CN105423620A - Efficient large temperature rise two-stage throttling intercooling heat pump water heater - Google Patents
Efficient large temperature rise two-stage throttling intercooling heat pump water heater Download PDFInfo
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- CN105423620A CN105423620A CN201510993754.6A CN201510993754A CN105423620A CN 105423620 A CN105423620 A CN 105423620A CN 201510993754 A CN201510993754 A CN 201510993754A CN 105423620 A CN105423620 A CN 105423620A
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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
- F25B30/00—Heat pumps
- F25B30/02—Heat pumps of the compression type
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
- F24H4/00—Fluid heaters characterised by the use of heat pumps
- F24H4/02—Water heaters
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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
- F25B2500/00—Problems to be solved
- F25B2500/18—Optimization, e.g. high integration of refrigeration components
Abstract
The invention discloses an efficient large temperature rise two-stage throttling intercooling heat pump water heater. An outlet of a high pressure compressor is communicated with a refrigerant inlet of a first condenser. A refrigerant outlet of the first condenser is communicated with a first inlet of a first gas-liquid separator through a first throttling device. A gas outlet of the first gas-liquid separator is communicated with an inlet of the high pressure compressor. A liquid outlet of the first gas-liquid separator is communicated with an inlet of an evaporator through a one-way valve and a second throttling device. An outlet of the evaporator is communicated with an inlet of a low pressure compressor. One outlet of the low pressure compressor is communicated with a refrigerant inlet of a second condenser through a first stop valve. A refrigerant outlet of the second condenser is communicated with an inlet of the second throttling device. Another outlet of the low pressure compressor is communicated with a second inlet of the first gas-liquid separator through a second stop valve. A total cooling water inlet is communicated with the second condenser and the first condenser through a water pump. A hot water outlet of the first condenser is a total hot water outlet. The heat pump water heater has the advantages that the power consumption is effectively reduced, the energy efficiency is improved, and the operating range is increased.
Description
Technical field
The present invention relates to field of water heaters, especially a kind of heat pump water-heating machine.
Background technology
Teat pump boiler is due to energy-conserving and environment-protective, and that deepens in the day by day serious especially haze harm of Environment and energy problem has become requisite a kind of device in the life with significant market prospect instantly.But Teat pump boiler still needs to consume a large amount of electric energy after all, the efficiency therefore improving heat pump is emphasis and the focus of a research.In addition, lower at ground winter temperatures such as China northeast, northwests, often reach even beyond the working limit of common Teat pump boiler, therefore expand the working range of heat pump water-heating machine, improving operation stability is also the important directions that it improves.
Summary of the invention
In order to overcome the deficiency that power consumption is comparatively large, efficiency is lower, working range is wide not of existing heat pump water-heating machine, the invention provides the large efficiently temperature rise two-stage throttling cooling during rolling heat pump water-heating machine of a kind of effective reduction power consumption, improving energy efficiency, increase working range.
The technical solution adopted for the present invention to solve the technical problems is:
A kind of large temperature rise two-stage throttling cooling during rolling heat pump water-heating machine efficiently, comprise high pressure compressor, low pressure compressor, first condenser, second condenser, first gas-liquid separator and evaporimeter, the outlet of described high pressure compressor is communicated with the refrigerant inlet of described first condenser, the refrigerant outlet of described first condenser is communicated with through first entrance of first throttle device with described first gas-liquid separator, the gas vent of described first gas-liquid separator is communicated with the entrance of described high pressure compressor, the liquid outlet of described first gas-liquid separator is communicated with through the entrance of check valve with the second throttling arrangement, the outlet of described second throttling arrangement is communicated with the entrance of described evaporimeter, the outlet of described evaporimeter is communicated with the entrance of described low pressure compressor, the outlet of described low pressure compressor is divided into two strands, one is communicated with through the refrigerant inlet of the first stop valve with the second condenser, the refrigerant outlet of described second condenser is communicated with the entrance of described second throttling arrangement, another stock-traders' know-how is crossed the second stop valve and is communicated with the second entrance of described first gas-liquid separator,
Total cooling water inlet is communicated with by the cooling water inlet of water pump with the second condenser, and the hot water outlet of described second condenser is communicated with the cooling water inlet of described first condenser, and the hot water outlet of described first condenser is total hot water outlet.
