CN201407856Y - Dual temperature refrigeration cycle system - Google Patents
Dual temperature refrigeration cycle system Download PDFInfo
- Publication number
- CN201407856Y CN201407856Y CN2009200140730U CN200920014073U CN201407856Y CN 201407856 Y CN201407856 Y CN 201407856Y CN 2009200140730 U CN2009200140730 U CN 2009200140730U CN 200920014073 U CN200920014073 U CN 200920014073U CN 201407856 Y CN201407856 Y CN 201407856Y
- Authority
- CN
- China
- Prior art keywords
- compressor
- cycle system
- refrigeration cycle
- intercooler
- duel
- 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 - Lifetime
Links
- 238000005057 refrigeration Methods 0.000 title claims abstract description 43
- 230000009977 dual effect Effects 0.000 title abstract 2
- 239000007788 liquid Substances 0.000 claims abstract description 38
- 238000001816 cooling Methods 0.000 claims description 8
- 238000010438 heat treatment Methods 0.000 claims description 2
- 238000001704 evaporation Methods 0.000 abstract description 18
- 230000008020 evaporation Effects 0.000 abstract description 8
- 230000000694 effects Effects 0.000 abstract 1
- 239000003921 oil Substances 0.000 description 13
- 230000006835 compression Effects 0.000 description 7
- 238000007906 compression Methods 0.000 description 7
- 238000007710 freezing Methods 0.000 description 5
- 230000008014 freezing Effects 0.000 description 5
- 235000013305 food Nutrition 0.000 description 4
- 239000010725 compressor oil Substances 0.000 description 2
- 238000000034 method Methods 0.000 description 2
- 235000013311 vegetables Nutrition 0.000 description 2
- 230000007812 deficiency Effects 0.000 description 1
- 235000013399 edible fruits Nutrition 0.000 description 1
- 239000004744 fabric Substances 0.000 description 1
- 239000010687 lubricating oil Substances 0.000 description 1
- 235000013372 meat Nutrition 0.000 description 1
- 230000000306 recurrent effect Effects 0.000 description 1
- 239000003507 refrigerant Substances 0.000 description 1
Images
Landscapes
- Compressor (AREA)
Abstract
The utility model relates to a dual temperature refrigeration cycle system, which comprises compressors, a condenser, an evaporator, a liquid storage device, an oil separator, a liquid tube solenoid valve, a gas-liquid separator and an expansion valve, wherein the system comprises two compressors which are used for the switching of single-stage or two-stage operation by two tee solenoid valves andan intercooler, and the two interfaces of the first tee solenoid valve of the two tee solenoid valves are connected with the pipeline of the exhaust end of the first compressor; the two interfaces ofthe second tee solenoid valve are connected with the pipeline of the air intake end of the second compressor, and the third interfaces of the two tee solenoid valves are respectively connected with the intercooler; and the other interface of the intercooler is connected with the liquid storage device in the refrigeration cycle system through a capillary tube. The utility model has the advantagesthat: the system not only can be used as a single-stage refrigeration system when the high evaporation temperature is needed, but also can be used as a two-stage refrigeration system when needed, thereby improving the refrigeration efficiency and having better energy-saving effect.
Description
Technical field
The utility model relates to refrigeration technology field, relates in particular to carry out single, double level switching according to load and demand, realizes the cooling cycle system of different evaporating temperatures, and this system is used for food processing, storage, fresh-keeping etc.
Background technology
The refrigeration system of in the food processing storing field, using, because the needs of using, sometimes need to give different functions of use according to changes of seasons, for example use as the sharp freezing storehouse of meat in spring and summer, need system that evaporating temperature below-40 ℃ is provided, and use in the vegetables and fruits refrigeration processing storehouse of being used as vegetables season of gathering, at this time need system that evaporating temperature more than-10 ℃ is provided.Even with a kind of refrigeration character, the cryogenic temperature that the food of different cultivars needs is also inequality.And, quick freezing for needs, also have very large difference with a kind of food in cold and the temperature of freezing to begin and finish whole process need.For adapting to the needs of above-mentioned situation, two kinds of technical schemes are arranged in the prior art, scheme one is: the refrigeration system of configuration two cover different temperatures is moved respectively.The less than one of scheme one is that the whole year operation rate of every cover system is very low, the 2nd, and output investment ratio is bigger.Scheme two is to adopt jumbo main frame, realizes different evaporating temperatures by different throttling arrangements.The deficiency of scheme two is to carry out throttling to the return-air of high evaporation temperature, causes unnecessary restriction loss, and the entire system combination property is descended.
