CN2530221Y - Double-staged compression low temp heat pump appts. - Google Patents
Double-staged compression low temp heat pump appts. Download PDFInfo
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- CN2530221Y CN2530221Y CN 02200545 CN02200545U CN2530221Y CN 2530221 Y CN2530221 Y CN 2530221Y CN 02200545 CN02200545 CN 02200545 CN 02200545 U CN02200545 U CN 02200545U CN 2530221 Y CN2530221 Y CN 2530221Y
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Abstract
A double-stage compression low-temperature heat pump device applicable to cold areas, which is made by adding a high pressure unit (16) composed of a high pressure compressor (17), a high pressure four-way valve (18), a middle throttle heat expansion valve (19), a solenoid valve (20), a middle cooler (21) and refrigerant connecting pipes to the refrigerant loop of an ordinary heat pump device consisting of a compressor (1), a four-way valve (2), refrigerant/ an air heat exchanger (3), heat expansion valves (5,8), one-way valves (6,9), a high pressure liquid container (7), a dry filter (15), refrigerant/ a water heat exchanger (11) and/or refrigerant a water heat exchanger (28), a gas-liquid separator (12), a water pump (13) and/or a fan (30), as well as refrigerant and water path connecting pipes. With help of the above technical proposal, the utility model not only can function and perform as an ordinary heat pump device under summer conditions and common winter conditions, but can run stably and reliably for a long period of time at a low temperature of minus 18 DEG, with sufficient heating capacity and a high coefficient of performance; the discharge temperature of the compress is maintained below 130 DEG, and is capable of providing heat as needed in cold areas in winter without supplementary heat sources.
Description
The utility model belongs to universal machine or field of fluid machinery, especially relates to a kind of heat pump air conditioner that heat can be provided to the indoor highly effective rate under extraneous cold environmental conditions.
In recent years, along with improving constantly of China's rapid development of economy and living standards of the people, the idle call heat pump in the middle and lower reach of Yangtze River, traditional non-heating zone such as south China and southwest is used widely, it has satisfied the requirement of this area's winter heating well with lower energy consumption, and effect is good.But in areas such as China Huanghe valley, North China is with fire coal, fuel oil and the electric heater main means as winter heating always.Because region temperatures such as the Huanghe valley and North China are lower, adopt the normal air source heat pump device, its heating capacity and the coefficient of performance reduce greatly, and the compressor exhaust temperature overtemperature, and the high frequent start and stop can't operate as normal.Therefore the normal air source heat pump device can't satisfy the cold district heating demand in winter.
For making can be in low temperature environment efficient, stable, the operation reliably of heat pump assembly, carry out many technical researches and improvement both at home and abroad.1997 the 7th periodicals of Japan's " freezing " magazine have been stepped on the article " Developmentof Packaged Air Conditioner For Cold Regions " of N.Horiuchi, having introduced the employing converter plant increases the working medium internal circulating load when the outdoor compressor high speed operation that allows during for low temperature environment, simultaneously to compressor operating chamber hydrojet to prevent its delivery temperature overtemperature; 1993 Nian 《 East sesame レ PVC ユ-" the 4th phase occasion light publish thesis well " ト リ プ Le De ラ イ Machine can pay I ガ ス エ ア コ Application ", " Mitsubishi Heavy Industries Ltd's skill newspaper " the 2nd periodical had been stepped on the refreshing article of controlling " refrigerant heated type Le-system エ ア コ Application is developed with バ-Na " that wins in mountain in 1998, had all proposed to adopt Wick lifter of kerosine burner auxiliary heating chamber external heat exchanger when low ambient temperature to improve the technical scheme of the cryogenic property of heat pump; March calendar year 2001, Tsing-Hua University Malaysian proposes to adopt the screw compressor of band auxilairy air intake in its post-doctor sets off report " research of air source heat pump low temperature adaptability ", when worst cold case by auxilairy air intake to compressor operating chamber spray cryogen, improve the technical scheme that heat pump internal compression process improves the cryogenic property of heat pump with this; More domestic producers once introduced at dress electrical auxiliary heater on the indoor water route and solved the not enough problem of heating capacity under the worst cold case.Generally speaking, these technology all can not be implemented in outdoor temperature effectively for high efficiency under-18 ℃ of conditions, big ability, safely and reliably to the target of indoor heating, so do not tackle the problem at its root.
