CN110822755A - Heat pump system using non-azeotropic refrigerant mixture - Google Patents

Heat pump system using non-azeotropic refrigerant mixture Download PDF

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Publication number
CN110822755A
CN110822755A CN201911181191.5A CN201911181191A CN110822755A CN 110822755 A CN110822755 A CN 110822755A CN 201911181191 A CN201911181191 A CN 201911181191A CN 110822755 A CN110822755 A CN 110822755A
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China
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working medium
boiling working
medium loop
low
compressor
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CN201911181191.5A
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王天舒
吴运运
王颖
杨奕
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Jiangsu Tianshu Electric Appliance Co Ltd
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Jiangsu Tianshu Electric Appliance Co Ltd
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Priority to CN201911181191.5A priority Critical patent/CN110822755A/en
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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
    • F25B7/00—Compression machines, plants or systems, with cascade operation, i.e. with two or more circuits, the heat from the condenser of one circuit being absorbed by the evaporator of the next circuit
    • 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
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • F25B40/06—Superheaters
    • 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
    • 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

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Drying Of Solid Materials (AREA)

Abstract

A heat pump system using a non-azeotropic refrigerant mixture is used for realizing drying and deep dehumidification, and the non-azeotropic refrigerant is discharged from an exhaust port of a compressor (1), and then enters a first condenser (2) and a liquid storage gas separator (3) respectively to form gas-liquid separation of a low-boiling working medium and a high-boiling working medium; the condensed and liquefied high-boiling working medium returns to the compressor (1) through a high-boiling working medium loop connected with a liquid outlet of the liquid storage gas separator (3), and the uncondensed and liquefied low-boiling working medium returns to the compressor (1) through a low-boiling working medium loop connected with a gas outlet of the liquid storage gas separator (3). The heat pump system utilizing the non-azeotropic refrigerant mixture disclosed by the invention forms respective responses of three requirements of primary independent drying, secondary drying and dehumidification and tertiary deep dehumidification or sequential secondary or tertiary responses through matching the high-boiling working medium loop with the low-boiling working medium loop in the double-evaporation refrigeration system.

