CN111412674A - Total-heat frostless air source heat pump system based on two-stage centrifugal compressor - Google Patents

Total-heat frostless air source heat pump system based on two-stage centrifugal compressor Download PDF

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Publication number
CN111412674A
CN111412674A CN202010248510.6A CN202010248510A CN111412674A CN 111412674 A CN111412674 A CN 111412674A CN 202010248510 A CN202010248510 A CN 202010248510A CN 111412674 A CN111412674 A CN 111412674A
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China
Prior art keywords
air
loop
heat exchanger
valve
input end
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Pending
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CN202010248510.6A
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Chinese (zh)
Inventor
张小松
朱赤
季建周
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Nanjing Dongda Intelligent Environmental Energy Research Institute Co ltd
Southeast University
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Nanjing Dongda Intelligent Environmental Energy Research Institute Co ltd
Southeast University
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Application filed by Nanjing Dongda Intelligent Environmental Energy Research Institute Co ltd, Southeast University filed Critical Nanjing Dongda Intelligent Environmental Energy Research Institute Co ltd
Priority to CN202010248510.6A priority Critical patent/CN111412674A/en
Publication of CN111412674A publication Critical patent/CN111412674A/en
Pending legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/10—Compression machines, plants or systems with non-reversible cycle with multi-stage compression
    • 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
    • F25B30/00—Heat pumps
    • F25B30/02—Heat pumps of the compression type
    • 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
    • F25B30/00—Heat pumps
    • F25B30/06—Heat pumps characterised by the source of low potential heat
    • 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
    • F25B47/00—Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass
    • F25B47/006—Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass for preventing frost

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Air Conditioning Control Device (AREA)

Abstract

The invention discloses a full-heat frostless air source heat pump system based on a two-stage centrifugal compressor, which comprises a solution loop, a water loop, a refrigerant loop and an air loop. The invention takes outdoor air as a low-grade heat source and absorbs sensible heat and latent heat from the outdoor air by solution circulation. The invention adopts the two-stage centrifugal compressor, solves the problem caused by overhigh compression ratio in winter work, and ensures that the system can safely and stably run in severe outdoor environments such as minus 20 ℃ and the like; and an intercooler is adopted to reduce the running power of the water side in summer. The source side adopts centralized water/solution circulation to absorb sensible heat and latent heat from outdoor air, so that the frosting problem of a conventional air source heat pump is avoided; the R22 refrigerant cycle is used as the final heat delivery and distribution link.

