger 210 deliver heat or cold to the room through the circulating water flowing in the water circulation device.
  • the air conditioner can realize cooling by the first heat exchanger 220 and heating by the second heat exchanger 210, so that thermostatic dehumidification can be realized.
  • the first throttle regulator 240 includes a solenoid throttle valve, such as a solenoid expansion valve
  • the second throttle regulator 230 includes a solenoid throttle valve, such as a solenoid expansion valve.
  • the first switching device 131 is in the second state, where the first heat exchanger 220 performs cooling at which point the refrigerant is discharged from the discharge pipe 111 and enters the second heat exchanger 210 through the branch pipe 112 and the third piping 160; and the second heat exchanger 210 performs heating at which point the refrigerant flows out of the second heat exchanger 210 and then flows into the second piping 150 and, along the second piping 150, passes through the refrigerant bridge 600, the economizer 143, the outdoor side heat exchanger 141 and the suction pipe and flows back to the low-pressure suction port of the compressor 110.
  • the air conditioner further includes a second switching device 132, the second switching device 132 being capable of switching between a third switching state and a fourth switching state of the second switching device 132, where in the third switching state, the second switching device 132 causes the third piping 160 to communicate with the branch pipe 112, and in the fourth switching state, the second switching device 132 causes the third piping 160 to communicate with the suction pipe.
  • the air conditioner is in a thermostatic dehumidification state.
  • the air conditioner is in the cooling state, i.e., the first heat exchanger 220 and the second heat exchanger 210 perform cooling at the same time.
  • the second switching device 132 may be a four-way valve.
  • an auxiliary branch pipe which communicates with the suction pipe when the third piping 160 communicates with the branch pipe 112.
  • the auxiliary branch pipe communicates with the low-pressure suction pipe 113 and the branch pipe 112.
  • a filter and a capillary are provided on the auxiliary branch pipe.
  • the first switching device 131 and the second switching device 132 may exist at the same time, so that the air conditioner can be switched among three states of thermostatic dehumidification, heating only and cooling only.
  • the air conditioner further includes an outdoor side throttle regulator 142, the outdoor side throttle regulator 142 being located on the first piping 140 between the economizer 143 and the outdoor side heat exchanger 141.
  • the outdoor side throttle regulator 142 includes an outdoor throttle valve, such as an electronic expansion valve.
  • the specific operation of the economizer 143 will be described below based on the situation where there exist a first indoor heat exchanger and a second indoor heat exchanger in the room.
  • the air conditioner further includes the economizer 143; the economizer 143 is provided on the first piping 140 between the outdoor side heat exchanger 141 and the first intersection point 211, and the return pipe 146 of the economizer 143 communicates with the medium-pressure suction port of the compressor 110.
  • the return pipe 146 may be in various forms, and the return pipe 146 may include only the return pipe 146 body, or may include the return pipe 146 body and the first communication pipe 148, one end of the first communication pipe 148 communicating with the return pipe 146 body and the other end communicating with the medium-pressure suction port of the compressor 110.
  • a first control valve 133 is provided on the return pipe 146 or on the first communication pipe 148 between the return pipe 146 and the medium-pressure suction port of the compressor 110.
  • the compressor 110 at this point is an enhanced vapor injection compressor 110 having a low-pressure suction port and a medium-pressure suction port.
  • the liquid pickup pipe 145 is provided with a liquid pickup throttle valve 144.
  • the discharge from the compressor 110 after being switched by the first switching device 131 and the second switching device 132, enters the second heat exchanger 210 (the refrigerant enters through the third piping 160) and the first heat exchanger 220 (the refrigerant enters through the first piping 140), respectively, for heating, and the liquid refrigerant coming from the second heat exchanger 210 and the first heat exchanger 220 is divided into two parts when it passes through the economizer 143: the first part (through the refrigerant bridge 600 and the first refrigerant flow path 143a) is directly subjected to throttling and pressure reduction by the outdoor side throttle regulator 142 (electronic expansion valve) and then enters the outdoor side heat exchanger 141 for evaporation and heat absorption; and the second part (through the second refrigerant flow path 143b) is subjected to throttling and pressure reduction by the liquid pickup throttle valve 144 (electronic expansion valve), and then enters the economizer 143
  • the system design of the enhanced vapor injection compressor 110 and the economizer 143 increases the refrigerant suction amount of the compressor 110 in low-temperature environments, which in turn increases the heat production at a low temperature, while reducing the compression ratio in low-temperature environments, so the reliability of the system can be improved.
  • the inflow end of the liquid pickup pipe 145 communicates with the first piping 140 between the economizer 143 and the outdoor side heat exchanger 141, while in some other embodiments, the inflow end of the liquid pickup pipe 145 may also communicate with the first piping 140 between the economizer 143 and the first intersection point 211 (in the absence of the first intersection point 211, the inflow end of the liquid pickup pipe 145 communicates with the first piping 140 between the economizer 143 and the first indoor throttle regulator). That is, the refrigerant flows in through the refrigerant outflow end of the economizer 143, which is conducive to improving the reliability of liquid pickup.