Further, the outlet of described evaporimeter is communicated with the entrance of the second gas-liquid separator, and the gas vent of described second gas-liquid separator is communicated with the entrance of described low pressure compressor.
Further again, the outlet of described high pressure compressor is connected with the first oil eliminator entrance, the oil export of described first oil eliminator is communicated with the entrance of described high pressure compressor, and the refrigerant outlet of described first oil eliminator is communicated with the refrigerant inlet of described first condenser; The outlet of described low pressure compressor is connected with the second oil eliminator entrance, the oil export of described second oil eliminator is communicated with the entrance of described low pressure compressor, and the refrigerant outlet of described second oil eliminator is divided into two stocks not to be connected with the entrance of the first stop valve and the entrance of the second stop valve.
Further, between the refrigerant outlet of described second condenser and the entrance of described evaporimeter, defrost arm is set, described defrost arm installs the 3rd stop valve.
The outlet of described evaporimeter is communicated with the entrance of described high pressure compressor through the 4th stop valve, the gas vent of described first gas-liquid separator is communicated with the entrance of the 5th stop valve, and the outlet of described 5th stop valve exports with the 4th stop valve, the entrance of high pressure compressor is all connected.
Or: the gas vent of described second gas-liquid separator is communicated with the entrance of described high pressure compressor through the 4th stop valve, the gas vent of described first gas-liquid separator is communicated with the entrance of the 5th stop valve, and the outlet of described 5th stop valve exports with the 4th stop valve, the entrance of high pressure compressor is all connected.
Beneficial effect of the present invention is mainly manifested in:
1, the throttling of two stages of compression two-stage is adopted, greatly the scope of application is extended compared with single-stage heat pump, improve efficiency, and send into high pressure stage compressor again after being cooled by low-pressure stage compressor air-discharging, reduce high pressure stage compressor delivery temperature, the higher hot water of temperature can be produced and improve the stability of a system;
2, compare existing two stages of compression heat pump, have employed two-step heating hot water dexterously, when hot water temperature rise is larger, to a certain degree can reduces the wasted work of high pressure compressor, namely improve system energy efficiency further.Essentially, existing directly-heated type Teat pump boiler has larger heat transfer temperature difference and namely produces larger entropy product, cold water and hot water then can mix and causes larger entropy and produce equally by circulating heat pump water heater, and the present invention reduces above-mentioned entropy and produce, and improve the thermodynamics integrity of system;
3, most suitable pattern can be selected under different seasons, different external condition, promote seasonal energy efficiency to greatest extent, and ensure the stable operation of system.The simple pipeline of parts is flexible, switches the two stages of compression two-step heating pattern that how realizes, two stages of compression one-level heating mode, low-pressure stage compression single-stage heating mode, hiigh pressure stage compression single-stage heating mode and hot-gas bypass defrost pattern by a small amount of stop valve.
Accompanying drawing explanation
Fig. 1 is a kind of schematic diagram of large temperature rise two-stage throttling cooling during rolling heat pump water-heating machine efficiently.
Fig. 2 is the schematic diagram of another kind of large temperature rise two-stage throttling cooling during rolling heat pump water-heating machine efficiently.
Fig. 3 is the schematic diagram of another efficient large temperature rise two-stage throttling cooling during rolling heat pump water-heating machine.
Detailed description of the invention
Below in conjunction with accompanying drawing, the invention will be further described.
With reference to Fig. 1 ~ Fig. 3, a kind of large temperature rise two-stage throttling cooling during rolling heat pump water-heating machine efficiently, comprise high pressure compressor 1, low pressure compressor 10, first condenser 3, second condenser 13, first gas-liquid separator 5 and evaporimeter 8, the outlet of described high pressure compressor 1 is communicated with the refrigerant inlet of described first condenser 3, the refrigerant outlet of described first condenser 3 is communicated with through first entrance of first throttle device 4 with described first gas-liquid separator 5, the gas vent of described first gas-liquid separator 5 is communicated with the entrance of described high pressure compressor 1, the liquid outlet of described first gas-liquid separator 5 is communicated with through the entrance of check valve 6 with the second throttling arrangement 7, the outlet of described second throttling arrangement 7 is communicated with the entrance of described evaporimeter 8, the outlet of described evaporimeter 8 is communicated with the entrance of described low pressure compressor 10, the outlet of described low pressure compressor 10 is divided into two strands, one is communicated with through the refrigerant inlet of the first stop valve 12 with the second condenser 13, the refrigerant outlet of described second condenser 13 is communicated with the entrance of described second throttling arrangement 7, another stock-traders' know-how is crossed the second stop valve 14 and is communicated with the second entrance of described first gas-liquid separator 5,
Total cooling water inlet is communicated with the cooling water inlet of the second condenser 13 by water pump 15, and the hot water outlet of described second condenser 13 is communicated with the cooling water inlet of described first condenser 3, and the hot water outlet of described first condenser 3 is total hot water outlet.