Description

Total-heat frostless air source heat pump system based on two-stage centrifugal compressor
Technical Field
The invention belongs to the field of design and manufacture of heat pump systems, and particularly relates to a full-heat frostless air source heat pump system based on a two-stage centrifugal compressor
Background
The energy consumption of the current air conditioner accounts for more than 30% of the energy consumption of a building, and is necessary for the optimization of the air conditioning system technology in view of the national important strategy of energy conservation and emission reduction.
The common cold and heat source equipment in the building at present mainly comprises a water chilling unit, a boiler, an air source heat pump and a water and ground source heat pump. The coupling of the water chilling unit and the boiler is poor, the seasonal idleness rate is high, the boiler has low utilization rate of primary energy, and the environmental friendliness is poor. The water-ground source heat pump has high efficiency in winter and summer, but has high initial investment and is limited by geographical geological conditions.
The air source heat pump is mainly suitable for working conditions in winter, has high energy utilization rate and strong environmental friendliness, but also has some problems: the frosting problem often exists during the operation in winter, particularly in the hot summer and cold winter areas at the middle and lower reaches of Yangtze river in China, the frosting problem is particularly serious due to cold and moist winter, and the heat supply capacity and efficiency are influenced; the operation efficiency in summer is lower than that of a water chilling unit; under extreme weather conditions, the compressor pressure ratio is too big, leads to the operating efficiency to reduce, even the unit shuts down.
Patent publication No. CN201410156239.8 is a system for preventing frosting of air source heat pump water heater by solution dehumidification. The dehumidification concentrated solution is used for dehumidifying and drying air at the inlet of the evaporator, frost-free operation of the heat pump water heater is guaranteed, and when the dehumidification solution reaches the dehumidification limit, heat of the heat pump loop is used for regeneration. The system uses most of the heat for solution regeneration during the regeneration process, and the longer the regeneration time, the thermal comfort in the chamber is obviously reduced in the period of time.
Patent publication CN 107218644A is a serial frostless air source heat pump system based on regenerative heat recovery. An auxiliary heat pump circulation loop is introduced, the condensation heat of the system is used for regenerating the diluted solution, and the regenerated air after heat absorption flows through an evaporator of the heat supply heat pump in the closed air path circulation to complete the recovery of all heat. The regenerated heat of solution is totally recycled in the closed air path circulation process, and the energy efficiency of the system is improved. But the problems of over high compressor pressure ratio, insufficient heat supply capacity and low efficiency exist when the air conditioner is applied to the areas with lower outdoor temperature in winter.
Therefore, designing a set of air source heat pump system suitable for cold regions, operating at a low pressure ratio and having high energy efficiency becomes a problem to be solved urgently by those skilled in the art.
Disclosure of Invention
In order to solve the technical problems, the invention aims to provide a full-heat frostless air source heat pump system based on a two-stage centrifugal compressor, which adopts solution circulation at a source side to extract heat from air, avoids the problem of frosting of a conventional air source heat pump, adopts a closed air path to complete the recovery of all solution regeneration heat, uses the two-stage centrifugal compressor to reduce the single-stage pressure ratio of the compressor, ensures the safe and stable operation of the system in severe outdoor environments such as 20 ℃ below zero and the like, adopts incomplete intermediate cooling to treat throttled refrigerant, and reduces the power consumption of the heat pump.
The technical scheme of the invention is as follows:
the utility model provides a full fever type frostless air source heat pump system based on doublestage centrifugal compressor which characterized in that: comprises a solution loop, a water loop, a refrigerant loop and an air loop;
in the solution loop, the input end of a solution pump (20) is connected to a first plate heat exchanger (10) in the loop, and a solution tower (22) is connected with the solution pump (20) through a second flowmeter (21) and is connected with the first plate heat exchanger (10) through a third valve (23) to form the loop;
in the refrigerant loop, the output end of the second plate heat exchanger (1) is connected with the first output end of the four-way reversing valve (2) and the input end of the low-pressure compressor (3), the output end of the low-pressure compressor (3) is connected with the first input end (4) of the intercooler, the input end of the high-pressure compressor (5) is connected with the output end (4) of the intercooler, the output end of the high-pressure compressor (5) is connected with the second output end of the four-way reversing valve (2) and the input end of the second finned coil heat exchanger (6), the first branch of the output end of the second finned coil heat exchanger (6) is connected with a first electronic expansion valve (7), and the second branch is connected with a first valve (8) and is connected with the first branch, and are connected in parallel to form two branches, the first branch is connected with a second input end (4) of the intercooler through a second valve (9), and the second branch flows through the intercooler (4) and is connected with the input end of the first plate heat exchanger (10). The output end of the first plate heat exchanger (10) is connected with the fourth valve (12) in parallel through a second electronic expansion valve (11) and is connected with the input end of the liquid storage tank (13). The output end of the liquid storage tank (13) is connected with the input end of a filter (14), and the filter (14) is connected with the input end of the second plate heat exchanger (1);
in the air loop, a first air valve (24) is an air pipe input end, and a third air valve (27) is an air pipe output end; the first branch is connected with the solution tower (22), the second finned coil heat exchanger (6) and the first fan (26) in sequence, and the second branch is connected with the second air valve (25) and the output end from the input end of the air pipe;
in the water loop, the input end of a water pump (15) is connected to the second plate type heat exchanger (1), the output end of the water pump (15) is connected with the input end of the second finned coil heat exchanger (17) through a first flow meter (16), and the output end of the second finned coil heat exchanger (17) is connected with the second plate type heat exchanger (1) through a fifth valve (18) to form the water loop.