Description

Heat pump system using non-azeotropic refrigerant mixture
Technical Field
The invention belongs to the field of heat pump dehumidification, and particularly relates to a heat pump system utilizing a non-azeotropic refrigerant mixture.
Background
For some production processes and article storage in industrial production, such as a clean room in the pharmaceutical industry or an electronic product production line of a processor, a camera and the like of a mobile phone, the air humidity is strictly controlled and adjusted, and the guarantee of low humidity is an important content for ensuring the product quality; meanwhile, too high relative humidity is not beneficial to the long-term stable operation of the precision instrument. In some underground building storage rooms, dehumidification of air is often the primary task undertaken by air conditioning systems. Under the low-temperature working condition, the dehumidification amount of the evaporator is reduced along with the reduction of the temperature of the inlet air wet bulb in the closed space, the reduction degree has a threshold value, the temperature of the inlet air wet bulb in the closed space is not reduced after being lower than a certain temperature, and the temperature of the outlet air wet bulb is lower than the dew point temperature of saturated wet air. How to realize the dehumidification based on the heat pump at low temperature to respond to the demand of low-temperature dehumidification becomes the problem that needs to be solved.
The application numbers are: 201610020342.9, the invention discloses a self-overlapping vapor compression type refrigeration cycle system with an evaporation subcooler, which comprises a compressor, a condenser and a gas-liquid separator which are connected in sequence, wherein the outlet of the gas-liquid separator is divided into two paths, one path of saturated refrigerant liquid outlet is connected with the inlet of a first throttling mechanism, and the outlet of the first throttling mechanism is connected with the evaporation side inlet of the evaporation condenser; the other path of saturated refrigerant gas outlet is connected with the condensation side inlet of the evaporation condenser, the condensation side outlet of the evaporation condenser is connected with the high-temperature side inlet of the evaporation subcooler, the high-temperature side outlet of the evaporation subcooler is connected with the inlet of the second throttling mechanism, the outlet of the second throttling mechanism is connected with the inlet of the evaporator, the outlet of the evaporator is connected with the evaporation side inlet of the evaporation subcooler, the evaporation side outlet of the evaporation subcooler is converged with the evaporation side outlet of the evaporation condenser, and then the evaporation side outlet is connected with the air suction port of the compressor to finish the circulation; the invention effectively improves the performance of the auto-cascade vapor compression type refrigeration cycle system by using one evaporation subcooler in the auto-cascade refrigeration cycle system.
The application numbers are: 201610167369.0 discloses a tuna and fishing boat waste heat recovery and injection type self-overlapping refrigerating system, which comprises an injector, a condenser, a gas-liquid separator, a low-temperature stage dry filter, a high-temperature stage throttling valve, an evaporative condenser, a low-temperature stage dry filter, a low-temperature stage throttling valve, an evaporator, a heat regenerator, a low-temperature stage electric regulating valve, a high-temperature stage electric regulating valve, an exhaust gas turbocharger, a circulating pump, a generator, a diesel engine and a generator. An ejector is arranged between the evaporative condenser and the condenser, and an exhaust gas turbocharger is arranged between the ejector and the evaporative condenser.
The application numbers are: 201610473584.3, discloses a self-cascade refrigeration system for preventing low-temperature frozen oil and a control method thereof, which comprises a compression refrigeration device, an intermediate heat regenerator, a first throttling unit and an evaporator unit; the heat flow inlet of the intermediate heat regenerator is connected with the first outlet of the compression refrigerating device through a pipeline, and the heat flow outlet of the intermediate heat regenerator is connected to the inlet of the evaporator unit through a first throttling unit; a first cold flow inlet of the intermediate heat regenerator is communicated with an outlet of the evaporator unit through a pipeline, and a cold flow outlet of the intermediate heat regenerator is connected with an inlet of the compression refrigerating device through a pipeline; a second outlet of the compression refrigerating device is communicated with a second cold flow inlet of the intermediate heat regenerator through an anti-freezing oil unit; after the system is started, the anti-freezing oil unit is started to enter a bidirectional conduction state; and after the system is closed, the anti-freezing oil unit is closed to enter a one-way conduction state.
Disclosure of Invention
In order to solve the problems, the invention provides a heat pump system using a non-azeotropic refrigerant mixture, which has the following technical scheme:
a heat pump system using non-azeotropic refrigerant mixture for drying and deep dehumidification, which is characterized in that:
the non-azeotropic refrigerant is discharged from an exhaust port of the compressor (1), and then enters the first condenser (2) and the liquid storage gas separator (3) respectively to form gas-liquid separation of low-boiling working medium and high-boiling working medium;
the condensed and liquefied high-boiling working medium returns to the compressor (1) through a high-boiling working medium loop connected with a liquid outlet of the liquid storage gas separator (3),
the low-boiling working medium which is not condensed and liquefied returns to the compressor (1) through a low-boiling working medium loop which is connected with a gas outlet of the liquid storage gas separator (3);
the low-boiling working medium loop is matched with the high-boiling working medium loop to form respective response of three requirements of primary drying, secondary drying and dehumidification and tertiary deep dehumidification in the double-evaporation refrigeration system or sequential secondary or tertiary response.
A heat pump system using a non-azeotropic refrigerant mixture according to the present invention is characterized in that:
the compressor is an enhanced vapor injection compressor, and an exhaust port, a middle cavity air inlet and an air suction port are arranged on the compressor;