  • the junction between the inflow end of the liquid pickup pipe 145 and the first piping 140 is referred to as the liquid pickup point.
  • the connection position is referred to as a first liquid pickup point 134, or referred to as an upstream liquid pickup point; and when the inflow end of the liquid pickup pipe 145 communicates with the first piping 140 between the economizer 143 and the first intersection point 211 (or the first indoor throttle regulator), the connection position is referred to as a second liquid pickup point 135, or referred to as a downstream liquid pickup point.
  • the first liquid pickup point 134 or the upstream liquid pickup point is selected in order to replenish air to the compressor 110, thus increasing its heating capacity in low-temperature environments; and in the situation of cooling or thermostatic dehumidification (or dehumidification and reheating) by the indoor heat exchanger, the second liquid pickup point 135 or the downstream liquid pickup point is selected to cause the refrigerant entering the indoor unit 200 to be liquid as much as possible, thus avoiding the generation of abnormal sound during indoor throttling.
  • the position of the liquid pickup port 840 By setting the position of the liquid pickup port 840 to be lower than that of the first piping 140, because the liquid refrigerant flows along the lower side pipe wall of the first piping 140 (the density of the refrigerant in the liquid state is greater than that in the gaseous state), so that when the refrigerant passes through the liquid pickup port 840, the liquid refrigerant enters preferentially under the action of gravity, thus ensuring that refrigerant picked up at the liquid pickup port 840 is in the liquid state.
  • the liquid pickup port 840 may be formed in many ways, such as, for example, providing a liquid pickup structure 800 at the junction of the liquid pickup pipe 145 with the first piping 140, where the liquid pickup structure 800 has a liquid pickup chamber 810 and three refrigerant ports that communicate with the liquid pickup chamber 810, namely, a first refrigerant port 830, a second refrigerant port 820 and a liquid pickup port 840, the liquid pickup port 840 being located below the first refrigerant port 830 and the second refrigerant port 820. Both the first refrigerant port 830 and the second refrigerant port 820 communicate with the first piping 140, and the liquid pickup port 840 communicates with the inflow end of the liquid pickup pipe 145.
  • the first refrigerant port 830 communicates with the first piping 140 near the outdoor heat exchanger
  • the second refrigerant port 820 communicates with the first piping 140 near the first indoor throttle regulator.
  • the liquid pickup port 840 is located at the bottom of the liquid pickup structure 800.
  • the liquid pickup structure 800 may be in various shapes, such as rectangular, square, column, etc.
  • the first refrigerant port 830 and the second refrigerant port 820 may be located at the two ends or at the top of the liquid pickup structure 800, but, of course, in some embodiments, the first piping 140 may also extend into the liquid pickup chamber 810 through the first refrigerant port 830 and the second refrigerant port 820.
  • the air conditioner further includes a gas-liquid separator 120 and the economizer 143, the gas-liquid separator 120 being provided on the low-pressure suction pipe 113; and the economizer 143 is provided on the first piping 140 between the outdoor side heat exchanger 141 and the first intersection point 211, and the return pipe 146 of the economizer 143 communicates with the gas-liquid separator 120.
  • the return pipe 146 includes the return pipe 146 body and the second communication pipe 147, one end of the second communication pipe 147 communicating with the return pipe 146 body and the other end communicating with the gas-liquid separator 120.
  • the return pipe 146 communicates with the gas-liquid separator 120 through the low-pressure suction pipe 113, and a second control valve 149 is provided on the return pipe 146 or the second connection pipe 250 between the return pipe 146 and the low-pressure suction pipe 113.
  • the refrigerant condensing temperature at the outlet of the outdoor side heat exchanger 141 is further reduced, which improves the subcooling degree and causes the refrigerant to condense completely to the liquid state, and the liquid refrigerant enters the indoor heat exchanger for heat absorption and evaporation after the throttling and pressure reduction by the indoor electronic expansion valves, so that the refrigerant passing through the indoor throttle devices is in the full liquid state, thus solving the problem of abnormal sound of refrigerant generated by the gas-liquid two-phase state refrigerant.