Furthermore, the system takes outdoor air as a low-grade heat source, absorbs sensible heat and latent heat from the outdoor air through solution circulation, and is high in heat exchange efficiency.
Furthermore, a two-stage centrifugal compressor is adopted, the pressure ratio of the compressor is reduced, and the safe and stable operation of the system in severe outdoor environments such as 20 ℃ below zero is ensured.
Furthermore, an intercooler is used for carrying out incomplete intermediate cooling on low-pressure refrigerant steam generated by the low-pressure compressor and providing heat for the refrigerant after throttling and heat exchange.
In the invention, when the device runs in summer, the evaporative cooling cycle and the heat pump cycle continuously work, and the solution tower is filled with water. The solution loop exchanges heat with the refrigerant loop through the second plate heat exchanger, the water loop exchanges heat with the refrigerant loop through the second plate heat exchanger, the air loop exchanges heat with the refrigerant loop through the first finned coil heat exchanger, the air loop exchanges heat with the water loop through the second finned coil heat exchanger, and the air loop exchanges heat with the solution loop through the solution tower. The basic process is as follows: for a refrigerant loop, low-temperature and low-pressure refrigerants are compressed by a low-pressure compressor, then flow into an intercooler, are mixed with part of high-temperature refrigerants flowing out of a first finned coil heat exchanger, enter a high-pressure compressor for compression, then flow into the first finned coil heat exchanger through a four-way reversing valve to exchange heat with an air loop, pass through a first valve, flow into the intercooler, and are mixed with the low-pressure and low-temperature refrigerants, part of the high-temperature and high-pressure refrigerants flow through the intercooler for cooling, flow through the first plate heat exchanger to exchange heat with a solution loop, then flow through a second electronic expansion valve, a liquid storage tank and a filter, and flow through a second plate. For the solution loop, the solution is pumped into the solution tower through a solution pump, mixed with high-temperature air, and precooled. For an air loop, air enters an air supply pipeline from a first air valve, cooling water passing through a solution tower is evaporated, cooled and cooled, the supercooling degree is increased, water drops are attached to the air, the air passes through a first fin coil heat exchanger, and the water drops are attached to the first fin coil heat exchanger to evaporate and absorb heat.
During winter operation, the solution tower is filled with solution. In the heating mode, for a refrigerant loop, low-temperature and low-pressure refrigerants are compressed by a low-pressure compressor, then flow into an intercooler, are mixed with part of high-temperature refrigerants flowing out of a condenser, enter a high-pressure compressor for compression, then flow into a second plate heat exchanger through a four-way reversing valve to exchange heat with a water loop, release all heat to cooling water, flow through a filter, a liquid storage tank, a second electronic expansion valve, a first plate heat exchanger, the intercooler, a first valve and a second fin coil heat exchanger, and absorb heat from solution, the intercooler and ambient air. For the air loop, air enters the air supply pipeline from the first air valve and is dehumidified by the solution tower, so that frostless operation is realized. And in the regeneration mode, the first air valve and the second air valve are closed, the third air valve is opened, the condensed high-pressure medium-temperature refrigerant liquid transfers the condensed residual heat to the dilute solution in the first plate heat exchanger, the partial pressure of the vapor on the surface of the dilute solution is increased, and the air absorbs moisture and condenses out water on the surface of the first fin coil heat exchanger. Circulating in the air duct until the dilute solution becomes the required concentrated solution.
By the scheme, the invention at least has the following advantages:
1. the invention adopts two-stage centrifugal compression, reduces the single-stage pressure ratio of the compressor and ensures the safe and stable operation of the system in severe outdoor environments such as minus 20 ℃ and the like.
2. By adopting incomplete cooling in the middle, when the compressor runs in winter, the throttled refrigerant absorbs heat from the solution, the intercooler and the ambient air in sequence, the inlet temperature of the low-pressure compressor is increased, and the frosting risk caused by too low air temperature is avoided.
The foregoing description is only an overview of the technical solutions of the present invention, and in order to make the technical solutions of the present invention more clearly understood and to implement them in accordance with the contents of the description, the following detailed description is given with reference to the preferred embodiments of the present invention and the accompanying drawings.
Drawings
In order to more clearly illustrate the technical solutions of the embodiments of the present invention, the drawings needed to be used in the embodiments will be briefly described below, it should be understood that the following drawings only illustrate a certain embodiment of the present invention, and therefore should not be considered as limiting the scope, and for those skilled in the art, other related drawings can be obtained according to the drawings without inventive efforts.
Fig. 1 is a schematic diagram of a total-heat frostless air source heat pump system based on a two-stage centrifugal compressor, which comprises a solution loop, a water loop, a refrigerant loop and an air loop.
The figure shows that: a second plate heat exchanger 1; a four-way reversing valve 2; a low-pressure compressor 3; an intercooler 4; a high-pressure compressor 5; a first finned coil heat exchanger 6; a first electronic expansion valve 7; a first valve 8; a second valve 9; a first plate heat exchanger 10; a second electronic expansion valve 11; a fourth valve 12; a liquid storage tank 13; a filter 14; a water pump 15; a first flow meter 16; a second finned coil heat exchanger 17; a fifth valve 18; a second fan 19; a solution pump 20; a second flow meter 21; a solution tower 22; a third valve 23; a first air valve 24; a second air valve 25; a first fan 26; and a third air valve 27.
Detailed Description
The following detailed description of embodiments of the present invention is provided in connection with the accompanying drawings and examples. The following examples are intended to illustrate the invention but are not intended to limit the scope of the invention.