the high-boiling working medium loop comprises a first high-boiling working medium loop and a second high-boiling working medium loop which are formed between an exhaust port and an air suction port of the compressor;
the low-boiling working medium loop comprises a first low-boiling working medium loop and a second low-boiling working medium loop which are formed between an exhaust port of the compressor and an air inlet of the middle cavity.
A heat pump system using a non-azeotropic refrigerant mixture according to the present invention is characterized in that:
the first high-boiling working medium loop forms first-stage drying in the double-evaporation refrigeration system; the first low-boiling working medium loop is matched with the first high-boiling working medium loop to form a heat pump cycle of primary drying;
the second low-boiling working medium loop and the second high-boiling working medium loop cooperate to form a third-stage deep dehumidification heat pump cycle;
the first low-boiling working medium loop, the second low-boiling working medium loop, the first high-boiling working medium loop and the second high-boiling working medium loop cooperate together to form a second-stage drying and dehumidifying heat pump cycle.
A heat pump system using a non-azeotropic refrigerant mixture according to the present invention is characterized in that:
the first low-boiling working medium loop is composed of a second condenser (4), a heat regenerator (5), a second electronic expansion valve (6), a second evaporator (7) and a gas-liquid separator (8) which are sequentially connected behind the first condenser (2) and the liquid storage gas separator (3);
the second low-boiling working medium loop is composed of a self-cascade heat exchanger (9), a heat regenerator (5), a second electronic expansion valve (6), a second evaporator (7) and a gas-liquid separator (8) which are sequentially connected behind the first condenser (2) and the liquid storage gas separator (3);
the first high-boiling working medium loop is composed of a first electronic expansion valve (10), a first evaporator (11) and a heat regenerator (5) which are sequentially connected behind a first condenser (2) and a liquid and gas storage separator (3);
the second high-boiling working medium loop is composed of a first electronic expansion valve (10), a self-cascade heat exchanger (9) and a heat regenerator (5) which are sequentially connected behind the first condenser (2) and the liquid and gas storage separator (3).
A heat pump system using a non-azeotropic refrigerant mixture according to the present invention is characterized in that:
the gas discharge end of the liquid storage type gas separator (3) is connected with a working medium inlet of the second condenser (4) and a first inlet of the self-cascade heat exchanger (9) through a first three-way valve (12);
the discharge port of the first electronic expansion valve (10) is connected with a second inlet of the self-cascade heat exchanger (9) and a working medium inlet of the first evaporator (11) through a second three-way valve (13);
a working medium outlet of the second condenser (4) is connected with a first outlet of the self-cascade heat exchanger (9) and a first inlet of the heat regenerator through a third three-way valve (14);
and a working medium outlet of the first evaporator (11) is connected with a second outlet of the self-cascade heat exchanger (9) and a second inlet of the heat regenerator through a fourth three-way valve (15).
According to the heat pump system utilizing the non-azeotropic refrigerant mixture, the self-overlapping structure concept and the enhanced vapor injection structure concept are infiltrated into the system and are constructively combined, so that the heat pump system capable of responding to drying, deep dehumidification and simultaneous response is built, and the problem of overhigh exhaust temperature caused by overlarge pressure ratio can be solved, so that the energy consumption is reduced, and the reliability of the system is guaranteed.
Drawings
FIG. 1 is a block diagram schematically illustrating the structure of the present invention;
fig. 2 is a schematic structural diagram of the present invention.
In the figure, the position of the upper end of the main shaft,
1-a compressor;
2-a first condenser;
3-liquid storage and air separator;
4-a second condenser;
5-a heat regenerator;
6-a second electronic expansion valve;
7-a second evaporator;
8-a gas-liquid separator;
9-a self-cascade heat exchanger;
10-a first electronic expansion valve;
11-a first evaporator;
12-a first three-way valve;
13-a second three-way valve;
14-a third three-way valve;
15-fourth three-way valve.
Detailed Description
Hereinafter, a heat pump system using a non-azeotropic refrigerant mixture according to the present invention will be described in further detail with reference to the drawings and embodiments.
As shown in fig. 1 and 2, a heat pump system using a non-azeotropic refrigerant mixture is used for realizing drying and deep dehumidification, wherein the non-azeotropic refrigerant is discharged from an exhaust port of a compressor (1), and then enters a first condenser (2) and a liquid storage gas separator (3) respectively to form gas-liquid separation of a low-boiling working medium and a high-boiling working medium;
the condensed and liquefied high-boiling working medium returns to the compressor (1) through a high-boiling working medium loop connected with a liquid outlet of the liquid storage gas separator (3),
the low-boiling working medium which is not condensed and liquefied returns to the compressor (1) through a low-boiling working medium loop which is connected with a gas outlet of the liquid storage gas separator (3);
the low-boiling working medium loop is matched with the high-boiling working medium loop to form respective response of three requirements of primary drying, secondary drying and dehumidification and tertiary deep dehumidification in the double-evaporation refrigeration system or sequential secondary or tertiary response.
Wherein the content of the first and second substances,
the compressor is an enhanced vapor injection compressor, and an exhaust port, a middle cavity air inlet and an air suction port are arranged on the compressor;
the high-boiling working medium loop comprises a first high-boiling working medium loop and a second high-boiling working medium loop which are formed between an exhaust port and an air suction port of the compressor;
the low-boiling working medium loop comprises a first low-boiling working medium loop and a second low-boiling working medium loop which are formed between an exhaust port of the compressor and an air inlet of the middle cavity.
Wherein the content of the first and second substances,
the first high-boiling working medium loop forms first-stage drying in the double-evaporation refrigeration system; the first low-boiling working medium loop is matched with the first high-boiling working medium loop to form a heat pump cycle of primary drying;