Summary of the invention
The purpose of this utility model provides a kind of freezing and refrigeration refrigeration system, realize the switching of different evaporating temperatures with a system, this system can be used as the single-stage refrigeration system when needs high evaporation temperature, also can be switching to Two-stage refrigerating system by pipeline when needed and use, satisfy the needs of the low evaporating temperature of freezing needs.
The technical solution of the utility model is: a kind of Duel-temperature refrigeration cycle system, comprise compressor, condenser, evaporimeter, reservoir, oil eliminator, liquid pipe magnetic valve, gas-liquid separator and expansion valve, described oil eliminator, condenser, reservoir, liquid pipe magnetic valve, expansion valve, evaporimeter and gas-liquid separator are connected in turn between the exhaust steam end and suction end of compressor by pipeline, its its structure is, described Duel-temperature refrigeration cycle system comprises two compressors, be connected with intercooler by two controlled three-way magnetic valves between two compressors, carry out the switching of single-stage or twin-stage operation, described two controlled three-way magnetic valves, two interfaces of the 1st controlled three-way magnetic valve are bound up on the pipeline of exhaust steam end of the 1st compressor, two interfaces of the 2nd controlled three-way magnetic valve are bound up on the pipeline of suction end of the 2nd compressor, the 3rd interface of two controlled three-way magnetic valves is connected with intercooler respectively, intercooler also has an interface to be connected with reservoir in the cooling cycle system by restricting element, and the exhaust end of the 2nd compressor is connected with the pipeline of condenser inlet end behind oil eliminator.
A kind of Duel-temperature refrigeration cycle system system described in the utility model, its structure are that described compressor is a kind of in reciprocating compressor or the rotary compressor.
A kind of Duel-temperature refrigeration cycle system described in the utility model, its structure are that described compressor is a kind of in constant volume compressor or the variable conpacitance compressor.
A kind of Duel-temperature refrigeration cycle system described in the utility model, its structure be described at the 1st compressor exhaust steam end and the controlled three-way magnetic valve of the suction end of the 2nd compressor, carry out the switching of three-way magnetic valve path according to predefined temperature or pressure by controller.
A kind of Duel-temperature refrigeration cycle system described in the utility model, its structure are that described intercooler 9 is a kind of of flash tank form or plate type heat exchanger form.
A kind of Duel-temperature refrigeration cycle system described in the utility model, its structure are that restricting element that the outlet of described reservoir is connected with intercooler is a kind of in the temperature-sensing valve of capillary, heating power expansion valve, electric expansion valve or hydrojet.
A kind of Duel-temperature refrigeration cycle system described in the utility model, its structure are that described condenser (3) is the condenser of band energy adjustment function.
Principle of the present utility model is the switching by controlled three-way magnetic valve, realizes the parallel connection use or the twin-stage compression cycle of compressor.
When needs high evaporation temperature was moved, system carried out the single-stage circulation.At this moment the 1st three-way magnetic valve is communicated with exhaust line, the 2nd three-way magnetic valve 22 connected suction line, the exhaust of No. 1 compressor and No. 2 compressors enters condenser through oil eliminator respectively, the highly pressurised liquid that comes out from condenser enters reservoir, then through entering evaporimeter behind liquid pipe magnetic valve, the expansion valve, the low-pressure gas that comes out from evaporimeter is got back to the air-breathing pipe end of compressor 1, compressor 2 respectively via gas-liquid separator, finishes a single-stage kind of refrigeration cycle.Under this single-stage kind of refrigeration cycle state, operation is not participated in the intercooler loop.
