CN101576327A - Duel-temperature refrigeration cycle system - Google Patents
Duel-temperature refrigeration cycle system Download PDFInfo
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- CN101576327A CN101576327A CNA2009100117936A CN200910011793A CN101576327A CN 101576327 A CN101576327 A CN 101576327A CN A2009100117936 A CNA2009100117936 A CN A2009100117936A CN 200910011793 A CN200910011793 A CN 200910011793A CN 101576327 A CN101576327 A CN 101576327A
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Abstract
The invention relates to a duel-temperature refrigeration cycle system, which comprises compressors, a condenser, an evaporator, a liquid storing device, an oil separator, a liquid tube electromagnetic valve, a gas-liquid separator and an expansion valve. The system comprises two compressors which perform a single-stage or double-stage running switch through two three-way electromagnetic valves and an intermediate cooler, wherein two interfaces of the first one of the two three-way electromagnetic valves are connected with a pipeline at an exhaust steam end of the first compressor, two interfaces of the second three-way electromagnetic valve are connected with a pipeline at a suction end of the second compressor, the third interfaces of the two three-way electromagnetic valves are connected with the intermediate cooler respectively, and the intermediate cooler has another interface which is connected with the liquid storing device in the refrigeration cycle system through a capillary. The duel-temperature refrigeration cycle system has the advantages that one system not only can be used as a single-stage refrigeration system when a high evaporating temperature is needed, but also can be used as a double-stage refrigeration system as required, thus the duel-temperature refrigeration cycle system improves the refrigeration efficiency and has good energy-saving effect.
Description
Technical field
The present invention relates to refrigeration technology field, relate in particular to and can carry out single, double level switching according to load and demand, realize the cooling cycle system of different evaporating temperatures, 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 invention is to provide 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.
Technical scheme of the present invention 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 of the present invention, 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 of the present invention, 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 of the present invention, 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 of the present invention, 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 of the present invention, 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 of the present invention, its structure are that described condenser (3) is the condenser of band energy adjustment facility.
Principle of the present invention 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 present invention 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 present invention has accompanying drawing 4 width of cloth, wherein
Fig. 1 is basic principle figure of the present invention;
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 invention will be further described below in conjunction with accompanying drawing.
Fig. 1 and Fig. 2 have 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, enter intercooler 9 after one tunnel process throttling of capillary 10, another road enters cold-producing medium after intercooler 9 and the throttling and carries out heat exchange and make liquid cold excessively, the liquid of crossing after cold comes out through liquid pipe magnetic valve 5 from charge air cooler, enter evaporimeter 7 behind the expansion valve 6, get back to compressor 1 via gas-liquid separator 8 from the low-pressure gas that evaporimeter comes out; The refrigerant gas that evaporation produces after the throttling in the intercooler 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.
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| CN2009100117936A CN101576327B (en) | 2009-05-27 | 2009-05-27 | Duel-temperature refrigeration cycle system |
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| CN2009100117936A CN101576327B (en) | 2009-05-27 | 2009-05-27 | Duel-temperature refrigeration cycle system |