The invention comprises a solution loop, a water loop, a refrigerant loop and an air loop. Wherein the solution circuit comprises a first plate heat exchanger 10, a solution pump 20, a second flow meter 21, a solution tower 22, and a third valve 23. In the solution loop, the input end of a solution pump 20 is connected to the first plate heat exchanger 10 in the loop, and a solution tower 22 is connected to the solution pump 20 through a second flowmeter 21 and connected to the first plate heat exchanger 10 through a third valve 23 to form the loop. The refrigerant loop comprises a second plate heat exchanger 1, a four-way reversing valve 2, a low-pressure compressor 3, an intercooler 4, a high-pressure compressor 5, a second finned coil heat exchanger 6, a first electronic expansion valve 7, a first valve 8, a second valve 9, a first plate heat exchanger 10, a second electronic expansion valve 11, a fourth valve 12, a liquid storage tank 13 and a filter 14. In a refrigerant loop, the output end of a second plate heat exchanger 1 is connected with the first output end of a four-way reversing valve 2 and the input end of a low-pressure compressor 3, the output end of the low-pressure compressor 3 is connected with a first input end 4 of an intercooler, the input end of a high-pressure compressor 5 is connected with the output end 4 of the intercooler, the output end of the high-pressure compressor 5 and the second output end of the four-way reversing valve 2 are connected with the input end of a second fin coil heat exchanger 6, a first branch of the output end of the second fin coil heat exchanger 6 is connected with a first electronic expansion valve 7, a second branch is connected with a first valve 8 and connected with the first branch in parallel, two branches are connected in parallel, the first branch is connected with a second input end 4 of the intercooler through a second valve 9, and the second branch flows through. The output end of the first plate heat exchanger 10 is connected with the fourth valve 12 in parallel through the second electronic expansion valve 11 and is connected with the input end of the liquid storage tank 13. The output end of the liquid storage tank 13 is connected with the input end of a filter 14, and the filter 14 is connected with the input end of the second plate heat exchanger 1. The air circuit comprises a first air valve 24, a second air valve 25, a third air valve 27, the solution tower 22, the second finned coil heat exchanger 6 and a first fan 26. In the air circuit, the first air valve 24 is an air pipe input end, and the third air valve 27 is an air pipe output end. The first branch is connected with the solution tower 22, the second finned coil heat exchanger 6 and the first fan 26 in sequence, and the second branch is connected with the second air valve 25 and the output end from the input end of the air pipe. The water circuit comprises a second plate heat exchanger 1, a water pump 15, a second flowmeter 16, a second finned coil heat exchanger 17 and a fifth valve 18. In the water loop, the input end of the water pump 15 is connected to the second plate heat exchanger 1, the output end of the water pump 15 is connected to the input end of the second fin coil heat exchanger 17 through the first flowmeter 16, and the output end of the second fin coil heat exchanger 17 is connected to the second plate heat exchanger 1 through the fifth valve 18 to form the water loop.
In the present invention, the evaporative cooling cycle and the heat pump cycle are continuously operated during summer operation, and the solution tower 22 contains water. The first electronic expansion valve 7 and the fourth valve 12 are closed. The solution loop exchanges heat with the refrigerant loop through the second plate heat exchanger 1, the water loop exchanges heat with the refrigerant loop through the second plate heat exchanger 1, the air loop exchanges heat with the refrigerant loop through the first finned coil heat exchanger 6, the air loop exchanges heat with the water loop through the second finned coil heat exchanger 17, and the air loop exchanges heat with the solution loop through the solution tower 22. The basic process is as follows: for a refrigerant loop, low-temperature and low-pressure refrigerants are compressed by a low-pressure compressor 3, then flow into an intercooler 4, are mixed with part of high-temperature refrigerants flowing out of a first finned coil heat exchanger 6, enter a high-pressure compressor 5 for compression, then flow into the first finned coil heat exchanger 6 through a four-way reversing valve 2 for heat exchange with an air loop, flow through a first valve 8, part of high-temperature and high-pressure refrigerants flow into the intercooler 4 for mixing with low-pressure and low-temperature refrigerants, flow through the intercooler 4 for cooling, flow through a first plate heat exchanger 10 for heat exchange with a solution loop, flow through a second electronic expansion valve 11, a liquid storage tank 13 and a filter 14, and flow through a second plate heat exchanger 1 for heat exchange. For the solution loop, the solution is pumped by a solution pump 20 into a solution tower 22, mixed with high temperature air, and pre-cooled. For the air loop, air enters the air supply pipeline from the first air valve 24, cooling water passing through the solution tower 22 is evaporated, cooled and cooled, the supercooling degree is increased, water drops are attached to the air, the air passes through the first fin coil heat exchanger 6, and the water drops are attached to the first fin coil heat exchanger 6 to evaporate and absorb heat.
During winter operation, the solution tower is filled with solution. The second electronic expansion valve 11, the first valve 8 are closed. In the heating mode, for a refrigerant loop, low-temperature and low-pressure refrigerants are compressed by the low-pressure compressor 3, then flow into the intercooler 4, are mixed with part of high-temperature refrigerants flowing out of the condenser, enter the high-pressure compressor 5 for compression, then flow into the second plate heat exchanger 1 through the four-way reversing valve 2 to exchange heat with the water loop, release all heat to cooling water, flow through the filter 4, the liquid storage tank 3, the fourth valve 12, the first plate heat exchanger 10, the intercooler 4, the first valve 7 and the second fin coil heat exchanger 6, and absorb heat from solution, the intercooler 4 and ambient air. For the air circuit, air enters the air supply pipeline from the first air valve 24 and is dehumidified by the solution tower 22, and frost-free operation is achieved. In the regeneration mode, the first air valve 24 and the second air valve 27 are closed, the third air valve 25 is opened, the condensed high-pressure medium-temperature refrigerant liquid transfers the residual heat of condensation to the dilute solution in the first plate heat exchanger 10, the water vapor pressure on the surface of the dilute solution is increased, and the air absorbs moisture and condenses water on the surface of the first fin coil heat exchanger 6. Circulating in the air duct until the dilute solution becomes the required concentrated solution. The above description is only a preferred embodiment of the present invention and is not intended to limit the present invention, it should be noted that, for those skilled in the art, many modifications and variations can be made without departing from the technical principle of the present invention, and these modifications and variations should also be regarded as the protection scope of the present invention.

