CN101737997B - Single-efficiency absorption type refrigerating device with expander-compressor - Google Patents
Single-efficiency absorption type refrigerating device with expander-compressor Download PDFInfo
- Publication number
- CN101737997B CN101737997B CN200910154365.9A CN200910154365A CN101737997B CN 101737997 B CN101737997 B CN 101737997B CN 200910154365 A CN200910154365 A CN 200910154365A CN 101737997 B CN101737997 B CN 101737997B
- Authority
- CN
- China
- Prior art keywords
- heat exchange
- absorber
- exchange member
- expander
- compressor
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Fee Related
Links
Landscapes
- Sorption Type Refrigeration Machines (AREA)
Abstract
The invention discloses a single-efficiency absorption type refrigerating device with an expander-compressor, comprising a generator, a preheater, a rectifier, a condenser, a second throttle valve, an evaporator, an expander-compressor, an absorber, a solution pump, a solution heat exchanger, a fourth throttle valve and two middle heat exchange parts, wherein the generator, the preheater, the rectifier, the condenser, a first middle heat exchange part, the second throttle valve, the evaporator, the expander-compressor, the absorber, the solution pump and the solution heat exchanger are sequentially connected; the generator, the second middle heat exchange part, the solution heat exchanger, the fourth throttle valve and the absorber are sequentially connected; a gas-phase outlet of the first middle heat exchange part, the preheater, the expander-compressor and the absorber are sequentially connected; and a gas-phase outlet of the second middle heat exchange part, the expander-compressor and the absorber are sequentially connected. In the invention, work produced by the device is utilized to compress steam at the outlet of the evaporator to improve the working pressure of the absorber so as to ensure that the device can prepare cold quantity having a higher grade than that prepared by a traditional single effect absorption type refrigerating device.
Description
Technical field
The invention belongs to refrigeration technology field, relate to a single-effective absorption refrigerating plant and system thereof, in particular to the single-effective absorption refrigerating plant of band expansion compressor capable, this device realizes the single-effective absorption refrigerating plant increasing absorber operating pressure and reduce cryogenic temperature by expansion compressor capable and intermediate heat exchange member.This device is particularly useful for the single-effective absorption refrigerating plant producing low temperature cold with low grade heat energy.
Background technology
Since Frenchman Ka Er invention continuity absorption refrigerating machine in 1860, Absorption Refrigerator is just always in the market in occupation of consequence.In recent years along with the environmental problem such as greenhouse effects and depletion of the ozone layer is day by day serious on the impact of the mankind, and refrigeration system consumes too much electric energy, people more and more pay attention to the utilization to the regenerative resource that solar energy etc. cleans, and drive the absorption refrigeration of refrigeration to receive larger concern as utilizing solar heat.
Although the collection that solar heat can be unlimited, in general the efficiency of solar energy energy heat collector reduces with providing the raising of thermal temperature.Common flat plate collector generally can only provide the heat source temperature of less than 100 degree.Therefore the most general still single-action and the multistage absorption type refrigerating unit that adopt at present.The absorption of single-action is that refrigerating plant is used for producing the higher cold of evaporating temperature, but the cold can not produced when heat source temperature is limited under lower evaporating temperature, and although multistage absorption refrigerating device can produce the cold under lower temperature, much lower than traditional single-effective absorption refrigerating plant of its performance under higher evaporating temperature.
Summary of the invention
The object of the invention is the deficiency for prior art existence and defect, a kind of single-effective absorption refrigerating plant of band expansion compressor capable is newly proposed, it is made both to have had the performance of traditional single-effective absorption refrigerating plant under higher cryogenic temperature, cold under simultaneously making this device can produce lower evaporating temperature, and keep higher performance.
Single-effective absorption refrigerating plant with expansion compressor capable comprises generator, preheater, rectifier, condenser, second throttle, evaporimeter, expansion compressor capable, absorber, solution pump, solution heat exchanger, the 4th choke valve, the first intermediate heat exchange member, the second intermediate heat exchange member; Generator, preheater, rectifier, condenser, the first intermediate heat exchange member, second throttle, evaporimeter, expansion compressor capable, absorber, solution pump, solution heat exchanger connect in turn, generator, the second intermediate heat exchange member, solution heat exchanger, the 4th choke valve, absorber connect in turn, the gaseous phase outlet of the first intermediate heat exchange member is connected in turn with preheater, expansion compressor capable, absorber, and the gaseous phase outlet of the second intermediate heat exchange member is connected in turn with expansion compressor capable, absorber; The first described intermediate heat exchange member is the first throttle valve and the first container that are connected; The second described intermediate heat exchange member is the 3rd choke valve and the second container be connected.