When the low evaporating temperature of needs was moved, system carried out the twin-stage circulation.At this moment the 1st three-way magnetic valve connected the exhaust end and the intercooler of No. 1 compressor, and the 2nd three-way magnetic valve connected the suction end and the intercooler of No. 2 compressors.The exhaust of No. 1 compressor enters in the intercooler through behind the oil eliminator, the exhaust of No. 2 compressors enters condenser through behind the oil eliminator, the highly pressurised liquid that condenser comes out enters reservoir, the liquid that reservoir comes out is divided into two-way, one the tunnel through entering evaporimeter behind liquid pipe magnetic valve, the expansion valve, gets back to compressor from the low-pressure gas that evaporimeter comes out No. 1 via gas-liquid separator; Enter intercooler after the throttling of another road through restricting element (capillary), get back to the suction end of No. 2 compressors after the exhaust of cold-producing medium after the throttling and No. 1 compressor mixes in intercooler, finish the twin-stage compression refrigeration circulation of cooling off fully in the middle of the one-level throttling.Perhaps enter intercooler 9 after the throttling of liquid that reservoir comes out through restricting element (capillary), come out afterwards with after the exhaust of No. 1 compressor mixes to enter the air-breathing of No. 2 compressors from middle cooler 9, finish the twin-stage compression refrigeration circulation of not exclusively cooling off in the middle of the one-level throttling, as shown in Figure 4.Under this two-stage refrigeration recurrent state, operation is participated in the intercooler loop.
The utlity model has significant advantage,
1, can make refrigeration and freezingly all keep high efficiency isolated operation respectively.Duty ratio is bigger when the high evaporation temperature is moved, and at this time two compressors move simultaneously and guarantee that big cold output is to satisfy the demands; And when the operation of low evaporating temperature, general single stage compress system is difficult to realize low evaporating temperature, and efficient is all very low, and at this time system switches to the twin-stage compressed format and improved refrigerating efficiency and reach purpose of energy saving.
2, carry out the twin-stage circulation time, the exhaust of compressor 1 can be connected with intercooler, also can be directly connected to the air intake duct of compressor 2, forms the middle not exclusively cool cycles of one-level throttling.
3, the outlet in compressor 1 and 2 is provided with oil eliminator, can prevent the twin-stage circulation time, and the lubricating oil of compressor 1 enters in the compressor 2.
4, carry out the twin-stage circulation time, it is cold to improve refrigeration to utilize charge air cooler to carry out for major loop liquid.
Description of drawings
The utility model has accompanying drawing 4 width of cloth, wherein
Fig. 1 is the utility model basic principle figure;
Circulation theory figure when Fig. 2 is the operation of high evaporation temperature single-stage;
The twin-stage compression refrigeration circulation theory figure that cools off fully in the middle of the one-level throttling when Fig. 3 is the twin-stage operation;
The twin-stage compression refrigeration circulation theory figure that not exclusively cools off in the middle of the one-level throttling when Fig. 4 is the twin-stage operation.
In the accompanying drawing: 1, No. 1 compressor, 2, No. 2 compressors, 3, condenser, 4, reservoir, 5, liquid pipe magnetic valve, 6, expansion valve, 7, evaporimeter, 8, gas-liquid separator, 9, intercooler, 10, restricting element, 11, No. 1 compressor oil eliminator, 12, No. 1 three-way magnetic valve, 21, No. 2 compressor oil eliminators, 22, No. 2 three-way magnetic valves.
The specific embodiment
The utility model will be further described below in conjunction with accompanying drawing.