the second low-boiling working medium loop and the second high-boiling working medium loop cooperate to form a third-stage deep dehumidification heat pump cycle;
the first low-boiling working medium loop, the second low-boiling working medium loop, the first high-boiling working medium loop and the second high-boiling working medium loop cooperate together to form a second-stage drying and dehumidifying heat pump cycle.
Wherein the content of the first and second substances,
the first low-boiling working medium loop is composed of a second condenser (4), a heat regenerator (5), a second electronic expansion valve (6), a second evaporator (7) and a gas-liquid separator (8) which are sequentially connected behind the first condenser (2) and the liquid storage gas separator (3);
the second low-boiling working medium loop is composed of a self-cascade heat exchanger (9), a heat regenerator (5), a second electronic expansion valve (6), a second evaporator (7) and a gas-liquid separator (8) which are sequentially connected behind the first condenser (2) and the liquid storage gas separator (3);
the first high-boiling working medium loop is composed of a first electronic expansion valve (10), a first evaporator (11) and a heat regenerator (5) which are sequentially connected behind a first condenser (2) and a liquid and gas storage separator (3);
the second high-boiling working medium loop is composed of a first electronic expansion valve (10), a self-cascade heat exchanger (9) and a heat regenerator (5) which are sequentially connected behind the first condenser (2) and the liquid and gas storage separator (3).
Wherein the content of the first and second substances,
the gas discharge end of the liquid storage type gas separator (3) is connected with a working medium inlet of the second condenser (4) and a first inlet of the self-cascade heat exchanger (9) through a first three-way valve (12);
the discharge port of the first electronic expansion valve (10) is connected with a second inlet of the self-cascade heat exchanger (9) and a working medium inlet of the first evaporator (11) through a second three-way valve (13);
a working medium outlet of the second condenser (4) is connected with a first outlet of the self-cascade heat exchanger (9) and a first inlet of the heat regenerator through a third three-way valve (14);
and a working medium outlet of the first evaporator (11) is connected with a second outlet of the self-cascade heat exchanger (9) and a second inlet of the heat regenerator through a fourth three-way valve (15).
Working principle and embodiment
When the drying is needed, the high-temperature and high-pressure refrigerant gas after being compressed after the compressor is started circulates to the first condenser 2, the refrigerant gas which is not condensed enters the second condenser 7 after passing through the liquid storage type gas separator 3 to be condensed into refrigerant liquid, then enters the economizer (heat regenerator) 6 again for heat exchange, is throttled by the second electronic expansion valve 8, enters the second evaporator 9 to be evaporated and absorb heat, and finally enters the middle cavity of the compressor 1; and the high-boiling refrigerant passes through the liquid storage type air separator 3, enters the first evaporator 5 for evaporation and heat absorption after the throttling action of the first electronic expansion valve 4, and finally returns to the air suction end of the compressor 1.
When drying and dehumidifying are needed; the refrigerant after being compressed after the compressor 1 is started circulates to the first condenser 2, and the refrigerant gas which is not condensed passes through the liquid storage type gas separator 3; through the adjustment of the three-way proportional valve 11, a part of the refrigerant enters the self-cascade heat exchanger 12 and is condensed into refrigerant liquid, and then the refrigerant liquid enters the economizer again for heat exchange; the other part of the refrigerant enters a second condenser 7 to be condensed into refrigerant liquid, and then enters an economizer (a heat regenerator) 6 again for heat exchange; after heat exchange is completed by the heat regenerator, the heat is throttled by the second electronic expansion valve 8, enters the second evaporator 9 for evaporation and heat absorption, and finally enters the middle cavity of the compressor 1; after passing through the liquid storage type gas separator 3, the high-boiling refrigerant passes through the throttling action of the first electronic expansion valve 4, one part of the high-boiling refrigerant enters the self-cascade heat exchanger 12 through the three-way proportional valve 11, the other part of the high-boiling refrigerant enters the first evaporator 5, the high-boiling refrigerant passing through the self-cascade heat exchanger 12 and the first evaporator 5 simultaneously enters the heat regenerator for heat exchange, and the high-boiling refrigerant gas after heat exchange is finished by the heat regenerator 6 returns to the air suction end of the compressor.
When deep dehumidification is needed, the compressed refrigerant circulates to the first condenser 2 after the compressor 1 is started, uncondensed refrigerant gas enters the self-cascade heat exchanger 12 through the liquid storage type gas separator 3 and is condensed into refrigerant liquid, then the refrigerant liquid enters the economizer 6 again to realize supercooling, and the refrigerant liquid is throttled by the second electronic expansion valve 8, evaporated and absorbed by the second evaporator 9 and finally enters the middle cavity of the compressor 1; and the high-boiling refrigerant passes through the liquid storage type gas separator 3, enters the self-cascade heat exchanger 12 after the throttling action of the first electronic expansion valve 4, completes heat exchange, enters the economizer 6 for further heat exchange to realize overheating, and the overheated refrigerant gas returns to the suction end of the compressor.
In the embodiment, when drying is required, the compressor performs frequency-up regulation; when drying and dehumidifying are needed, the compressor performs frequency reduction regulation; when deep dehumidification is required, the compressor is further slowed down.
According to the heat pump system utilizing the non-azeotropic refrigerant mixture, the self-overlapping structure concept and the enhanced vapor injection structure concept are infiltrated into the system and are constructively combined, so that the heat pump system capable of responding to drying, deep dehumidification and simultaneous response is built, and the problem of overhigh exhaust temperature caused by overlarge pressure ratio can be solved, so that the energy consumption is reduced, and the reliability of the system is guaranteed.