  • the high-pressure and high-temperature gaseous refrigerant enters the outdoor side heat exchanger 141 for condensation and heat exchange
  • the medium-temperature and high-pressure refrigerant in the gas-liquid two-phase state coming out of the outdoor side heat exchanger 141 enters the economizer 143 and is then divided into two parts: the first part, after the throttling and pressure reduction by the liquid pickup throttle valve 144, passes through the liquid pickup pipe 145 and then enters the economizer 143 for heat absorption and evaporation
  • the evaporated gaseous refrigerant enters the gas-liquid separator 120 through the return pipe 146, the second control valve 149 (solenoid valve) and the connection pipe, and after being mixed with the gaseous refrigerant that has been subjected to heat absorption and evaporation by the indoor heat exchanger, enters the suction port of the compressor 110 together; and the second part, after further condensation and heat exchange by the
  • the refrigerant condensing temperature at the outlet of the outdoor side heat exchanger 141 is further reduced, which improves the subcooling degree and causes the refrigerant to condense completely to the liquid state from the gas-liquid two-phase state, and the liquid refrigerant enters the indoor heat exchanger for heat absorption and evaporation after the throttling and pressure reduction by the indoor electronic expansion valves (the first throttle regulator 240 and the second throttle regulator 230), so that the refrigerant passing through the indoor throttle devices (the first throttle regulator 240 and the second throttle regulator 230) is in the full liquid state, thus solving the problem of abnormal sound of refrigerant generated by the gas-liquid two-phase refrigerant when passing through the throttle regulators, thereby improving the satisfaction of users
  • the return pipe 146 communicates with the medium-pressure suction port of the compressor 110 and the gas-liquid separator 120, respectively, through different communication pipes, in which case the two communication pipes (the first communication pipe 148 and the second communication pipe 147) are provided with the first control valve 133 (near the compressor 110) and the second control valve 149 (near the gas-liquid separator 120), respectively.
  • the return pipe 146 according to the invention includes the return pipe 146 body and the two communication pipes. In the heating mode, the second control valve 149 is closed and the first control valve 133 is opened, allowing the refrigerant to flow into the compressor 110 to improve heating capacity.
  • the first control valve 133 In the cooling mode or thermostatic dehumidification mode, the first control valve 133 is closed and the second control valve 149 is opened to eliminate the abnormal sound.
  • the second control valve 149 may also be closed and the first control valve 133 opened due to special working conditions.
  • the air conditioner can adjust the first control valve 133 and the second control valve 149 according to the specific situation, thus improving the heating capacity of the air conditioner in the heating mode and reducing noise in the cooling and thermostatic dehumidification modes.
  • the compressor 110 is an enhanced vapor injection compressor 110, and this compressor 110 has a medium-pressure suction port M (i.e., vapor injection port) in addition to the conventional high-pressure exhaust port P and low-pressure suction port S, where the medium-pressure refrigerant vapor enters the compressor 110 through this vapor injection port to increase the effective flow of refrigerant.
  • M medium-pressure suction port
  • the a port of the economizer 143 is connected to a third port 630 of the refrigerant bridge 600, the b port of the economizer 143 is connected to a fourth port 640 of the refrigerant bridge 600, the c port of the economizer 143 is connected to the liquid pickup pipe 145, the d port of the economizer 143 is connected to the return pipe 146, the liquid pickup throttle valve 144 is connected in series to the liquid pickup pipe 145, the first control valve 133 is connected in series to a communication pipe, and the second control valve 149 is connected in series to another communication pipe, with one end of the communication pipe being connected to the medium-pressure suction port M of the compressor 110, and the other communication pipe being connected to the inlet end of the gas-liquid separator 120.
  • the air conditioner further includes multiple indoor units 200, and the form of heat exchangers included in each indoor unit 200 may be different, for example, one or more of an indoor machine with thermostatic dehumidification function (having both the first heat exchanger 220 and the second heat exchanger 210), an ordinary cooling/heating indoor machine (having only one heat exchanger and a corresponding throttle device), and an indoor machine with a conversion device that can freely switch between cooling or heating states may be included, so that the air conditioner can perform mixed operations of thermostatic dehumidification, cooling and heating at the same time.
  • an indoor machine with thermostatic dehumidification function having both the first heat exchanger 220 and the second heat exchanger 210
  • an ordinary cooling/heating indoor machine having only one heat exchanger and a corresponding throttle device
  • an indoor machine with a conversion device that can freely switch between cooling or heating states
  • the air conditioner further includes: a first connection pipe 260 branching off from a second intersection point 212 of the first piping 140 and a second connection pipe 250 branching off from the second piping 150, the second intersection point 212 being located between the first throttle regulator 240 and the outdoor side heat exchanger 141, and the air conditioner further includes multiple indoor units 200, the multiple indoor units 200 being connected in parallel to the first connection pipe 260 and the second connection pipe 250.
  • the second switching device 132 is controlled using two solenoid valves.
  • the third piping 160 communicates with the branch pipe 112 and communicates with the low-pressure suction pipe 113 or the second piping 150, with a third control valve 310 being provided on the branch pipe 112, and the third piping 160 communicates with the low-pressure suction pipe 113 or with the second piping 150 through the coupling pipe 114, with a fourth control valve 320 being provided on the coupling pipe 114.
  • the end of the coupling pipe 114 away from the third piping 160 may communicate with either the second piping 150 between the first switching device 131 and the indoor heat exchanger or the second piping 150 between the first switching device 131 and the gas-liquid separator 120.
  • the third control valve 310 and the fourth control valve 320 are separate control valves, the structure is simpler and more stable and reliable compared to the four-way valve.
  • the third control valve 310 and the fourth control valve 320 may be solenoid valves. The solenoid valve can still work stably and reliably when liquid refrigerant enters, while in the four-way valve, if liquid refrigerant enters, its working stability will be affected. Therefore, the use of separate third control valve 310 and fourth control valve 320 can improve the stability and reliability of the operation and state switching of the air conditioner.