Fig. 1～Fig. 3 has provided embodiment 1.Oil eliminator 11, condenser 3, reservoir 4, liquid pipe magnetic valve 5, expansion valve 6, evaporimeter 7 and gas-liquid separator 8 are connected in turn between the exhaust end and suction end of No. 1 compressor 1 by pipeline, No. 1 and No. 2 two compressors 1, pass through two controlled three-way magnetic valves 12 between 2,22 are connected with intercooler 9, two controlled three-way magnetic valves 12,22, two interfaces of the 1st controlled three-way magnetic valve 12 are bound up on the pipeline of exhaust steam end of the 1st compressor 1, two interfaces of the 2nd controlled three-way magnetic valve 22 are bound up on the pipeline of suction end of the 2nd compressor 2, two controlled three-way magnetic valves 12,22 the 3rd interface is connected with intercooler 9 respectively, intercooler 9 also has an interface to be connected with reservoir 4 in the cooling cycle system by throttle capillary tube 10, and the exhaust end of the 2nd compressor 2 is connected with the pipeline of condenser 3 entrance points behind oil eliminator 21.The running of present embodiment is:
When needs high evaporation temperature was moved, system carried out the single-stage circulation, as shown in Figure 2.Three-way magnetic valve 12,22 is under controller control, the d of No. 1 three-way magnetic valve 12, e connect, the a of No. 2 three-way magnetic valves 22, b connect, the exhaust of No. 1 compressor and No. 2 compressors enters condenser 3 through oil eliminator 11,21 respectively, the highly pressurised liquid that comes out from condenser enters reservoir 4, then through entering evaporimeter 7 behind liquid pipe magnetic valve 5, the expansion valve 6, the low-pressure gas that comes out from evaporimeter is got back to the air-breathing pipe end of compressor 1, compressor 2 respectively via gas-liquid separator 8, finishes a single-stage kind of refrigeration cycle.
Carry out the twin-stage circulation time when the low evaporating temperature of needs, three-way magnetic valve 12,22 is under controller control, and the d of No. 1 three-way magnetic valve 12, f connect, and the b of No. 2 three-way magnetic valves 22, c connect.As shown in Figure 3.The exhaust of No. 1 compressor enters in the intercooler 9 through behind the oil eliminator 11, the exhaust of No. 2 compressors enters condenser 3 through behind the oil eliminator 21, the highly pressurised liquid that condenser comes out enters reservoir 4, the liquid that reservoir comes out is divided into two-way, one the tunnel through entering evaporimeter 7 behind liquid pipe magnetic valve 5, the expansion valve 6, gets back to compressor 1 from the low-pressure gas that evaporimeter comes out via gas-liquid separator 8; Another road enters intercooler 9 through after the throttling of capillary 10, the exhaust of cold-producing medium after the throttling and No. 1 compressor is got back to the air-breathing of No. 2 compressors after mixing in intercooler 9, finish the twin-stage compression refrigeration circulation of cooling off fully in the middle of the one-level throttling.
That Fig. 4 provides is embodiment 2.Be the embodiment that not exclusively cools off the twin-stage circulation in the middle of the one-level throttling.Among this embodiment, the c of the f of No. 1 three-way magnetic valve 12 and No. 2 three-way magnetic valves 22 directly connects, under this state, the exhaust of compressor 1 does not directly enter intercooler 9, but directly the exhaust of compressor 1 is connected to the air intake duct of compressor 2 by two triple valves, form in the middle of the one-level throttling not exclusively cool cycles.As shown in Figure 4, the exhaust of compressor 1 is directly connected to the air intake duct of compressor 2 by two triple valves, the exhaust of No. 2 compressors enters condenser 3 through behind the oil eliminator 21, the highly pressurised liquid that condenser comes out enters reservoir 4, the liquid that reservoir comes out is divided into two-way, enters intercooler 9 after one tunnel process throttling of capillary 10.Another road enters cold-producing medium after intercooler and the throttling and carries out heat exchange and make liquid cold excessively, the liquid of crossing after cold comes out to get back to compressor 1 from the low-pressure gas that evaporimeter comes out via gas-liquid separator 8 through entering evaporimeter 7 behind liquid pipe magnetic valve 5, the expansion valve 6 from charge air cooler; The refrigerant gas that evaporation produces after the throttling in the charge air cooler 9 is then got back to the air-breathing of No. 2 compressors, finishes the twin-stage compression refrigeration circulation of not exclusively cooling off in the middle of the one-level throttling.