Claims (3)

1. The utility model provides a full fever type frostless air source heat pump system based on doublestage centrifugal compressor which characterized in that: comprises a solution loop, a water loop, a refrigerant loop and an air loop;
in the solution loop, the input end of a solution pump (20) is connected to a first plate heat exchanger (10) in the loop, and a solution tower (22) is connected with the solution pump (20) through a second flowmeter (21) and is connected with the first plate heat exchanger (10) through a third valve (23) to form the loop;
in the refrigerant loop, the output end of the second plate heat exchanger (1) is connected with the first output end of the four-way reversing valve (2) and the input end of the low-pressure compressor (3), the output end of the low-pressure compressor (3) is connected with the first input end (4) of the intercooler, the input end of the high-pressure compressor (5) is connected with the output end (4) of the intercooler, the output end of the high-pressure compressor (5) is connected with the second output end of the four-way reversing valve (2) and the input end of the second finned coil heat exchanger (6), the first branch of the output end of the second finned coil heat exchanger (6) is connected with the first electronic expansion valve (7), and the second branch is connected with the first valve (8), the first branch is connected with a second branch in parallel, the first branch is connected with a second input end (4) of the intercooler through a second valve (9), and the second branch flows through the intercooler (4) and is connected with the input end of the first plate heat exchanger (10); the output end of the first plate heat exchanger (10) is connected with the fourth valve (12) in parallel through a second electronic expansion valve (11) and is connected with the input end of the liquid storage tank (13); the output end of the liquid storage tank (13) is connected with the input end of a filter (14), and the filter (14) is connected with the input end of the second plate heat exchanger (1);
in the air loop, a first air valve (24) is an air pipe input end, and a third air valve (27) is an air pipe output end; the first branch is connected with the solution tower (22), the second finned coil heat exchanger (6) and the first fan (26) in sequence, and the second branch is connected with the second air valve (25) and the output end from the input end of the air pipe;
in the water loop, the input end of a water pump (15) is connected to the second plate type heat exchanger (1), the output end of the water pump (15) is connected with the input end of the second finned coil heat exchanger (17) through a first flow meter (16), and the output end of the second finned coil heat exchanger (17) is connected with the second plate type heat exchanger (1) through a fifth valve (18) to form the water loop.
2. The full-thermal frostless air source heat pump system based on the two-stage centrifugal compressor as claimed in claim 1, wherein: the system takes outdoor air as a low-grade heat source and absorbs sensible heat and latent heat from the outdoor air through solution circulation.
3. The full-thermal frostless air source heat pump system based on the two-stage centrifugal compressor as claimed in claim 1, wherein: the intercooler performs intermediate incomplete cooling on low-pressure refrigerant steam generated by the low-pressure compressor and provides heat for the refrigerant after throttling heat exchange.
CN202010248510.6A 2020-04-01 2020-04-01 Total-heat frostless air source heat pump system based on two-stage centrifugal compressor Pending CN111412674A (en)