  • the states of the third control valve 310 and the fourth control valve 320 in the case of power off may be set according to the actual requirements of the working conditions.
  • the third control valve 310 as an example.
  • the third control valve 310 may be selected as a normally open valve, that is, most of its work can be completed in the power-off state, and it needs to be powered on only when the state of the third control valve 310 needs to be switched.
  • the third control valve 310 maintains a normally closed state for a long time, it is selected to be a normally closed valve. In this way, it is conducive to reducing the electrical energy consumed by the second switching device 132 (including the third control valve 310) during the operation of the air conditioner, thus contributing to the rational use of energy.
  • the third piping 160, the branch pipe 112 and the coupling pipe 114 are connected at the first junction Q.
  • the low-pressure suction pipe 113 may communicate with the other two pipes through the coupling pipe 114.
  • one three-way valve may be provided at the first junction Q instead of two two-way valves.
  • the three-way valve realizes the communication of the third piping 160 to the coupling pipe 114 and the branch pipe 112, respectively, and may control the opening and closing of the coupling pipe 114 and the branch pipe 112, respectively. In this way, it is conducive to improving the convenience of the connection of the third piping 160, the coupling pipe 114 and the branch pipe 112.
  • the high-temperature and high-pressure refrigerant is discharged from an exhaust pipe and passes through the first switching device 131, the first piping 140, the outdoor side heat exchanger 141, and the economizer 143 in sequence, and then enters an evaporation heat exchanger and the first heat exchanger 220, respectively, for cooling.
  • the third control valve 310 is closed and the fourth control valve 320 is opened.
  • the high-temperature and high-pressure refrigerant is discharged from the exhaust pipe, and one part thereof passes through the first switching device 131 (which may be absent in some embodiments) and the second piping 150 in sequence, then enters the first heat exchanger 220 for heating, and then flows out of the first heat exchanger 220 and enters the first piping 140; and the other part passes through the branch pipe 112 and the third piping 160 in sequence and enters the second heat exchanger 210 for heating, and flows out of the second heat exchanger 210 and then enters the first piping 140, passes through the economizer 143, the outdoor side heat exchanger 141, and the first switching device 131, and then flows into the gas-liquid separator 120.
  • the third control valve 310 is opened and the fourth control valve 320 is closed.
  • Thermostatic dehumidification mode is the same as Thermostatic dehumidification mode:
  • the high-temperature and high-pressure refrigerant is discharged from the exhaust pipe, and one part thereof passes through the first switching device 131 (which may be absent in some embodiments), the first piping 140, the outdoor side heat exchanger 141, and the economizer 143 in sequence, and then enters the first heat exchanger 220 for cooling, and then passes through the second piping 150 and the first switching device 131 and flows into the gas-liquid separator 120.
  • the other part passes through the branch pipe 112 and the third piping 160 in sequence and enters the second heat exchanger 210 for heating, and then flows into the first heat exchanger 220 for cooling.
  • the third control valve 310 is opened and the fourth control valve 320 is closed.
  • the refrigerant bridge 600 has a first port 610, a second port 620, and a refrigerant passage that causes the first port 610 to communicate with the second port 620, and the refrigerant bridge 600 is connected to the first piping 140 through the first port 610 and the second port 620.
  • the first port 610 communicates with the first piping 140 near the outdoor side heat exchanger 141
  • the second port 620 communicates with the first piping 140 near the indoor unit 200.
  • the refrigerant bridge 600 further has a second port 620 and a fourth port 640, where the refrigerant bridge 600 is connected to the first refrigerant flow path of the economizer 143 through the second port 620 and the fourth port 640.
  • the refrigerant may enter the refrigerant bridge 600 through the first port 610 or the second port 620, flow into the first refrigerant flow path 143a through the third port 630 (the fourth port 640), pass through the first refrigerant flow path 143a and then enter the refrigerant bridge 600 through the fourth port 640 (the third port 630), and then flow into the first piping 140 through the second port 620 or the first port 610.
  • the refrigerant bridge 600 has a third port 630 and a fourth port 640, with the two ends of the first refrigerant flow path 143a being connected to the third port 630 and the fourth port 640, respectively;
  • the first port 610 communicates with the third port 630 through a first bridge section 650, the first bridge section 650 allowing unidirectional fluid flow from the first port 610 to the third port 630;
  • the third port 630 communicates with the second port 620 through a second bridge section 660, the second bridge section 660 allowing unidirectional fluid flow from the second port 620 to the third port 630;
  • the second port 620 communicates with the fourth port 640 through a third bridge section 670, the third bridge section 670 allowing unidirectional fluid flow from the fourth port 640 to the second port 620;
  • the fourth port 640 communicates with the first port 610 through a fourth bridge section 680, the fourth bridge section
  • liquid pickup is conducted at the first liquid pickup point 134 (the upstream liquid pickup point):
  • the refrigerant after flowing out of the indoor heat exchanger, enters the first piping 140, and enters the first bridge section 650 along the first piping 140 through the first port 610, flows out through the third port 630 and then enters the first refrigerant flow path 143a of the economizer 143, enters through the first end 510 (in some embodiments, it may also enter through the second end 520 and flow out through the first end 510) into the plate heat exchanger or double-pipe heat exchanger for heat exchange and then flows out through the second end 520, and then enters the third bridge section 670 through the fourth port 640, flows out of the refrigerant bridge 600 through the second port 620 and enters the first piping 140, and then passes through the outdoor side throttle regulator 142 and the outdoor side heat exchanger 141 in sequence.