Further, the outlet of described evaporimeter 8 is communicated with the entrance of the second gas-liquid separator 9, and the gas vent of described second gas-liquid separator 9 is communicated with the entrance of described low pressure compressor 10.
Further again, the outlet of described high pressure compressor 1 is connected with the entrance of the first oil eliminator 2, the oil export of described first oil eliminator 2 is communicated with the entrance of described high pressure compressor 1, and the refrigerant outlet of described first oil eliminator 2 is communicated with the refrigerant inlet of described first condenser 3; The outlet of described low pressure compressor 10 is connected with the entrance of the second oil eliminator 11, the oil export of described second oil eliminator 11 is communicated with the entrance of described low pressure compressor 10, and the refrigerant outlet of described second oil eliminator 11 is divided into two stocks not to be connected with the entrance of the first stop valve and the entrance of the second stop valve.
Further, between the refrigerant outlet of described second condenser 13 and the entrance of described evaporimeter 8, defrost arm is set, described defrost arm installs the 3rd stop valve 16
The outlet of described evaporimeter is communicated with the entrance of described high pressure compressor through the 4th stop valve, the gas vent of described first gas-liquid separator is communicated with the entrance of the 5th stop valve, and the outlet of described 5th stop valve exports with the 4th stop valve, the entrance of high pressure compressor is all connected.
Or: the gas vent of described second gas-liquid separator 9 is communicated with through the entrance of the 4th stop valve 17 with described high pressure compressor 1, the gas vent of described first gas-liquid separator 5 is communicated with the entrance of the 5th stop valve 18, and the outlet of described 5th stop valve 18 exports with the 4th stop valve 17, the entrance of high pressure compressor 1 is all connected.
The course of work of the present embodiment is:
With reference to Fig. 1:
Two stages of compression two-step heating pattern: when environment temperature is lower, required hot water temperature is higher again, and adopts this pattern when inlet water temperature is lower, and the first stop valve 12 and the second stop valve 14 are all opened, high pressure compressor 1, low pressure compressor 10 all run, and water pump 15 runs.The oil-containing gaseous refrigerant of HTHP exports outflow from high pressure compressor 1 and enters the first oil eliminator 2, lubricating oil in refrigerating agent containing oil is separated at the first oil eliminator and flows out from the oil export of the first oil eliminator 2 and gets back to suction port of compressor, the cold-producing medium of HTHP flows out from the refrigerant outlet of oil eliminator and enters the first condenser 3 refrigerant inlet exothermic condensation, the liquid refrigerant of high pressure flows out after first throttle device 4, become middle pressure gas-liquid mixed refrigerant the first entrance entering the first gas-liquid separator 5 from the refrigerant outlet of the first condenser 3, gaseous refrigerant flows out from the gas vent of the first gas-liquid separator 5, liquid refrigerant from the liquid outlet of the first gas-liquid separator 5 flow out mix with the liquid refrigerant from the second condenser 13 after check valve 6 after after the second throttling arrangement 7, become low-temp low-pressure refrigerant air-liquid mixture enter evaporimeter 8 absorbing environmental heat, then low-temp low-pressure gaseous refrigerant after heat absorption evaporation is inhaled into the entrance of low pressure compressor 10 through the second gas-liquid separator 9, the refrigerating agent containing oil of medium temperature and medium pressure is discharged from the outlet of low pressure compressor 10 and is entered the second oil eliminator 11, lubricating oil wherein flows out from the oil export of the second oil eliminator 11 entrance returning low pressure compressor 10, the cold-producing medium of medium temperature and medium pressure then flows out from the refrigerant outlet of the second oil eliminator 11 and is divided into two strands, one enters condensation heat release in the second condenser 13 through the first stop valve 12 and becomes the liquid refrigerant of middle pressure, with the refrigerant mixed from one-way valved outlet after flowing out from the refrigerant outlet of the second condenser 13, another road enters the second entrance of the first gas-liquid separator 5 through the second stop valve 14.Cold water enters in the second condenser 13 and is tentatively heated after water pump 15, becomes middle warm water, and then enters the first condenser 3 and be further heated, and flows out supply user after becoming high-temperature-hot-water from the first condenser 3 water out.