This device compares traditional single-effective absorption refrigerating plant, can significantly increase the interval of producing temperature, obtains the many cold lower than traditional absorption type refrigerating unit temperature.Compare traditional single-effective absorption refrigerating plant, refrigerant vapour due to evaporator outlet can be pressed onto a higher pressure by compressor and flow to absorber again, therefore when identical absorption pressure, the outlet pressure of evaporimeter can be low more than traditional absorption type refrigerating unit, thus produce the many cold lower than traditional single-effective absorption refrigerating plant evaporating temperature.New refrigerating plant is when best middle pressure runs, can not only guarantee there is the performance being not less than traditional single-effective absorption refrigerating plant under higher evaporating temperature, and the efficiency of new equipment also can have the systematic function higher than traditional twin-stage absorption type refrigerating unit producing the cold under low temperature when the efficiency of expansion compressor capable reaches certain value time.
Accompanying drawing explanation
Fig. 1 is the single-effective absorption refrigerating device structure schematic diagram of band expansion compressor capable;
The single-effective absorption refrigerating plant example structure schematic diagram of Fig. 2 band expansion compressor capable;
In figure: generator 1, preheater 2, rectifier 3, condenser 4, first throttle valve 5, first container 6, second throttle 7, evaporimeter 8, expansion compressor capable 9, absorber 10, solution pump 11, solution heat exchanger 12, the 3rd choke valve 13, second container 14, the 4th choke valve 15, first intermediate heat exchange member 16, second intermediate heat exchange member 17
Detailed description of the invention
As shown in Figure 1, the single-effective absorption refrigerating plant of expansion compressor capable is with to comprise generator 1, preheater 2, rectifier 3, condenser 4, second throttle 7, evaporimeter 8, expansion compressor capable 9, absorber 10, solution pump 11, solution heat exchanger 12, the 4th choke valve 15, first intermediate heat exchange member 16, second intermediate heat exchange member 17; Generator 1, preheater 2, rectifier 3, condenser 4, first intermediate heat exchange member 16, second throttle 7, evaporimeter 8, expansion compressor capable 9, absorber 10, solution pump 11, solution heat exchanger 12 connect in turn, generator 1, second intermediate heat exchange member 17, solution heat exchanger 12, the 4th choke valve 15, absorber 10 connect in turn, the gaseous phase outlet of the first intermediate heat exchange member 16 is connected in turn with preheater 2, expansion compressor capable 9, absorber 10, and the gaseous phase outlet of the second intermediate heat exchange member 17 is connected in turn with expansion compressor capable 9, absorber 10; The first described intermediate heat exchange member 16 is the first throttle valve 5 that is connected and the first container 6; The second described intermediate heat exchange member 17 is the 3rd choke valve 13 that is connected and second container 14.
Condensator outlet high-pressure refrigerant flows to the first intermediate heat exchange member, and the gaseous phase outlet of intermediate heat exchange member is the refrigerant vapour of intermediate pressure, is preheated after device is heated to higher temperature and flows to expansion generation merit inside expansion compressor capable.
The dense absorbent solution of generator taphole flows to the second intermediate heat exchange member, and the gaseous phase outlet of intermediate heat exchange member is the steam of intermediate pressure, flows to expansion inside expansion compressor capable and produces merit.
First intermediate heat exchange member and the second intermediate heat exchange member have two Main Functions, first effect makes system works under best intermediate pressure, because when evaporating pressure is determined, along with the increase of intermediate pressure, the inlet pressure of decompressor can be made to increase on the one hand, absorption pressure is made to have the trend of increase, the steam flow of decompressor can be made to reduce simultaneously, absorption pressure is made to have the trend of minimizing, therefore there is a best intermediate pressure to make absorption pressure to reach maximum, reaching this object by regulating intermediate heat exchange member.