  • the refrigerant after being subjected to liquid pickup at the first liquid pickup point 134 by the liquid pickup pipe 145, passes through the liquid pickup throttle valve 144 and enters through the second end 520 into the plate heat exchanger or double-pipe heat exchanger for heat exchange, and then flows out through the first end 510 (in some embodiments it may also enter through the first end 510 and flow out through the second end 520, as long as it is opposite to the first refrigerant flow path 143a), and then enters the return pipe 146 and, along the return pipe 146, flows back to the medium-pressure suction port of the compressor 110.
  • liquid pickup is conducted at the second liquid pickup point 135 (the downstream liquid pickup point):
  • the refrigerant after flowing out of the outdoor side heat exchanger 141, enters the first piping 140, and enters the second bridge section 660 along the first piping 140 through the second port 620, flows out through the third port 630 and then enters the first refrigerant flow path 143a of the economizer 143, enters through the first end 510 (in some embodiments, it may also enter through the second end 520 and flow out through the first end 510) into the plate heat exchanger or double-pipe heat exchanger for heat exchange and then flows out through the second end 520, and then enters the fourth bridge section 680 through the fourth port 640, flows out of the refrigerant bridge 600 through the first port 610 and enters the first piping 140, and then enters the indoor heat exchanger.
  • the refrigerant after being subjected to liquid pickup at the second liquid pickup point 135 by the liquid pickup pipe 145, passes through the liquid pickup throttle valve 144 and enters through the second end 520 into the plate heat exchanger or double-pipe heat exchanger for heat exchange, and then flows out through the first end 510 (in some embodiments it may also enter through the first end 510 and flow out through the second end 520, as long as it is opposite to the first refrigerant flow path 143a), and then enters the return pipe 146, and along the return pipe 146 it flows back to the medium-pressure suction port of the compressor 110.
  • the refrigerant bridge 600 has a third port 630 and a fourth port 640, with the two ends of the first refrigerant flow path 143a being connected to the third port 630 and the fourth port 640, respectively;
  • the first port 610 communicates with the third port 630 through a first bridge section 650, the first bridge section 650 allowing unidirectional fluid flow from the third port 630 to the first port 610;
  • the third port 630 communicates with the second port 620 through a second bridge section 660, the second bridge section 660 allowing unidirectional fluid flow from the third port 630 to the second port 620;
  • the second port 620 communicates with the fourth port 640 through a third bridge section 670, the third bridge section 670 allowing unidirectional fluid flow from the second port 620 to the fourth port 640;
  • the fourth port 640 communicates with the first port 610 through a fourth bridge section 680, the fourth bridge section 680 allowing unidirectional fluid flow from the first port 610 to the fourth port 640
  • liquid pickup is conducted at the first liquid pickup point 134 (the upstream liquid pickup point):
  • the refrigerant after flowing out of the indoor heat exchanger, enters the first piping 140, and enters the fourth bridge section 680 along the first piping 140 through the first port 610, flows out through the fourth port 640 and then enters the first refrigerant flow path 143a of the economizer 143, enters through the second end 520 (in some embodiments, it may also enter through the first end 510 and flow out through the second end 520) into the plate heat exchanger or double-pipe heat exchanger for heat exchange and then flows out through the first end 510, and then enters the second bridge section 660 through the third port 630, flows out of the refrigerant bridge 600 through the second port 620 and enters the first piping 140, and then passes through the outdoor side throttle regulator 142 and the outdoor side heat exchanger 141 in sequence.
  • the refrigerant after being subjected to liquid pickup at the first liquid pickup point 134 by the liquid pickup pipe 145, passes through the liquid pickup throttle valve 144 and enters through the first end 510 into the plate heat exchanger or double-pipe heat exchanger for heat exchange, and then flows out through the second end 520 (in some embodiments it may also enter through the second end 520 and flow out through the first end 510, as long as it is opposite to the refrigerant flow direction in the first refrigerant flow path 143a), and then enters the return pipe 146 and, along the return pipe 146, flows back to the medium-pressure suction port of the compressor 110.
  • liquid pickup is conducted at the second liquid pickup point 135 (the downstream liquid pickup point).