In order to energy-saving effect of the present invention is described better, shown below is systematic simulation calculation result based on two stages of compression two-step heating pattern and with traditional single-stage heat pump and be representative with patent (200720039229.1) two stages of compression heat pump (comprise and spray enthalpy increasing heat pump) contrasts.During calculating, all parts is according to the conservation of mass and conservation of energy modeling, compressor isentropic efficiency adopts the (InternationalJournalofRefrigeration such as Navarro-Peris, 2013,36 (7)) equation proposed, ignore pipeline friction loss and leak heat, other setup parameters, in table 1, the results are shown in Table 2.
As can be known from the results of Table 2, COP of the present invention is the highest, higher than two stages of compression heat pump by 21.4%, exceeds 27.8% especially than traditional single-stage heat pump.
Table 1
Table 2
Two stages of compression two-step heating pattern: when environment temperature is lower, required hot water temperature is higher again, and adopts this pattern when inlet water temperature is more higher than environment temperature, first stop valve 12 is closed, second stop valve 14 is opened, and high pressure compressor 1, low pressure compressor 10 all run, and water pump 15 runs.Running is now compared with regular run mode, and because the first stop valve 12 is closed, the second condenser 13 does not work, from water pump 15 out cold water do not heated when the second condenser 13, but only to be heated in the first condenser 3.
Low-pressure stage compression single-stage heating mode: when environment temperature is relatively high, and adopt this pattern when required hot water temperature is normal.First stop valve 12 is opened, and the second stop valve 14 is closed, and high pressure compressor 1 cuts out, and low pressure compressor 10 runs, and water pump 15 runs.The refrigerating agent containing oil of HTHP is discharged from the outlet of low pressure compressor 10 and is entered the second oil eliminator 11, lubricating oil wherein flows out from the oil export of the second oil eliminator 11 entrance returning low pressure compressor 10, the cold-producing medium of medium temperature and medium pressure then flows out from the refrigerant outlet of the second oil eliminator 11 and enters through the first stop valve 12 liquid refrigerant that second condenser 13, condensation heat release becomes, the refrigerant air-liquid mixture becoming low-temp low-pressure after the refrigerant outlet outflow of the second condenser 13 after the second throttling arrangement 7 enters evaporimeter 8 absorbing environmental heat, low-temp low-pressure gaseous refrigerant after heat absorption evaporation is inhaled into the entrance of low pressure compressor 10 through the second gas-liquid separator 9.Cold water enters in the second condenser 13 and is heated after water pump 15, because the first condenser 3 does not work, is not heated when hot water flows through the first condenser 3, finally flows out supply user from the first condenser 3 water out.
With reference to Fig. 2:
When outdoor environment temperature is near or below 0 DEG C, evaporating temperature can reach less than 0 DEG C, may frosting freeze outside evaporimeter, now needs to carry out defrost to the evaporimeter of heat pump water-heating machine.Therefore, the basis of Fig. 1 adds the 3rd stop valve 16 between the refrigerant outlet of the second condenser 2 and the entrance of evaporimeter 8, and connects with pipeline, hot-gas bypass defrosting function can be realized, heat pump water-heating machine can more stably be run.Except increasing defrost power, the function that this flow process can realize is the same with Fig. 1's, and the 3rd stop valve 16 keeps closing when realizing the pattern of Fig. 1.