As Fig. 2 shows, generator 1 gaseous phase outlet in the single-effective absorption refrigerating plant of band expansion compressor capable and preheater 2, rectifier 3, condenser 4, first throttle valve 5, with the first container 6, second throttle 7, evaporimeter 8, expansion compressor capable 9, absorber 10, solution pump 11, solution heat exchanger 12, the cryogenic fluid entrance of solution heat exchanger 1 connects in turn, with gaseous phase outlet and the preheater 2 of the first container 6, expansion compressor capable 9, the gas access of absorber 10 connects in turn, the taphole of generator 1 and the 3rd choke valve 13 and second container 14, solution heat exchanger 12, 4th choke valve 15, the solution inlet of absorber 10 connects in turn, the gaseous phase outlet of second container 14 and expansion compressor capable 9, the gas access of absorber 10 connects in turn.
Embodiment using ammonia-device of working medium to as working medium, analog computation has been carried out to the performance of new equipment and traditional single stage absorption type refrigerating unit, suppose in analog computation that condensation temperature and absorber absorb finishing temperature equal, generator and absorber outlet solution are saturated solution.Condensator outlet degree of supercooling is 2 degree, and evaporator outlet is saturated ammonia.Table 1 is the Performance comparision of traditional single-action/twin-stage absorption type refrigerating unit and new absorption type refrigerating unit under different evaporating temperature.
The Performance comparision of each device of table 1 under different evaporating temperature
| η | / | / | / | / | / | 0.6 | 0.8 | 1 |
| Parameter | T g | T k | T e | COP t1 | COP t2 | COP n | COP n | COP n |
| Unit | K | K | K | / | / | / | / | / |
| Operating mode 1 | 370 | 313 | 223 | 0 | 0 | 0.1089 | 0.1355 | 0.1574 |
| Operating mode 2 | 370 | 313 | 228 | 0 | 0.0988 | 0.1244 | 0.1517 | 0.1771 |
| Operating mode 3 | 370 | 313 | 233 | 0 | 0.1519 | 0.1426 | 0.1721 | 0.1962 |
| Operating mode 4 | 370 | 313 | 238 | 0 | 0.1816 | 0.1624 | 0.1951 | 0.2118 |
| Operating mode 5 | 370 | 313 | 243 | 0 | 0.2019 | 0.1889 | 0.2211 | 0.2479 |
| Operating mode 6 | 370 | 313 | 248 | 0 | 0.2191 | 0.2183 | 0.2517 | 0.2710 |
| Operating mode 7 | 370 | 313 | 253 | 0 | 0.2359 | 0.2540 | 0.2875 | 0.3162 |
| Operating mode 8 | 370 | 313 | 258 | 0 | 30.2502 | 0.2992 | 0.3296 | 0.3530 |
| Operating mode 9 | 370 | 313 | 263 | 0 | 0.2658 | 0.3507 | 0.3767 | 0.3958 |
| Operating mode 10 | 370 | 313 | 268 | 0.2599 | 0.2821 | 0.4105 | 0.4285 | 0.4419 |
| Operating mode 11 | 370 | 313 | 273 | 0.4701 | 0.2995 | 0.4779 | 0.4855 | 0.4926 |
| Operating mode 12 | 370 | 313 | 278 | 0.5415 | 0.3170 | 0.5415 | 0.5415 | 0.5415 |
η in table 1 represents the isentropic efficiency of expansion compressor capable, T
grepresent and finishing temperature occurs, T
krepresent condensation temperature and absorb finishing temperature, T
erepresent evaporating temperature, COP
t1represent the coefficient of performance of traditional single-effective absorption refrigerating plant, COP
t2represent traditional twin-stage absorption type refrigerating unit coefficient of performance, COP
nrepresent the coefficient of performance of new equipment.As can be seen from Table 1 along with the increase of evaporating temperature, the coefficient of performance of three kinds of devices is all continuous increase, compares traditional single-effective absorption refrigerating plant, and under the condition of supposition, new equipment can obtain the cold at much lower temperature.As can be seen from the table, when evaporating temperature drops to 263K time, tradition single-effective absorption refrigerating plant can not produce cold, and new equipment is when evaporating temperature drops to 223K, its coefficient of performance still can reach more than 0.1, this is because the refrigerant vapour of evaporator outlet can be pressed onto higher pressure by compressor by new equipment, thus the pressure of absorber can be improved and absorb the refrigerant concentration of end of a period solution, and then the cold can produced under lower temperature, and under identical evaporating temperature, because the absorption pressure of new equipment is higher, make its recycle ratio lower than traditional single-effective absorption refrigerating plant, therefore the coefficient of performance also may be higher.The operating pressure of new equipment has four pressure, absorption pressure and intermediate pressure is also had except condensing pressure and evaporating pressure, intermediate pressure refers to the pressure of the entrance mist of expansion compressor capable decompressor, so the increase of intermediate pressure, the pressure reduction that decompressor is imported and exported has the trend of increase, the expansion work that the mist of unit mass flow is produced has the trend of increase, the increase of intermediate pressure simultaneously, also the mass flow of the entrance mist of decompressor can be made to have the trend of minimizing, therefore maximum expansion works