In view of the foregoing, the utility model proposes a kind of technical scheme of double stage compresses hot pump in low temp device of suitable cold district use.Adopt the heat pump assembly of this technical scheme not only to have performance and the function of ordinary hot pump installation under summer and general winter condition, and can in-18 ℃ low temperature environment, stablize, long-time running reliably, and have the enough heating capacities and the higher coefficient of performance, compressor exhaust temperature is lower than 130 ℃ all the time, can not have to satisfy the cold district heating requirement in winter under the condition of auxiliary thermal source.
The double stage compresses hot pump in low temp device that the utility model proposed is set up the hiigh pressure stage unit and is constituted on ordinary hot pump installation refrigeration cycle basis.Wherein, ordinary hot pump installation kind of refrigeration cycle comprises compressor, cross valve, refrigerant/air heat exchanger, fan, heating power expansion valve, device for drying and filtering, check valve, high pressure receiver, refrigerant/water heat exchanger, gas-liquid separator, cold-producing medium connecting line, water pump, water route tube connector; The kind of refrigeration cycle hiigh pressure stage unit of being set up is made of hiigh pressure stage compressor, hiigh pressure stage cross valve, middle throttling heating power expansion valve, magnetic valve, intercooler and cold-producing medium tube connector.
The double stage compresses hot pump in low temp kind of refrigeration cycle that the utility model proposes and the characteristic feature of device thereof are the devices for drying and filtering in ordinary hot pump installation kind of refrigeration cycle as shown in Figure 1 and heat between the cold-producing medium tube connector of ordering with the A between the point of the B between the heating power expansion valve and cross valve and the refrigerant/water heat exchanger and set up a hiigh pressure stage unit.This heat pump assembly summer cooling condition with general winter heating operating mode under, the hiigh pressure stage unit does not put into operation, the effect operation by the ordinary hot pump installation has the performance and the function of ordinary hot pump installation; When outdoor environment temperature reduces, when causing device performance to descend, heat pump assembly then starts the hiigh pressure stage unit, the single stage compress kind of refrigeration cycle is converted into twin-stage compression refrigeration circulation, increase the degree of supercooling of high pressure liquid refrigerant, reduce the compressor air suction degree of superheat, increase the heating capacity of heat pump assembly effectively, reduce compressor exhaust temperature, result of implementation shows that this heat pump assembly can be stablized in-18 ℃ low temperature environment, long-time running reliably, and have the enough heating capacities and the higher coefficient of performance, compressor exhaust temperature is lower than 130 ℃ all the time, can satisfy the heating demand of cold district.
In the double stage compresses hot pump in low temp device that the utility model proposed, be used in the middle cooling type high pressure receiver replacement high pressure receiver and the intercooler of isolating and having the heat exchange coil of import and export with the high pressure receiver cavity is set in the high pressure receiver, will the simplification device structure, reduce installation cost, improve the reliability of device.
In the double stage compresses hot pump in low temp device that the utility model proposed, the compressor that one of two compressors or the two adopt capacity such as frequency conversion to regulate, regulate the intermediate pressure of heat pump assembly in the time of can moving in the hiigh pressure stage unit, the coefficient of performance of double stage compresses hot pump in low temp device and heating capacity are further improved.
In the double stage compresses hot pump in low temp device that the utility model proposed, replace the refrigerant/water heat exchanger with the refrigerant/air heat exchanger, replace water pump with blower fan, then can utilize air that the cold of cooling condition generation in summer and the heat of winter heating's operating mode generation are directly flowed to indoor environment.
Below in conjunction with the drawings and the specific embodiments technical characterictic of the present utility model further is described.
Accompanying drawing 1 is ordinary hot pump installation refrigerant line catenation principle figure.
Accompanying drawing 2 is double stage compresses hot pump in low temp device embodiment 1 refrigerant line catenation principle figure.
Accompanying drawing 3 is double stage compresses hot pump in low temp device embodiment 2 refrigerant line catenation principle figure.
Accompanying drawing 4 is the middle cooling type high pressure receiver structure charts among the double stage compresses hot pump in low temp device embodiment 2, and wherein figure (a) is its sectional elevation, and figure (b) is its drawing in side sectional elevation.
Accompanying drawing 5 is double stage compresses hot pump in low temp device embodiment 3 refrigerant line catenation principle figure.