Hot-gas bypass defrost pattern: the first stop valve 12 is opened, the second stop valve 14 is closed, the 3rd stop valve 16 is opened, and high pressure compressor 1 cuts out, and low pressure compressor 10 runs, and water pump 15 cuts out.The gaseous state refrigerating agent containing oil of HTHP is discharged from the outlet of low pressure compressor 10 and is entered the second oil eliminator 11, lubricating oil wherein flows out from the oil export of the second oil eliminator 11 entrance returning low pressure compressor 10, high temperature liquid refrigerant then flows out through the first stop valve 12 and the second condenser 13 from the refrigerant outlet of the second oil eliminator 11, because water pump 15 cuts out, second condenser 13 does not work, high temperature liquid refrigerant does not carry out heat exchange in the second condenser 13, high temperature liquid refrigerant enters evaporimeter 8 heat release after the refrigerant outlet of the second condenser 13 flows out after the 3rd stop valve 16, make the defrost of evaporimeter outer wall, cold-producing medium exports the entrance flowing out and be finally inhaled into low pressure compressor 10 after the second gas-liquid separator 9 from evaporimeter 8.
With reference to Fig. 3:
When environment temperature is relatively high, and required hot water temperature normal time, low pressure compressor 10 is adopted to carry out single stage compress heating mode in the embodiment of Fig. 1, and in Fig. 3, add the 4th stop valve 17 and the 5th stop valve 18, make also can adopt high pressure compressor 1 when carrying out single stage compress heating, because high pressure compressor 1 is different with cylinder dimensions from the rated power of low pressure compressor 10, therefore expand the heating power scope of single stage compress heating mode, also improve the utilization rate of high pressure compressor simultaneously.This flow process is except can realizing hiigh pressure stage compression single-stage heating mode, and also can realize all operational modes of Fig. 1 and Fig. 2, only the 4th stop valve 17 need be kept closing, the 5th stop valve 18 is held open.
Hiigh pressure stage compression single-stage heating mode: the first stop valve 12, second stop valve the 14, three stop valve the 16, five stop valve 18 is closed, and the 4th stop valve 17 is opened, and high pressure compressor 1 and water pump 15 are opened, and low pressure compressor 10 cuts out.The oil-containing gaseous refrigerant of HTHP exports outflow from high pressure compressor 1 and enters the first oil eliminator 2, lubricating oil in refrigerating agent containing oil is separated at the first oil eliminator and flows out from the oil export of the first oil eliminator 2 and gets back to suction port of compressor, the cold-producing medium of HTHP flows out from the refrigerant outlet of oil eliminator and enters the first condenser 3 refrigerant inlet exothermic condensation, the liquid refrigerant of high pressure becomes the gas-liquid mixed refrigerant of middle pressure from the refrigerant outlet outflow of the first condenser 3 and enters the first entrance of the first gas-liquid separator 5 and flow out after check valve 6 again through the second throttling arrangement 7 from the liquid outlet of the first gas-liquid separator 5 after first throttle device 4, the refrigerant air-liquid mixture becoming low-temp low-pressure enters evaporimeter 8 absorbing environmental heat, then low-temp low-pressure gaseous refrigerant after heat absorption evaporation returns the entrance of high pressure compressor 1 through Section of four stop valve 17 through the second gas-liquid separator 9.Cold water flows through the second condenser 13 but does not heat after water pump 15, and then enters the first condenser 3 and heated, and flows out supply user after becoming high-temperature-hot-water from the first condenser 3 water out.
Claims (8)
1. an efficient large temperature rise two-stage throttling cooling during rolling heat pump water-heating machine, it is characterized in that: comprise high pressure compressor, low pressure compressor, first condenser, second condenser, first gas-liquid separator and evaporimeter, the outlet of described high pressure compressor is communicated with the refrigerant inlet of described first condenser, the refrigerant outlet of described first condenser is communicated with through first entrance of first throttle device with described first gas-liquid separator, the gas vent of described first gas-liquid separator is communicated with the entrance of described high pressure compressor, the liquid outlet of described first gas-liquid separator is communicated with through the entrance of check valve with the second throttling arrangement, the outlet of described second throttling arrangement is communicated with the entrance of described evaporimeter, the outlet of described evaporimeter is communicated with the entrance of described low pressure compressor, the outlet of described low pressure compressor is divided into two strands, one is communicated with through the refrigerant inlet of the first stop valve with the second condenser, the refrigerant outlet of described second condenser is communicated with the entrance of described second throttling arrangement, another stock-traders' know-how is crossed the second stop valve and is communicated with the second entrance of described first gas-liquid separator,
Total cooling water inlet is communicated with by the cooling water inlet of water pump with the second condenser, and the hot water outlet of described second condenser is communicated with the cooling water inlet of described first condenser, and the hot water outlet of described first condenser is total hot water outlet.