to be produced, there is the intermediate pressure that best, now the recycle ratio of system can drop to minimum, also to consider the reduction along with intermediate pressure simultaneously, the inlet temperature of the pyrosol of System Solution heat exchanger can reduce gradually, the generator inlet solution temperature of system now can be made to have the trend of reduction, this will increase the generation heat of unit solution, therefore system intermediate pressure will minimum than recycle ratio time intermediate pressure high.Along with the increase of evaporating temperature, intermediate pressure has ever-increasing trend, when evaporating temperature is increased to certain value time, the best intermediate pressure of system equals the condensing pressure of system, now the expansion compressor capable of system will not work, system is equivalent to traditional single-effective absorption refrigerating plant, as the operating mode 12 of table 1.As can be seen from table 1 also, new equipment is compared with traditional twin-stage absorption type refrigerating unit, not only at high evaporation temperature, there is the higher coefficient of performance, and when lower evaporating temperature, if time the efficiency of the expansion compressor capable of new system reaches certain value, the coefficient of performance of new equipment is also by higher than the coefficient of performance of traditional twin-stage absorption type refrigerating unit.This is because the refrigerant vapour of new equipment only needs to occur once, and the refrigerant vapour of traditional twin-stage absorption type refrigerating unit needs generation twice.Also can find out that new equipment can be produced than the cold traditional double stage refrigerating device lower temperature from table 1.
What table 2 showed is that the coefficient of performance of each device under difference generation finishing temperature compares, symbol in table is identical with the meaning of the symbol in table 1, can see from table 2, the coefficient of performance of each device along with the increase that finishing temperature occurs be all first increase rear minimizing, this is because can reduce along with the increase recycle ratio of occurrence temperature, thus make COP have the trend of increase, but along with the increase of occurrence temperature, the rectifying loss of each device also can increase gradually, therefore, when occurrence temperature is greater than certain value time, the coefficient of performance of each device can slowly reduce.As can be seen from Table 2, under identical working condition, in order to produce the cold of 258K, traditional single-effective absorption refrigerating plant needs the generation finishing temperature more than 100 degree (385K), and general flat plate collector can not provide the heat of this grade, new absorption type refrigerating unit then normally can work when occurrence temperature is lower than 70 degree (340K).Can also see from table 2, lower in occurrence temperature, time traditional single-effective absorption refrigerating plant can not produce cold, when the efficiency of expansion compressor capable reaches certain value, new equipment will have the coefficient of performance higher than traditional twin-stage absorption type refrigerating unit.
The Performance comparision of each device of table 2 under difference generation finishing temperature
| η | / | / | / | / | / | 0.6 | 0.8 | 1 |
| Parameter | T g | T k | T e | COP t1 | COP t2 | COP n | COP n | COP n |
| Unit | K | K | K | / | / | / | / | / |
| Operating mode 1 | 340 | 313 | 258 | 0 | 0 | 0.0847 | 0.1082 | 0.1297 |
| Operating mode 2 | 345 | 313 | 258 | 0 | 0 | 0.1185 | 0.1492 | 0.1770 |
| Operating mode 3 | 350 | 313 | 258 | 0 | 0.1930 | 0.1533 | 0.1855 | 0.2138 |
| Operating mode 4 | 355 | 313 | 258 | 0 | 0.2366 | 0.1899 | 0.2273 | 0.2561 |
| Operating mode 6 | 360 | 313 | 258 | 0 | 0.2488 | 0.2306 | 0.2677 | 0.2963 |
| Operating mode 7 | 365 | 313 | 258 | 0 | 0.2511 | 0.2668 | 0.3015 | 0.3288 |
| Operating mode 8 | 370 | 313 | 258 | 0 | 0.2502 | 0.2992 | 0.3296 | 0.3530 |
| Operating mode 9 | 375 | 313 | 258 | 0 | 0.2474 | 0.3305 | 0.3559 | 0.3746 |
| Operating mode 10 | 380 | 313 | 258 | 0 | 0.2446 | 0.3532 | 0.3730 | 0.3873 |
| Operating mode 11 | 385 | 313 | 258 | 0.2374 | 0.2407 | 0.3674 | 0.3832 | 0.3940 |
| Operating mode 12 | 390 | 313 | 258 | 0.3516 | 0.2376 | 0.3807 | 0.3894 | 0.3969 |
| Operating mode 13 | 395 | 313 | 258 | 0.3793 | 0.2333 | 0.3881 | 0.3925 | 0.3964 |
| Operating mode 14 | 400 | 313 | 258 | 0.3832 | 0.2266 | 0.3842 | 0.3868 | 0.3891 |
| Operating mode 15 | 405 | 313 | 258 | 0.3743 | 0.2158 | 0.3743 | 0.3746 | 0.3761 |
| Operating mode 16 | 410 | 313 | 258 | 0.3589 | 0.2031 | 0.3589 | 0.3589 | 0.3592 |
In addition, in the present invention, the merit of solution pump also can be provided by decompressor, and such whole system will not need the external world to provide electric energy, thus can save precious electric energy.For not needing the working medium of rectifying to such as ammonia-sodium sulfocyanate, only rectifier need be removed.