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Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2005214443A (en) * 2004-01-27 2005-08-11 Sanyo Electric Co Ltd Refrigerator
EP2224187A2 (en) * 2004-10-18 2010-09-01 Mitsubishi Denki Kabushiki Kaisha Refrigeration/air conditioning equipment
CN103644677A (en) * 2013-12-05 2014-03-19 东南大学 Solution regeneration device based on throttling flash and capable of realizing self-balance of regenerated energy
CN103900310A (en) * 2014-04-17 2014-07-02 东南大学 Solution desiccant system and method for preventing air source heat pump water heater from frosting

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2005214443A (en) * 2004-01-27 2005-08-11 Sanyo Electric Co Ltd Refrigerator
EP2224187A2 (en) * 2004-10-18 2010-09-01 Mitsubishi Denki Kabushiki Kaisha Refrigeration/air conditioning equipment
CN103644677A (en) * 2013-12-05 2014-03-19 东南大学 Solution regeneration device based on throttling flash and capable of realizing self-balance of regenerated energy
CN103900310A (en) * 2014-04-17 2014-07-02 东南大学 Solution desiccant system and method for preventing air source heat pump water heater from frosting

Non-Patent Citations (2)

* Cited by examiner, † Cited by third party
Title
邱君君 张小松 李玮豪: "无霜空气源热泵系统冬季再生性能初步实验", 《制冷学报》 *
陈维刚: "《制冷空调技术一本通》", 30 April 2012, 上海科学技术出版社 *

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Application publication date: 20200714