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| CN101576327B CN101576327B (en) | 2011-04-06 |
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| CN102251965A (en) * | 2010-05-19 | 2011-11-23 | 珠海格力节能环保制冷技术研究中心有限公司 | Compressor capable of performing one-stage and double-stage switching, and control method thereof |
| 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 |
| CN104567063A (en) * | 2014-12-31 | 2015-04-29 | 江苏兆胜空调有限公司 | Marine mixed variable frequency low-temperature quick freezing device |
| CN105509358A (en) * | 2015-12-21 | 2016-04-20 | 重庆美的通用制冷设备有限公司 | Refrigeration unit |
| CN108954909A (en) * | 2018-09-19 | 2018-12-07 | 珠海格力电器股份有限公司 | A kind of heat pump system and its oily cooling cycle control method |
| CN110470067A (en) * | 2018-05-11 | 2019-11-19 | 松下冷链（大连）有限公司 | A kind of carbon dioxide refrigerant two-stage pressurization convertible device in parallel with single-stage |
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| CN113503653A (en) * | 2021-08-04 | 2021-10-15 | 珠海格力电器股份有限公司 | Multi-compressor refrigeration system and air conditioner |
| CN113983712A (en) * | 2021-10-22 | 2022-01-28 | 珠海格力节能环保制冷技术研究中心有限公司 | Unit operation control method and device, two-stage unit and refrigeration equipment |
| WO2022116133A1 (en) * | 2020-12-03 | 2022-06-09 | 苏州电器科学研究院股份有限公司 | Wide-range low-temperature refrigeration system for test chamber |
| CN114777352A (en) * | 2022-03-23 | 2022-07-22 | 浙江中广电器集团股份有限公司 | Fluorine cooling variable frequency drive control module unit and control method thereof |
| CN114992895A (en) * | 2022-06-21 | 2022-09-02 | 珠海万纬物流发展有限公司 | One-stage throttling intermediate complete cooling two-stage compression low-temperature refrigeration system |
| CN115060018A (en) * | 2022-06-21 | 2022-09-16 | 珠海万纬物流发展有限公司 | Two-stage throttling intermediate complete cooling two-stage compression carbon dioxide cold carrying system |
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| CN201407856Y (en) * | 2009-05-27 | 2010-02-17 | 大连三洋压缩机有限公司 | Dual temperature refrigeration cycle system |
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- 2009-05-27 CN CN2009100117936A patent/CN101576327B/en active Active
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| CN102251965B (en) * | 2010-05-19 | 2013-08-28 | 珠海格力节能环保制冷技术研究中心有限公司 | Compressor capable of performing one-stage and double-stage switching, and control method thereof |
| CN102251965A (en) * | 2010-05-19 | 2011-11-23 | 珠海格力节能环保制冷技术研究中心有限公司 | Compressor capable of performing one-stage and double-stage switching, and control method thereof |
| 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 |
| CN104567063A (en) * | 2014-12-31 | 2015-04-29 | 江苏兆胜空调有限公司 | Marine mixed variable frequency low-temperature quick freezing device |
| CN105509358A (en) * | 2015-12-21 | 2016-04-20 | 重庆美的通用制冷设备有限公司 | Refrigeration unit |
| CN105509358B (en) * | 2015-12-21 | 2018-05-01 | 重庆美的通用制冷设备有限公司 | Refrigeration unit |
| CN110470067A (en) * | 2018-05-11 | 2019-11-19 | 松下冷链（大连）有限公司 | A kind of carbon dioxide refrigerant two-stage pressurization convertible device in parallel with single-stage |
| CN108954909A (en) * | 2018-09-19 | 2018-12-07 | 珠海格力电器股份有限公司 | A kind of heat pump system and its oily cooling cycle control method |
| WO2021057137A1 (en) * | 2019-09-23 | 2021-04-01 | 珠海格力电器股份有限公司 | Refrigeration system and refrigerated storage |
| WO2022116133A1 (en) * | 2020-12-03 | 2022-06-09 | 苏州电器科学研究院股份有限公司 | Wide-range low-temperature refrigeration system for test chamber |
| CN113503653A (en) * | 2021-08-04 | 2021-10-15 | 珠海格力电器股份有限公司 | Multi-compressor refrigeration system and air conditioner |
| CN113983712A (en) * | 2021-10-22 | 2022-01-28 | 珠海格力节能环保制冷技术研究中心有限公司 | Unit operation control method and device, two-stage unit and refrigeration equipment |
| CN114777352A (en) * | 2022-03-23 | 2022-07-22 | 浙江中广电器集团股份有限公司 | Fluorine cooling variable frequency drive control module unit and control method thereof |
| CN114992895A (en) * | 2022-06-21 | 2022-09-02 | 珠海万纬物流发展有限公司 | One-stage throttling intermediate complete cooling two-stage compression low-temperature refrigeration system |
| CN115060018A (en) * | 2022-06-21 | 2022-09-16 | 珠海万纬物流发展有限公司 | Two-stage throttling intermediate complete cooling two-stage compression carbon dioxide cold carrying system |
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