2. large temperature rise two-stage throttling cooling during rolling heat pump water-heating machine efficiently as claimed in claim 1, it is characterized in that: the outlet of described evaporimeter is communicated with the entrance of the second gas-liquid separator, the gas vent of described second gas-liquid separator is communicated with the entrance of described low pressure compressor.
3. large temperature rise two-stage throttling cooling during rolling heat pump water-heating machine efficiently as claimed in claim 1, it is characterized in that: the outlet of described high pressure compressor is connected with the first oil eliminator entrance, the oil export of described first oil eliminator is communicated with the entrance of described high pressure compressor, and the refrigerant outlet of described first oil eliminator is communicated with the refrigerant inlet of described first condenser; The outlet of described low pressure compressor is connected with the second oil eliminator entrance, the oil export of described second oil eliminator is communicated with the entrance of described low pressure compressor, and the refrigerant outlet of described second oil eliminator is divided into two stocks not to be connected with the entrance of the first stop valve and the entrance of the second stop valve.
4. large temperature rise two-stage throttling cooling during rolling heat pump water-heating machine efficiently as claimed in claim 2, it is characterized in that: the outlet of described high pressure compressor is connected with the first oil eliminator entrance, the oil export of described first oil eliminator is communicated with the entrance of described high pressure compressor, and the refrigerant outlet of described first oil eliminator is communicated with the refrigerant inlet of described first condenser; The outlet of described low pressure compressor is connected with the second oil eliminator entrance, the oil export of described second oil eliminator is communicated with the entrance of described low pressure compressor, and the refrigerant outlet of described second oil eliminator is divided into two stocks not to be connected with the entrance of the first stop valve and the entrance of the second stop valve.
5. the large efficiently temperature rise two-stage throttling cooling during rolling heat pump water-heating machine as described in one of Claims 1 to 4, it is characterized in that: between the refrigerant outlet of described second condenser and the entrance of described evaporimeter, defrost arm is set, described defrost arm installs the 3rd stop valve.
6. the large efficiently temperature rise two-stage throttling cooling during rolling heat pump water-heating machine as described in one of Claims 1 to 4, it is characterized in that: the outlet of described evaporimeter is communicated with the entrance of described high pressure compressor through the 4th stop valve, the gas vent of described first gas-liquid separator is communicated with the entrance of the 5th stop valve, and the outlet of described 5th stop valve exports with the 4th stop valve, the entrance of high pressure compressor is all connected.
7. large temperature rise two-stage throttling cooling during rolling heat pump water-heating machine efficiently as claimed in claim 5, it is characterized in that: the outlet of described evaporimeter is communicated with the entrance of described high pressure compressor through the 4th stop valve, the gas vent of described first gas-liquid separator is communicated with the entrance of the 5th stop valve, and the outlet of described 5th stop valve exports with the 4th stop valve, the entrance of high pressure compressor is all connected.
8. large temperature rise two-stage throttling cooling during rolling heat pump water-heating machine efficiently as claimed in claim 2, it is characterized in that: the gas vent of described second gas-liquid separator is communicated with the entrance of described high pressure compressor through the 4th stop valve, the gas vent of described first gas-liquid separator is communicated with the entrance of the 5th stop valve, and the outlet of described 5th stop valve exports with the 4th stop valve, the entrance of high pressure compressor is all connected.
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Cited By (4)
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| CN107198887A (en) * | 2016-09-08 | 2017-09-26 | 江苏科技大学 | A kind of steam compression system and method for work |
| CN109059279A (en) * | 2017-06-13 | 2018-12-21 | 上海海立电器有限公司 | Compressor heat pumping system with double water temperature |
| CN110056936A (en) * | 2019-04-24 | 2019-07-26 | 东北大学 | A kind of low ebb electric heat storage cascade type heat pump heating system and mode |
| 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 |
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| CN110056936A (en) * | 2019-04-24 | 2019-07-26 | 东北大学 | A kind of low ebb electric heat storage cascade type heat pump heating system and mode |
| CN110056936B (en) * | 2019-04-24 | 2020-09-15 | 东北大学 | Off-peak electricity heat storage cascade heat pump heat supply method |
| 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 |
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| CN105423620B (en) | 2017-11-07 |
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