Component names in the accompanying drawing is as follows with numbering:
1 compressor; 2 cross valves; 3 refrigerant/air heat exchangers; 4 heat exchanger fan; 5 heat and use heating power expansion valve; 6 check valves; 7 high pressure receivers; 8 cooling heating power expansion valves; 9 check valves; 10 water route tube connectors; 11 refrigerant/water heat exchangers; 12 gas-liquid separators; 13 water pumps; 14 liquid-dividing heads; 15 devices for drying and filtering; 16 hiigh pressure stage unit; 17 hiigh pressure stage compressors; 18 hiigh pressure stage cross valves; Throttling heating power expansion valve in the middle of 19; 20 magnetic valves; 21 intercoolers; Cooling type high pressure receiver in the middle of 22; 23 cylindrical shells; 24 coil heat exchangers; 25/26 highly pressurised liquid advances/drain pipe; 27/28 coil heat exchanger import/export; 29 refrigerant/air heat exchangers; 30 blower fans.
In above-mentioned parts, refrigerant/air heat exchanger 3 and the 29 general fin-tube heat exchangers that adopt; Refrigerant/water heat exchanger 11 general plate type heat exchanger, the double pipe heat exchangers of adopting; Blower fan 30 general axial flow blower, centrifugal blower and the cross flow fans of adopting.
Fig. 2 is the refrigerant line catenation principle figure of one of double stage compresses hot pump in low temp device embodiment of proposing of the utility model.It comprises compressor 1, cross valve 2, refrigerant/air heat exchanger 3, heating power expansion valve 5 and 8, check valve 6 and 9, high pressure receiver 7, device for drying and filtering 15, refrigerant/water heat exchanger 11, gas-liquid separator 12, water pump 13, cold-producing medium tube connector, water route tube connector and the hiigh pressure stage unit 16 that is made of hiigh pressure stage compressor 17, hiigh pressure stage cross valve 18, middle throttling heating power expansion valve 19, magnetic valve 20, intercooler 21 and cold-producing medium tube connector.Comparison diagram 1 and Fig. 2 as can be seen, the double stage compresses hot pump in low temp device that the utility model proposes is to set up hiigh pressure stage unit 16 to constitute on ordinary hot pump installation cold-producing medium connecting line shown in Figure 1.
The hiigh pressure stage unit 16 of described device is connected between the disconnection ordinary hot pump installation cross valve 2 and refrigerant/water heat exchanger 11 as shown in Figure 1, device for drying and filtering 15 outlet and heating with behind the tube connector between heating power expansion valve 5 inlets between formed A, A ', four interfaces of B, B ', and four interface A, A ', B, B ' export with c outlet, highly pressurised liquid tube inlet, highly pressurised liquid pipe with the d outlet of the hiigh pressure stage cross valve 18 of hiigh pressure stage unit 16 respectively and link to each other.
By the double stage compresses hot pump in low temp device that above-mentioned connected mode constituted, not only possess the function and the effect of ordinary hot pump installation, and can be outside low temperature stable under the gas condition, reliably, provide heat to air conditioner water efficiently, to satisfy the heating demand of cold district.The operation principle of this heat pump assembly is as described below under different operating modes:
Summer cooling condition operation principle: under the summer cooling condition, the hiigh pressure stage unit in this double stage compresses hot pump in low temp device quits work; Pairing each the parts compressor 1 of former ordinary hot pump installation, heat exchanger fan 4, water pump 13 operations, cross valve 2 does not power on.The gaseous refrigerant of low-temp low-pressure is collapsed into the gaseous refrigerant of HTHP by compressor 1, flow into refrigerant/air heat exchanger 3 through cross valve 2, cooling, condensation through outdoor air became cold anticyclone liquid, entered in the high pressure receiver 7 by the flow through highly pressurised liquid passage of intercooler 21 of check valve 6 again; Behind the high pressure liquid refrigerant drying filter 15 by high pressure receiver 7 outflows, the throttling step-down becomes the liquid state and the gaseous state mix refrigerant of low-temp low-pressure in cooling heating power expansion valve 8, and enter refrigerant/water heat exchanger 11, the heat of vaporization of recirculated water becomes the gaseous refrigerant of low-temp low-pressure in this liquid refrigerant absorption water route, realizes producing the purpose of cold water; (c → d), cross valve 2, gas-liquid separator 12 return compressor 1 to the gaseous refrigerant of low-temp low-pressure, finish kind of refrigeration cycle through hiigh pressure stage cross valve 18.