  • the refrigerant after flowing out of the outdoor side heat exchanger 141, enters the first piping 140, and enters the third bridge section 670 along the first piping 140 through the second port 620, flows out through the fourth port 640 and then enters the first refrigerant flow path 143a of the economizer 143, enters through the second end 520 (in some embodiments, it may also enter through the first end 510 and flow out through the second end 520) into the plate heat exchanger or double-pipe heat exchanger for heat exchange and then flows out through the first end 510, and then enters the first bridge section 650 through the third port 630, flows out of the refrigerant bridge 600 through the first port 610 and enters the first piping 140, and then enters the indoor heat exchanger.
  • the refrigerant after being subjected to liquid pickup at the second liquid pickup point 135 by the liquid pickup pipe 145, passes through the liquid pickup throttle valve 144 and enters through the first end 510 into the plate heat exchanger or double-pipe heat exchanger for heat exchange, and then flows out through the second end 520 (in some embodiments it may also enter through the second end 520 and flow out through the first end 510, as long as it is opposite to the first refrigerant flow direction), and then enters the return pipe 146 and, along the return pipe 146, flows back to the medium-pressure suction port of the compressor 110.
  • the first bridge section 650, the second bridge section 660, the third bridge section 670, and the fourth bridge section 680 are each provided with a one-way valve 690 to achieve unidirectional fluid flow with each bridge section.

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Claims (14)

  1. Klimaanlage, Folgendes umfassend: eine Außeneinheit (100), die einen Mechanismus zur verstärkten Dampfkompression und einen Außenwärmetauscher umfasst, eine Inneneinheit (200), die einen ersten Wärmetauscher (220) und einen ersten Drosselregler (240) umfasst, eine Ablassleitung (111), die mit einer Ablassseite des Kompressionsmechanismus verbunden ist, eine Niederdruck-Ansaugleitung (113), die mit einer Niederdruck-Ansaugseite des Kompressionsmechanismus verbunden ist, eine erste Rohrleitung (140), welche die Ablassleitung (111), den Außenwärmetauscher, den ersten Drosselregler (240) und den ersten Wärmetauscher (220) in Reihe verbindet, und eine zweite Rohrleitung (150), die den ersten Wärmetauscher (220) und die Niederdruck-Ansaugleitung (113) verbindet, wodurch ein Kühlkreis gebildet wird, eine erste Schaltvorrichtung (131), die in der Lage ist, zwischen Folgendem umzuschalten: einem ersten Schaltzustand der ersten Schaltvorrichtung (131), in dem die erste Schaltvorrichtung (131) bewirkt, dass die erste Rohrleitung (140) mit der Ansaugleitung in Verbindung steht, und bewirkt, dass die zweite Rohrleitung (150) in Verbindung mit der Ablassleitung (111) steht, und einem zweiten Schaltzustand der ersten Schaltvorrichtung (131), in dem die erste Schaltvorrichtung (131) bewirkt, dass die erste Rohrleitung (140) mit der Ablassleitung (111) in Verbindung steht, und bewirkt, dass die zweite Rohrleitung (150) mit der Ansaugleitung in Verbindung steht, und einen Vorwärmer (143), der an der ersten Rohrleitung (140) zwischen dem Außenwärmetauscher und der ersten Drosselvorrichtung angeordnet ist, einen ersten Kühlmittel-Strömungsweg (143a), der in dem Vorwärmer (143) angeordnet und durch eine Kühlmittelbrücke (600) mit der ersten Rohrleitung (140) verbunden ist, und einen zweiten Kühlmittel-Strömungsweg (143b), der in dem Vorwärmer (143) angeordnet ist, wobei ein Ende des zweiten Kühlmittel-Strömungsweges (143b) durch eine Flüssigkeitsaufnahmeleitung (145) mit der ersten Rohrleitung (140) in Verbindung steht und das andere Ende des zweiten Kühlmittel-Strömungsweges (143b) durch eine Rückführungsleitung (146) mit sowohl einem Mitteldruck-Ansauganschluss des Kompressors (110) als auch der Ansaugleitung in Verbindung steht, wobei die Strömungsrichtungen des Kühlmittels in dem ersten Kühlmittel-Strömungsweg (143a) und dem zweiten Kühlmittel-Strömungsweg (143b) entgegengesetzt sind,
    dadurch gekennzeichnet, dass die Rückführungsleitung (146) einen Rückführungsleitungskörper, eine erste Verbindungsleitung (148) und eine zweite Verbindungsleitung (147) umfasst, ein Ende der ersten Verbindungsleitung (148) mit dem Rückführungsleitungskörper in Verbindung steht und das andere Ende der ersten Verbindungsleitung (148) mit einem Mitteldruck-Ansauganschluss des Kompressors (110) in Verbindung steht, der Rückführungsleitungskörper oder die erste Verbindungsleitung (148) mit einem ersten Steuerventil (133) versehen ist und ein Ende der zweiten Verbindungsleitung (147) mit dem Rückführungsleitungskörper in Verbindung steht und das andere Ende der zweiten Verbindungsleitung (147) mit der Ansaugleitung in Verbindung steht und die zweite Verbindungsleitung (147) mit einem zweiten Steuerventil (149) versehen ist.