Claims (5)

1. A heat pump system using non-azeotropic refrigerant mixture for drying and deep dehumidification, which is characterized in that:
the non-azeotropic refrigerant is discharged from an exhaust port of the compressor (1), and then enters the first condenser (2) and the liquid storage gas separator (3) respectively to form gas-liquid separation of low-boiling working medium and high-boiling working medium;
the condensed and liquefied high-boiling working medium returns to the compressor (1) through a high-boiling working medium loop connected with a liquid outlet of the liquid storage gas separator (3),
the low-boiling working medium which is not condensed and liquefied returns to the compressor (1) through a low-boiling working medium loop which is connected with a gas outlet of the liquid storage gas separator (3);
the low-boiling working medium loop is matched with the high-boiling working medium loop to form respective response of three requirements of primary drying, secondary drying and dehumidification and tertiary deep dehumidification in the double-evaporation refrigeration system or sequential secondary or tertiary response.
2. A heat pump system using a zeotropic refrigerant mixture as set forth in claim 1, wherein:
the compressor is an enhanced vapor injection compressor, and an exhaust port, a middle cavity air inlet and an air suction port are arranged on the compressor;
the high-boiling working medium loop comprises a first high-boiling working medium loop and a second high-boiling working medium loop which are formed between an exhaust port and an air suction port of the compressor;
the low-boiling working medium loop comprises a first low-boiling working medium loop and a second low-boiling working medium loop which are formed between an exhaust port of the compressor and an air inlet of the middle cavity.
3. A heat pump system using a zeotropic refrigerant mixture as set forth in claim 2, wherein:
the first high-boiling working medium loop forms first-stage drying in the double-evaporation refrigeration system; the first low-boiling working medium loop is matched with the first high-boiling working medium loop to form a heat pump cycle of primary drying;
the second low-boiling working medium loop and the second high-boiling working medium loop cooperate to form a third-stage deep dehumidification heat pump cycle;
the first low-boiling working medium loop, the second low-boiling working medium loop, the first high-boiling working medium loop and the second high-boiling working medium loop cooperate together to form a second-stage drying and dehumidifying heat pump cycle.
4. A heat pump system using a non-azeotropic refrigerant mixture according to claim 2 or 3, wherein:
the first low-boiling working medium loop is composed of a second condenser (4), a heat regenerator (5), a second electronic expansion valve (6), a second evaporator (7) and a gas-liquid separator (8) which are sequentially connected behind the first condenser (2) and the liquid storage gas separator (3);
the second low-boiling working medium loop is composed of a self-cascade heat exchanger (9), a heat regenerator (5), a second electronic expansion valve (6), a second evaporator (7) and a gas-liquid separator (8) which are sequentially connected behind the first condenser (2) and the liquid storage gas separator (3);
the first high-boiling working medium loop is composed of a first electronic expansion valve (10), a first evaporator (11) and a heat regenerator (5) which are sequentially connected behind a first condenser (2) and a liquid and gas storage separator (3);
the second high-boiling working medium loop is composed of a first electronic expansion valve (10), a self-cascade heat exchanger (9) and a heat regenerator (5) which are sequentially connected behind the first condenser (2) and the liquid and gas storage separator (3).
5. A heat pump system using a zeotropic refrigerant mixture as set forth in claim 4, wherein:
the gas discharge end of the liquid storage type gas separator (3) is connected with a working medium inlet of the second condenser (4) and a first inlet of the self-cascade heat exchanger (9) through a first three-way valve (12);
the discharge port of the first electronic expansion valve (10) is connected with a second inlet of the self-cascade heat exchanger (9) and a working medium inlet of the first evaporator (11) through a second three-way valve (13);
a working medium outlet of the second condenser (4) is connected with a first outlet of the self-cascade heat exchanger (9) and a first inlet of the heat regenerator through a third three-way valve (14);
and a working medium outlet of the first evaporator (11) is connected with a second outlet of the self-cascade heat exchanger (9) and a second inlet of the heat regenerator through a fourth three-way valve (15).
CN201911181191.5A 2019-11-27 2019-11-27 Heat pump system using non-azeotropic refrigerant mixture Pending CN110822755A (en)