Claims (7)
1, a kind of Duel-temperature refrigeration cycle system, comprise compressor (1), condenser (3), evaporimeter (7), reservoir (4), oil eliminator (11), liquid pipe magnetic valve (5), gas-liquid separator (8) and expansion valve (6), described oil eliminator (11,), condenser (3), reservoir (4), liquid pipe magnetic valve (5), expansion valve (6), evaporimeter (7) and gas-liquid separator (8) are connected in turn between the exhaust end and suction end of compressor (1) by pipeline, it is characterized in that, described Duel-temperature refrigeration cycle system comprises two compressors (1,2), pass through two controlled three-way magnetic valves (12 between two compressors, 22) be connected with intercooler (9), carry out the switching of single-stage or twin-stage operation, described two controlled three-way magnetic valves (12,22), two interfaces of the 1st controlled three-way magnetic valve (12) are bound up on the pipeline of exhaust steam end of the 1st compressor (1), two interfaces of the 2nd controlled three-way magnetic valve (22) are bound up on the pipeline of suction end of the 2nd compressor (2), two controlled three-way magnetic valves (12,22) the 3rd interface is connected with intercooler (9) respectively, intercooler (9) also has an interface to be connected with reservoir (4) in the cooling cycle system by restricting element (10), and the exhaust end of the 2nd compressor (2) is connected with the pipeline of condenser (3) entrance point behind oil eliminator (21).
2, a kind of Duel-temperature refrigeration cycle system system according to claim 1 is characterized in that described compressor (1,2) is a kind of in reciprocating compressor or the rotary compressor.
3, a kind of Duel-temperature refrigeration cycle system according to claim 2 is characterized in that described compressor (1,2) is a kind of in constant volume compressor or the variable conpacitance compressor.
4, a kind of Duel-temperature refrigeration cycle system according to claim 1, it is characterized in that described at the 1st compressor (1) exhaust steam end and the three-way magnetic valve (12,22) of the suction end of the 2nd compressor (2), by controller according to predefined temperature or/and pressure carries out the switching of three-way magnetic valve path.
5, a kind of Duel-temperature refrigeration cycle system according to claim 1 is characterized in that described intercooler (9) is a kind of of flash tank form or plate type heat exchanger form.
6, a kind of Duel-temperature refrigeration cycle system according to claim 1 is characterized in that restricting element (10) that described reservoir (4) outlet is connected with intercooler (9) is a kind of in the temperature-sensing valve of capillary, heating power expansion valve, electric expansion valve or hydrojet.
7, a kind of Duel-temperature refrigeration cycle system according to claim 1 is characterized in that described condenser (3) is the condenser of band energy adjustment facility.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2009200140730U CN201407856Y (en) | 2009-05-27 | 2009-05-27 | Dual temperature refrigeration cycle system |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2009200140730U CN201407856Y (en) | 2009-05-27 | 2009-05-27 | Dual temperature refrigeration cycle system |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN201407856Y true CN201407856Y (en) | 2010-02-17 |
Family
ID=41678791
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2009200140730U Expired - Lifetime CN201407856Y (en) | 2009-05-27 | 2009-05-27 | Dual temperature refrigeration cycle system |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN201407856Y (en) |
Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101576327B (en) * | 2009-05-27 | 2011-04-06 | 大连三洋压缩机有限公司 | Duel-temperature refrigeration cycle system |
| CN102927713A (en) * | 2012-11-12 | 2013-02-13 | 天津商业大学 | Double-stage multi-concatenate secondary throttling refrigerating system with middle cooling completely |
| CN103105014A (en) * | 2011-11-10 | 2013-05-15 | 株式会社前川制作所 | Refrigeration system for use in ship |
| CN103335441A (en) * | 2013-07-04 | 2013-10-02 | 天津商业大学 | Secondary throttling middle incomplete cooling variable flow double-stage compression refrigeration system |
| CN103335440A (en) * | 2013-07-04 | 2013-10-02 | 天津商业大学 | Secondary throttling middle complete cooling double-working-condition refrigeration system |
| CN105444446A (en) * | 2014-08-27 | 2016-03-30 | 艾默生网络能源有限公司 | System, method and devices for refrigeration control of computer room |