  2. Klimaanlage nach Anspruch 1, wobei: die Kühlmittelbrücke (600) einen ersten Anschluss (610), einen zweiten Anschluss (620) und einen Kühlmitteldurchlass aufweist, der bewirkt, dass der erste Anschluss (610) mit dem zweiten Anschluss (620) in Verbindung steht, und die Kühlmittelbrücke (600) durch den ersten Anschluss (610) und den zweiten Anschluss (620) mit der ersten Rohrleitung (140) verbunden ist.
  3. Klimaanlage nach Anspruch 2, wobei: die Kühlmittelbrücke (600) einen dritten Anschluss (630) und einen vierten Anschluss (640) aufweist, die zwei Enden des ersten Kühlmittel-Strömungsweges (143a) mit dem dritten Anschluss (630) beziehungsweise dem vierten Anschluss (640) verbunden sind, der erste Anschluss (610) durch einen ersten Brückenabschnitt (650), der ein unidirektionales Strömen von Fluid von dem ersten Anschluss (610) zu dem dritten Anschluss (630) ermöglicht, mit dem dritten Anschluss (630) in Verbindung steht, der dritte Anschluss (630) durch einen zweiten Brückenabschnitt (660), der ein unidirektionales Strömen von Fluid von dem zweiten Anschluss (620) zu dem dritten Anschluss (630) ermöglicht, mit dem zweiten Anschluss (620) in Verbindung steht, der zweite Anschluss (620) durch einen dritten Brückenabschnitt (670), der ein unidirektionales Strömen von Fluid von dem vierten Anschluss (640) zu dem zweiten Anschluss (620) ermöglicht, mit dem vierten Anschluss (640) in Verbindung steht und der vierte Anschluss (640) durch einen vierten Brückenabschnitt (680), der ein unidirektionales Strömen von Fluid von dem vierten Anschluss (640) zu dem ersten Anschluss (610) ermöglicht, mit dem ersten Anschluss (610) in Verbindung steht.
  4. Klimaanlage nach Anspruch 2, wobei: die Kühlmittelbrücke (600) einen dritten Anschluss (630) und einen vierten Anschluss (640) aufweist, die zwei Enden des ersten Kühlmittel-Strömungsweges (143a) mit dem dritten Anschluss (630) beziehungsweise dem vierten Anschluss (640) verbunden sind, der erste Anschluss (610) durch einen ersten Brückenabschnitt (650), der ein unidirektionales Strömen von Fluid von dem dritten Anschluss (630) zu dem ersten Anschluss (610) ermöglicht, mit dem dritten Anschluss (630) in Verbindung steht, der dritte Anschluss (630) durch einen zweiten Brückenabschnitt (660), der ein unidirektionales Strömen von Fluid von dem dritten Anschluss (630) zu dem zweiten Anschluss (620) ermöglicht, mit dem zweiten Anschluss (620) in Verbindung steht, der zweite Anschluss (620) durch einen dritten Brückenabschnitt (670), der ein unidirektionales Strömen von Fluid von dem zweiten Anschluss (620) zu dem vierten Anschluss (640) ermöglicht, mit dem vierten Anschluss (640) in Verbindung steht und der vierte Anschluss (640) durch einen vierten Brückenabschnitt (680), der ein unidirektionales Strömen von Fluid von dem ersten Anschluss (610) zu dem vierten Anschluss (640) ermöglicht, mit dem ersten Anschluss (610) in Verbindung steht.
  5. Klimaanlage nach Anspruch 4, wobei der erste Brückenabschnitt (650), der zweite Brückenabschnitt (660), der dritte Brückenabschnitt (670) und der vierte Brückenabschnitt (680) jeweils mit einem Rückschlagventil (690) versehen sind.
  6. Klimaanlage nach Anspruch 1, wobei die Flüssigkeitsaufnahmeleitung (145) mit einem Flüssigkeitsaufnahme-Drosselventil (144) versehen ist.
  7. Klimaanlage nach Anspruch 1, wobei: ein Einlassende der Flüssigkeitsaufnahmeleitung (145) zwischen dem Vorwärmer (143) und dem außenseitigen Wärmetauscher mit der ersten Rohrleitung (140) in Verbindung steht oder ein Einlassende der Flüssigkeitsaufnahmeleitung (145) zwischen dem Vorwärmer (143) und dem ersten Innendrosselregler mit der ersten Rohrleitung (140) in Verbindung steht.
  8. Klimaanlage nach Anspruch 1, wobei ein Einlassende der Flüssigkeitsaufnahmeleitung (145) an einer Kreuzung mit der ersten Rohrleitung (140) einen Flüssigkeitsaufnahmeanschluss (840) aufweist, wobei sich der Flüssigkeitsaufnahmeanschluss (840) unter der ersten Rohrleitung (140) befindet.