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Application Number Priority Date Filing Date Title
CN201911181191.5A CN110822755A (en) 2019-11-27 2019-11-27 Heat pump system using non-azeotropic refrigerant mixture

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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN112011311A (en) * 2020-08-13 2020-12-01 珠海格力电器股份有限公司 Non-azeotropic environment-friendly refrigerant, preparation method thereof and dehumidification system
CN112923680A (en) * 2021-02-22 2021-06-08 陕西理工大学 Air source heat pump drying system capable of operating independently
WO2021213548A1 (en) * 2020-06-01 2021-10-28 青岛经济技术开发区海尔热水器有限公司 Heat exchange device, water heater, and air conditioner

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2021213548A1 (en) * 2020-06-01 2021-10-28 青岛经济技术开发区海尔热水器有限公司 Heat exchange device, water heater, and air conditioner
CN112011311A (en) * 2020-08-13 2020-12-01 珠海格力电器股份有限公司 Non-azeotropic environment-friendly refrigerant, preparation method thereof and dehumidification system
CN112011311B (en) * 2020-08-13 2021-06-18 珠海格力电器股份有限公司 Non-azeotropic environment-friendly refrigerant, preparation method thereof and dehumidification system
CN112923680A (en) * 2021-02-22 2021-06-08 陕西理工大学 Air source heat pump drying system capable of operating independently

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