Claims (1)
1. the single-effective absorption refrigerating plant with expansion compressor capable, is characterized in that comprising generator (1), preheater (2), rectifier (3), condenser (4), second throttle (7), evaporimeter (8), expansion compressor capable (9), absorber (10), solution pump (11), solution heat exchanger (12), the 4th choke valve (15), the first intermediate heat exchange member (16), the second intermediate heat exchange member (17), generator (1), preheater (2), rectifier (3), condenser (4), first intermediate heat exchange member (16), second throttle (7), evaporimeter (8), expansion compressor capable (9), absorber (10), solution pump (11), solution heat exchanger (12) connects in turn, generator (1), second intermediate heat exchange member (17), solution heat exchanger (12), 4th choke valve (15), absorber (10) connects in turn, the gaseous phase outlet of the first intermediate heat exchange member (16) and preheater (2), expansion compressor capable (9), absorber (10) connects in turn, the gaseous phase outlet of the second intermediate heat exchange member (17) and expansion compressor capable (9), absorber (10) connects in turn, described the first intermediate heat exchange member (16) is the first throttle valve (5) that is connected and the first container (6), described the second intermediate heat exchange member (17) is the 3rd choke valve (13) that is connected and second container (14).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN200910154365.9A CN101737997B (en) | 2009-11-30 | 2009-11-30 | Single-efficiency absorption type refrigerating device with expander-compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN200910154365.9A CN101737997B (en) | 2009-11-30 | 2009-11-30 | Single-efficiency absorption type refrigerating device with expander-compressor |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN101737997A CN101737997A (en) | 2010-06-16 |
| CN101737997B true CN101737997B (en) | 2015-05-06 |
Family
ID=42461797
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN200910154365.9A Expired - Fee Related CN101737997B (en) | 2009-11-30 | 2009-11-30 | Single-efficiency absorption type refrigerating device with expander-compressor |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN101737997B (en) |
Families Citing this family (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102230686A (en) * | 2011-06-12 | 2011-11-02 | 浙江理工大学 | Lithium bromide absorption-compression type series boosting refrigeration/heating pump system |
| CN103398501B (en) * | 2013-07-29 | 2015-06-10 | 中国科学院理化技术研究所 | Composite refrigeration system with main refrigeration system pre-cooling by heat driven absorption refrigerating |
| CN104048450A (en) * | 2014-06-23 | 2014-09-17 | 周永奎 | Absorption type heat pump refrigeration and power combined supply method and device thereof |
| CN105841401B (en) * | 2015-04-13 | 2020-04-07 | 李华玉 | First-class thermally driven compression-absorption heat pump |
| CN106123393B (en) * | 2015-06-08 | 2019-11-12 | 李华玉 | 4th class thermal drivers compressing-absorbing type heat pump |
| CN106152599B (en) * | 2015-06-08 | 2019-11-12 | 李华玉 | 4th class thermal drivers compressing-absorbing type heat pump |
| CN107525301B (en) * | 2017-08-18 | 2020-07-24 | 中原工学院 | Novel absorption-injection composite refrigerating system |
| US10612821B1 (en) | 2018-07-03 | 2020-04-07 | Kalindha Rashmi LLC | Heat-pump system with combined vapor expansion-compression stages and single-effect vapor absorption unit |
| US11221161B1 (en) | 2018-07-03 | 2022-01-11 | Kalindha Rashmi LLC | Heat-pump system with combined vapor expansion-compression stages and single-effect vapor absorption unit |
| CN112880230B (en) * | 2021-04-29 | 2021-07-02 | 湖南大学 | Power generation and refrigeration combined system |