The operation principle of general winter heating operating mode: under general winter heating operating mode, the hiigh pressure stage unit in this double stage compresses hot pump in low temp device still quits work; Pairing each the parts compressor 1 of former ordinary hot pump installation, heat exchanger fan 4, water pump 13 operations, cross valve 2 powers on.The gaseous refrigerant of low-temp low-pressure is collapsed into the gaseous refrigerant of HTHP by compressor 1, (d → c), flow into refrigerant/water heat exchanger 11 through cross valve 2, hiigh pressure stage cross valve 18, entrained heat is discharged to recirculated water in the water route with heat cycles water, realize producing the purpose of hot water; The refrigerant vapour of HTHP became cold anticyclone liquid in this cooling, condensation, entered in the high pressure receiver 7 by check valve 9 again; The flow through highly pressurised liquid passage of device for drying and filtering 15, intercooler 21 of the high pressure liquid refrigerant that flows out by high pressure receiver 7, enter and heat liquid state and the gaseous state mix refrigerant that becomes low-temp low-pressure with heating power expansion valve 5 and throttling step-down, enter refrigerant/air heat exchanger 3 again, become the gaseous refrigerant of low-temp low-pressure in the heat of vaporization of this liquid refrigerant absorption chamber outer air, flow through again cross valve 2, gas-liquid separator 12 returns compressor 1, finishes heating circulation.
The operation principle of severe cold winter heating operating mode: under severe cold winter heating operating mode, the hiigh pressure stage unit in this double stage compresses hot pump in low temp device puts into operation, i.e. hiigh pressure stage compressor 17 operations, and hiigh pressure stage cross valve 18, magnetic valve 20 power on; Pairing each the parts compressor 1 of former ordinary hot pump installation, heat exchanger fan 4, water pump 13 operations, cross valve 2 powers on.On the one hand, the gaseous refrigerant of low-temp low-pressure by compressor 1 (can claim that compressor 1 is low-pressure stage compressor 1 this moment) be collapsed into temperature higher in the attitude cold-producing medium of calming the anger, (d → b) flows to the hiigh pressure stage compressor suction duct through cross valve 2, hiigh pressure stage cross valve 18; On the other hand, the high-temperature high-pressure refrigerant that is flowed out into intercooler 21 by high pressure receiver 7 is divided into two-way, sub-fraction is throttling heating power expansion valve 19 in the middle of magnetic valve 20 enters, become the medium temperature and medium pressure coolant channel that enters intercooler 21 behind the gas-liquid mixed refrigerant of medium temperature and medium pressure in this throttling, absorption flow through liquid refrigerant in the intercooler 21 high-temperature high-pressure refrigerant passages heat and evaporate, obtain cold excessively fully with up-to-date style high-temperature high-pressure liquid attitude cold-producing medium, the higher middle compacting refrigerant vapor of the medium temperature and medium pressure refrigerant vapour that evaporates and the temperature that is flowed out by cross valve 2 is mixed, and mixed gaseous refrigerant temperature is between the delivery temperature of the saturation temperature of intermediate pressure correspondence and compressor 1; Mixed gaseous refrigerant enters hiigh pressure stage compressor 17, be compressed into high temperature and high pressure gaseous refrigerant through hiigh pressure stage compressor 17, (a → c) flows into refrigerant/water heat exchanger 11 through hiigh pressure stage cross valve 18 again, entrained heat is discharged to recirculated water in the water route with heat cycles water, realize producing the purpose of hot water; The refrigerant vapour of HTHP becomes high temperature high pressure liquid in this cooling, condensation, enters in the high pressure receiver 7 by check valve 9 again; Enter the medium temperature and medium pressure coolant channel of intercooler 21 through magnetic valve 20, middle throttling heating power expansion valve 19 by the high pressure liquid refrigerant sub-fraction of high pressure receiver 7 outflows, most of high pressure liquid refrigerant intercooler 21 high-temperature high-pressure refrigerant passages of flowing through absorb the evaporation latent heat of medium temperature and medium pressure coolant channel inner refrigerant and realize significantly cold excessively; Obtain cold fully excessively high pressure liquid refrigerant, through heating liquid state and gaseous state mix refrigerant with heating power expansion valve 5 throttling step-downs becoming low-temp low-pressure, enter refrigerant/air heat exchanger 3 again, become the gaseous refrigerant of low-temp low-pressure in the heat of vaporization of this liquid refrigerant absorption chamber outer air, flow through again cross valve 2, gas-liquid separator 12 returns compressor 1, finishes heating circulation.Because the suction temperature of hiigh pressure stage compressor 17 is lower than the delivery temperature of (low-pressure stage) compressor 1, make that the delivery temperature of hiigh pressure stage compressor 17 is more direct by the compressor 1 independent delivery temperature of compressing than not adopting hiigh pressure stage unit 16, thereby improved the reliability of heat pump assembly, thereby guaranteed heat pump assembly stable operation in low temperature environment for a long time; On the other hand, though entering the mass flow of the liquid refrigerant of refrigerant/air heat exchanger 3 reduces to some extent, but compress the work done during compression of having saved the unit mass cold-producing medium because of twin-stage, increased considerably the degree of supercooling of the liquid refrigerant that enters refrigerant/air heat exchanger 3 simultaneously, make the unit mass cold-producing medium can from air, obtain more heat, thereby improved the coefficient of performance and the heating capacity of the operation of heat pump ultralow temperature operating mode.