  9. Klimaanlage nach Anspruch 8, ferner Folgendes umfassend: eine Flüssigkeitsaufnahmestruktur (800), die Folgendes umfasst: eine Flüssigkeitsaufnahmekammer (810), einen ersten Kühlmittelanschluss (830), der mit der Flüssigkeitsaufnahmekammer (810) in Verbindung steht, einen zweiten Kühlmittelanschluss (820), der mit der Flüssigkeitsaufnahmekammer (810) in Verbindung steht, und einen Flüssigkeitsaufnahmeanschluss (840), der mit der Flüssigkeitsaufnahmekammer (810) in Verbindung steht, wobei sich der Flüssigkeitsaufnahmeanschluss (840) unter dem ersten Kühlmittelanschluss (830) und dem zweiten Kühlmittelanschluss (820) befindet.
  10. Klimaanlage nach Anspruch 1, ferner Folgendes umfassend: einen zweiten Wärmetauscher (210), einen zweiten Drosselregler (230), eine Zweigleitung (112), die von der Ablassleitung (111) abzweigt, und eine dritte Rohrleitung (160), die einen ersten Schnittpunkt (211) der ersten Rohrleitung, den zweiten Drosselregler (230), den zweiten Wärmetauscher (210) und die Zweigleitung (112) in Reihe verbindet, wobei sich der erste Schnittpunkt (211) zwischen dem ersten Drosselregler (240) und dem Außenwärmetauscher befindet, sich der Vorwärmer (143) zwischen dem ersten Schnittpunkt (211) und dem Außenwärmetauscher an der ersten Rohrleitung (140) befindet.
  11. Klimaanlage nach Anspruch 10, ferner Folgendes umfassend: eine Kopplungsleitung (114), ein drittes Steuerventil (310), das an der Zweigleitung (112) angeordnet ist, um das Öffnen und Schließen der Zweigleitung (112) zu steuern, und ein viertes Steuerventil (320), das an der Kopplungsleitung (114) angeordnet ist, um das Öffnen und Schließen der Kopplungsleitung (114) zu steuern, wobei die dritte Rohrleitung (160) mit der Zweigleitung (112) in Verbindung steht, die dritte Rohrleitung (160) durch die Kopplungsleitung (114) mit der Niederdruck-Ansaugleitung (113) oder mit der zweiten Rohrleitung (150) in Verbindung steht, ferner optional Folgendes umfassend: eine zweite Schaltvorrichtung (132), die in der Lage ist, zwischen einem dritten Schaltzustand der zweiten Schaltvorrichtung (132), in dem die zweite Schaltvorrichtung (132) bewirkt, dass die dritte Rohrleitung (160) mit der Zweigleitung (112) in Verbindung steht, und einem vierten Schaltzustand der zweiten Schaltvorrichtung (132), in dem die zweite Schaltvorrichtung (132) bewirkt, dass die dritte Rohrleitung (160) mit der Ansaugleitung in Verbindung steht, umzuschalten.
  12. Klimaanlage nach Anspruch 1, ferner einen außenseitigen Drosselregler (142) umfassend, wobei sich der außenseitige Drosselregler (142) zwischen dem Vorwärmer (143) und dem außenseitigen Wärmetauscher an der ersten Rohrleitung (140) befindet.
  13. Klimaanlage nach Anspruch 1, ferner Folgendes umfassend: eine erste Verbindungsleitung (260), die von einem zweiten Schnittpunkt (212) der ersten Rohrleitung (140) abzweigt, wobei sich der zweite Schnittpunkt (212) zwischen dem ersten Drosselregler (240) und dem Außenwärmetauscher befindet, eine zweite Verbindungsleitung (250), die von der zweiten Rohrleitung (150) abzweigt, und mehrere Inneneinheiten (200), die mit der ersten Verbindungsleitung (260) und der zweiten Verbindungsleitung (250) parallel verbunden sind.
  14. Klimaanlage nach einem der Ansprüche 1 bis 13, wobei der Vorwärmer (143) Folgendes umfasst: einen Plattenwärmetauscher oder einen Doppelrohrwärmetauscher, der ein erstes Ende (510) und ein zweites Ende (520) aufweist, die einander gegenüber bereitgestellt sind, wobei: der erste Kühlmittel-Strömungsweg (143a) durch das erste Ende (510) ein- und durch das zweite Ende (520) austritt und der zweite Kühlmittel-Strömungsweg (143b) durch das zweite Ende (520) ein- und durch das erste Ende (510) austritt oder der erste Kühlmittel-Strömungsweg (143a) durch das zweite Ende (520) ein- und durch das erste Ende (510) austritt und der zweite Kühlmittel-Strömungsweg (143b) durch das erste Ende (510) ein- und durch das zweite Ende (520) austritt.
EP20882824.4A 2019-10-28 2020-03-13 Klimaanlage Active EP4008973B1 (de)

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CN201921830849.6U CN211177490U (zh) 2019-10-28 2019-10-28 空调器
CN201911034323.1A CN112797658A (zh) 2019-10-28 2019-10-28 空调器
PCT/CN2020/079187 WO2021082331A1 (zh) 2019-10-28 2020-03-13 空调器

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