| CN113375360B (en) * | 2021-05-06 | 2023-06-20 | 郑喜勋 | Multistage cascade solution adjusting device and method |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1199456A (en) * | 1995-10-14 | 1998-11-18 | 阿伯索泰克节能体系有限两合公司 | Sorption heat converter system with additional components |
| US6715290B1 (en) * | 2002-12-31 | 2004-04-06 | Donald C. Erickson | Fluid mixture separation by low temperature glide heat |
| JP2009047354A (en) * | 2007-08-20 | 2009-03-05 | Osaka Gas Co Ltd | Combined heat pump system |
| CN101506596A (en) * | 2006-01-16 | 2009-08-12 | 雷克索斯热离子学公司 | High efficiency absorption heat pump and methods of use |
-
2009
- 2009-11-30 CN CN200910154365.9A patent/CN101737997B/en not_active Expired - Fee Related
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1199456A (en) * | 1995-10-14 | 1998-11-18 | 阿伯索泰克节能体系有限两合公司 | Sorption heat converter system with additional components |
| US6715290B1 (en) * | 2002-12-31 | 2004-04-06 | Donald C. Erickson | Fluid mixture separation by low temperature glide heat |
| CN101506596A (en) * | 2006-01-16 | 2009-08-12 | 雷克索斯热离子学公司 | High efficiency absorption heat pump and methods of use |
| JP2009047354A (en) * | 2007-08-20 | 2009-03-05 | Osaka Gas Co Ltd | Combined heat pump system |
Also Published As
| Publication number | Publication date |
|---|---|
| CN101737997A (en) | 2010-06-16 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN101737997B (en) | Single-efficiency absorption type refrigerating device with expander-compressor | |
| CN100491866C (en) | Multistage-cascaded compression type heat pump set under large temperature difference | |
| CN101520250B (en) | Efficient two-stage absorption refrigerating device | |
| CN102230702B (en) | Two-stage ejection refrigeration cycle system with economizer | |
| CN101776347B (en) | Absorption type refrigerating unit with pressure recovery part | |
| CN202133176U (en) | Two-stage injection refrigeration circulating system with economizer | |
| CN103615824A (en) | Method and device for obtaining cooling capacities of multiple temperature zones based on expansion work recycling drive | |
| CN116558145A (en) | Refrigerating system adopting double ejectors | |
| CN208871901U (en) | Not exclusively cooling two-stage compression heat pump system among second throttle | |
| CN113587471B (en) | Double-stage compression and absorption type high-temperature heat pump combined cold and heat combined supply system | |
| CN110296625B (en) | Parallel-type cold-heat-electricity three-cogeneration Kazakh circulating system | |
| CN204006779U (en) | A kind of efficient HGAX absorption type refrigerating unit | |
| CN211823239U (en) | Ultra-low temperature transcritical cascade refrigeration system | |
| CN109708337B (en) | Multistage series compression heat pump unit | |
| CN210004626U (en) | ground source heat pump heat recovery unit with high-efficiency throttling system | |
| CN112923423A (en) | Heat pump heating system with solar heat energy and air heat energy complementary | |
| CN112963979A (en) | Overlapping heat pump system capable of realizing work cycle conversion | |
| CN112303958A (en) | High-efficiency refrigerating and heating equipment | |
| CN1260535C (en) | Small gas air conditioner with air cooling | |
| CN113294928B (en) | Absorption refrigeration system matched with compressor | |
| CN104197575B (en) | Efficient HGAX absorption refrigeration device | |
| CN219264605U (en) | Coupling heat pump double-circulation energy-saving system and three-circulation energy-saving system without condensing heat emission | |
| CN115507564B (en) | Compound absorption refrigeration system with two-stage evaporation | |
| CN111520202B (en) | Combined cooling, heating and power system with condensation decoupling and cascade evaporation coupling | |
| CN116085993A (en) | Waste heat recovery method for air source heat pump |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20150506 Termination date: 20171130 |
|
| CF01 | Termination of patent right due to non-payment of annual fee |