High pressure receiver in the double stage compresses hot pump in low temp device shown in Figure 27 and intercooler 21 are integrated into middle cooling type high pressure receiver 22 among Fig. 3, can obtain another embodiment of this invention, as shown in Figure 3.The supercooling process that this embodiment removes the liquid cold-producing medium of HTHP occurs in inside and outside the high pressure receiver its operation principle and embodiment illustrated in fig. 2 identical.Cooling type high pressure receiver 22 replaces high pressure receiver 7 and intercooler 21 in the middle of adopting, and with the simplification device form, reduces installation cost, improves the reliability of device.
Fig. 4 has provided a kind of structural principle sketch of middle cooling type high pressure receiver 22, and wherein figure (a) is its sectional elevation, and figure (b) is its drawing in side sectional elevation.Middle cooling type high pressure receiver 22 is made of liquid reservoir cylindrical shell 23, coil heat exchanger 24, highly pressurised liquid feed tube 25 and drain pipe 26 4 parts; Its coil heat exchanger 24 is arranged on liquid reservoir cylindrical shell 23 inside and is not communicated with liquid reservoir cylindrical shell 23 inside, and stretch out outside the liquid reservoir cylindrical shell 23 its import/export 27/28.The import 27 of coil heat exchanger 24 links to each other with the outlet of middle throttling heating power expansion valve 19, its b outlet connecting pipe that exports 28 tube connectors and hiigh pressure stage cross valve 18 converges, together be connected with hiigh pressure stage compressor 17 air intake ducts, not only can realize the comprehensive function of high pressure receiver 7 and intercooler 21, and guarantee the 17 effective oil returns of hiigh pressure stage compressor.
In the double stage compresses hot pump in low temp device that the utility model proposed, replace refrigerant/water heat exchanger 11 with refrigerant/air heat exchanger 29, replace water pump 13 with blower fan 30, then can utilize air that the cold of cooling condition generation in summer and the heat of winter heating's operating mode generation are directly flowed to indoor environment, this is the another embodiment of the double stage compresses hot pump in low temp device that the utility model proposes, as shown in Figure 5.In this embodiment, do not need the cold/heat of cold-producing medium is passed to aqueous medium earlier, cold/heat transferred the indoor environment of aqueous medium being carried again by indoor end-equipment, and cold-producing medium directly is directly passed to air dielectric with its cold/heat that carries by refrigerant/air heat exchanger 29, if refrigerant/air heat exchanger 29 and blower fan 30 are arranged on indoor, then cold-producing medium directly and room air carry out heat exchange, to the entrained cold/heat of indoor release cold-producing medium; If it is outdoor that refrigerant/air heat exchanger 29 and blower fan 30 are arranged on, then need utilize outer air duct to send into indoor environment through the air after refrigerant/air heat exchanger 29 cooling.
In the double stage compresses hot pump in low temp device shown in Fig. 2,3,5 that the utility model proposed, the compressor that one of two compressors 1,17 or the two adopt capacity such as frequency conversion to regulate, regulate the intermediate pressure of heat pump assembly in the time of can moving in the hiigh pressure stage unit, increase the circulating mass of refrigerant of low-pressure stage, can further improve the coefficient of performance and the heating capacity of double stage compresses hot pump in low temp device.
The utility model has been obtained good effect.Adopt the heat pump assembly of this device scheme not only to have performance and the function of ordinary hot pump installation under summer and general winter condition, and can in-18 ℃ low temperature environment, stablize, long-time running reliably, and have the enough heating capacities and the higher coefficient of performance, compressor exhaust temperature is lower than 130 ℃ all the time, can not have to satisfy the cold district heating requirement in winter under the condition of auxiliary thermal source.