| CN108253655A (en) * | 2018-03-21 | 2018-07-06 | 天津商业大学 | Variable-flow single stage compress cycle and the heat pump system of two-stage compression cycle can be achieved |
| CN111316046A (en) * | 2017-10-30 | 2020-06-19 | 伸和控制工业股份有限公司 | Liquid temperature control device and temperature control method using same |
-
2009
- 2009-05-27 CN CN2009200140730U patent/CN201407856Y/en not_active Expired - Lifetime
Cited By (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101576327B (en) * | 2009-05-27 | 2011-04-06 | 大连三洋压缩机有限公司 | Duel-temperature refrigeration cycle system |
| CN103105014A (en) * | 2011-11-10 | 2013-05-15 | 株式会社前川制作所 | Refrigeration system for use in ship |
| CN103105014B (en) * | 2011-11-10 | 2016-08-17 | 株式会社前川制作所 | Refrigeration system for use in ship |
| CN102927713A (en) * | 2012-11-12 | 2013-02-13 | 天津商业大学 | Double-stage multi-concatenate secondary throttling refrigerating system with middle cooling completely |
| CN103335441A (en) * | 2013-07-04 | 2013-10-02 | 天津商业大学 | Secondary throttling middle incomplete cooling variable flow double-stage compression refrigeration system |
| CN103335440A (en) * | 2013-07-04 | 2013-10-02 | 天津商业大学 | Secondary throttling middle complete cooling double-working-condition refrigeration system |
| CN105444446A (en) * | 2014-08-27 | 2016-03-30 | 艾默生网络能源有限公司 | System, method and devices for refrigeration control of computer room |
| CN105444446B (en) * | 2014-08-27 | 2017-12-19 | 维谛技术有限公司 | A kind of refrigeration control system of computer room, method and device |
| CN111316046A (en) * | 2017-10-30 | 2020-06-19 | 伸和控制工业股份有限公司 | Liquid temperature control device and temperature control method using same |
| CN111316046B (en) * | 2017-10-30 | 2021-12-07 | 伸和控制工业股份有限公司 | Liquid temperature control device and temperature control method using same |
| CN108253655A (en) * | 2018-03-21 | 2018-07-06 | 天津商业大学 | Variable-flow single stage compress cycle and the heat pump system of two-stage compression cycle can be achieved |
| CN108253655B (en) * | 2018-03-21 | 2024-03-01 | 天津商业大学 | Heat pump system capable of realizing variable flow single-stage compression cycle and double-stage compression cycle |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN101576327B (en) | Duel-temperature refrigeration cycle system | |
| CN201407856Y (en) | Dual temperature refrigeration cycle system | |
| CN202757337U (en) | Screw type refrigeration compressor unit for economizer | |
| CN103363717A (en) | Refrigerating system and operation method thereof | |
| CN101691960A (en) | Three-pipe heating and reclaiming air-conditioning system | |
| CN102042721A (en) | Synergy type steam compression heat pump circulating system of ejector | |
| CN105423656A (en) | Refrigeration system and control method thereof | |
| CN101482321B (en) | Ultra-low temperature heat pump water heater | |
| CN101493269B (en) | Low temperature heat pump air conditioning system | |
| CN202813592U (en) | air conditioner | |
| CN110701819B (en) | Three-working-condition system | |
| CN106871474A (en) | Air-cooled water-cooled combined air-conditioning system | |
| CN102494375A (en) | Ultrahigh and low-temperature refrigerating, heating and water heating three-purpose air-conditioning system | |
| CN200993450Y (en) | Variable refrigerant flow intelligent ice-storage air conditioning system | |
| CN101487643A (en) | Ultra-low temperature heat pump air conditioning system | |
| CN210425610U (en) | Refrigeration system | |
| CN101782292B (en) | Three-purpose air conditioner system of ultra low temperature refrigeration, heating and hot water | |
| CN109520163B (en) | Wide-temperature-zone small-sized refrigerating and refrigerating unit with rapid pulse defrosting function | |
| CN208222889U (en) | The refrigeration system of variable-flow single stage compress circulation and two-stage compression cycle can be achieved | |
| CN202303718U (en) | Ice storage system of ice storage multi-connected air-conditioning unit | |
| CN202221182U (en) | Steam injection device and refrigerating system with same | |
| CN201159556Y (en) | Low-temperature hot pump air conditioning system | |
| CN105202609B (en) | A kind of heating heat pump system increasing worker quality liquid degree of supercooling using air natural cooling source | |
| CN202149639U (en) | Pressure-adjusting regenerative refrigeration compression condensing unit adopting R404A refrigerant | |
| CN101799224B (en) | Low-temperature cooling, heating and water heating tri-purpose air-conditioning system |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| AV01 | Patent right actively abandoned |
Granted publication date: 20100217 Effective date of abandoning: 20090527 |