Claims (7)
1. one kind is suitable for the double stage compresses hot pump in low temp device that cold district uses, it comprises compressor (1), cross valve (2), refrigerant/air heat exchanger (3), heating power expansion valve (5,8), check valve (6,9), high pressure receiver (7), device for drying and filtering (15), refrigerant/water heat exchanger (11), gas-liquid separator (12), water pump (13), cold-producing medium tube connector, water route tube connector and hiigh pressure stage unit (16), it is characterized in that: include hiigh pressure stage compressor (17) in hiigh pressure stage unit (16).
2. according to the described double stage compresses hot pump in low temp device of claim 1, it is characterized in that: described hiigh pressure stage unit (16) is made of with the cold-producing medium tube connector hiigh pressure stage compressor (17), hiigh pressure stage cross valve (18), middle throttling heating power expansion valve (19), magnetic valve (20), intercooler (21).
3. according to the described double stage compresses hot pump in low temp device of claim 1, it is characterized in that: described system be break between cross valve (2) and the refrigerant/water heat exchanger (11) at the ordinary hot pumping system, device for drying and filtering (15) exports and heats to export with c outlet, highly pressurised liquid tube inlet, highly pressurised liquid pipe with hiigh pressure stage cross valve (18) the d outlet of hiigh pressure stage unit (16) with formed A, A ', four interfaces of B, B ' behind the tube connector between heating power expansion valve (5) import and link to each other respectively.
4. according to the described double stage compresses hot pump in low temp device of claim 1, it is characterized in that: replace high pressure receiver (7) and intercooler (21) with middle cooling type high pressure receiver (22).
5. according to the described double stage compresses hot pump in low temp device of claim 4, it is characterized in that: cooling type high pressure receiver (22) is made of liquid reservoir cylindrical shell (23), coil heat exchanger (24), highly pressurised liquid feed tube (25) and drain pipe (26) four parts in the middle of described, its coil heat exchanger (24) is arranged on liquid reservoir cylindrical shell (23) inside and is not communicated with liquid reservoir cylindrical shell (23) inside, and its import (27) is stretched out outside the liquid reservoir cylindrical shell (23) with outlet (28).
6. according to the described double stage compresses hot pump in low temp device of claim 1, it is characterized in that: the compressor that one of compressor (1) and hiigh pressure stage compressor (17) or the two adopt capacity such as frequency conversion to regulate.
7. according to the described double stage compresses hot pump in low temp device of claim 1, it is characterized in that: refrigerant/water heat exchanger (11) and water pump (13) can be replaced by refrigerant/air heat exchanger (29) and blower fan (30) respectively.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 02200545 CN2530221Y (en) | 2002-01-11 | 2002-01-11 | Double-staged compression low temp heat pump appts. |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 02200545 CN2530221Y (en) | 2002-01-11 | 2002-01-11 | Double-staged compression low temp heat pump appts. |
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| Publication Number | Publication Date |
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| CN2530221Y true CN2530221Y (en) | 2003-01-08 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN 02200545 Expired - Fee Related CN2530221Y (en) | 2002-01-11 | 2002-01-11 | Double-staged compression low temp heat pump appts. |
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Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107726656A (en) * | 2017-11-08 | 2018-02-23 | 郑州云宇新能源技术有限公司 | The refrigerant heat pump system of single twin-stage conversion can be carried out |
| CN111023227A (en) * | 2019-11-21 | 2020-04-17 | 东南大学 | Double-stage compression heat source tower heat pump system suitable for cold areas |
| CN112050492A (en) * | 2020-09-25 | 2020-12-08 | 浙江国祥股份有限公司 | Energy-saving constant temperature and humidity unit |
-
2002
- 2002-01-11 CN CN 02200545 patent/CN2530221Y/en not_active Expired - Fee Related
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107726656A (en) * | 2017-11-08 | 2018-02-23 | 郑州云宇新能源技术有限公司 | The refrigerant heat pump system of single twin-stage conversion can be carried out |
| CN111023227A (en) * | 2019-11-21 | 2020-04-17 | 东南大学 | Double-stage compression heat source tower heat pump system suitable for cold areas |
| CN111023227B (en) * | 2019-11-21 | 2021-06-25 | 东南大学 | Double-stage compression heat source tower heat pump system suitable for cold areas |
| CN112050492A (en) * | 2020-09-25 | 2020-12-08 | 浙江国祥股份有限公司 | Energy-saving constant temperature and humidity unit |
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