CN204963276U - Single compressor second grade developments refrigeration cold -storage air conditioning system - Google Patents
Single compressor second grade developments refrigeration cold -storage air conditioning system Download PDFInfo
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- CN204963276U CN204963276U CN201520735741.4U CN201520735741U CN204963276U CN 204963276 U CN204963276 U CN 204963276U CN 201520735741 U CN201520735741 U CN 201520735741U CN 204963276 U CN204963276 U CN 204963276U
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Abstract
The utility model discloses a single compressor second grade developments refrigeration cold -storage air conditioning system. The utility model discloses a blast pipe of compressor loops through vapour and liquid separator I, condensers, reservoir and I intercommunication of solenoid valve, still include one -level refrigerating plant, two -stage system ice device, trade cold cooling air conditioner device, one -level refrigerating plant's evaporimeter submergence is in heat exchanger, the export and the evaporimeter of solenoid valve I, the cold -storage bucket is established ties or parallelly connected back and vapour and liquid separator's II entry communicates, heat exchanger's export loops through water pump I and the entry intercommunication of solenoid valve II with cold -storage bucket upper portion, the export of cold -storage bucket lower part and heat exchanger's entry intercommunication, the liquid outlet and the income liquid mouth of cold -storage bucket communicate with the export with the entry that trades cold cooling air conditioner device respectively. The utility model has the characteristics of refrigeration efficiency is high, equipment once drops into and the running cost is low, the reliability is high.
Description
Technical field
The utility model belongs to refrigeration technology field, is specifically related to the single compressor the two-stage dynamic refrigeration and cold accumulation air-conditioning system that a kind of refrigerating efficiency is high, equipment once drops into and operating cost is low, reliability is high.
Background technology
Along with the development of modern industry and the raising of living standards of the people, modern air conditioning equipment become people produce with life in the urgent need to, the application of central air-conditioning is more and more extensive, its power consumption is also increasing, some big and medium-sized cities central air-conditioning power consumptions have accounted for more than 20% of its Peak power use amount, and the ratio of air conditioning energy consumption in national economy always consumes energy is up to 30%.Power system peak load difference strengthens, and load rate of grid declines, and electrical network carries out power cuts to limit consumption, seriously governs industrial and agricultural production, reduces people's quality of life.
For above problem, Double-working-condition refrigerating ice Cool Storage Technology of the prior art, ice-chilling air conditioning system utilizes night dip electric power to carry out cold storage of ice making, at power surges period cool thermal discharge in the daytime, can peak load shifting, balancing power network load, reduces the construction cost in peak clipping power station and the pollution reduced environment, has good economic benefit and social benefit.But the function of the double duty chiller unit of prior art is split, carried out various combination by conventional refrigerant unit and ice making unit two groups of refrigeration unit and realized.Under ice making operating mode, carry out chilled water the supply system ice maker group that ice making-conventional refrigerant unit produces to make its cooling water by two groups of refrigeration unit associated working, ice making unit is then with the refrigerating medium ice making that conventional refrigerant unit is produced for cold source device; And the compression ratio often organizing refrigeration unit is all much smaller than existing double duty chiller unit.Due to two groups of units, not only cost is high, and complete independent operating between unit, can not Coordination Treatment two different loads mutually, and two units are also difficult to realize integrated ground control and management.For function segmentation and unmanageable problem, in prior art, also there is the structure proposing unit realization group jointly refrigeration and ice making.But, existing double duty chiller unit adopts after refrigeration machine and Ice Storage Tank serial or parallel connection to indoor apparatus of air conditioner cooling, refrigeration working medium passes through the evaporimeter indirect heat exchange ice making in Ice Storage Tank after refrigeration machine, and part adopts refrigeration working medium directly for indoor apparatus of air conditioner refrigeration, not only heat exchange efficiency is low, and refrigeration working medium consumption is more, cost is higher, also easily causes refrigeration working medium to the corrosion of air-conditioning duct.In addition, when running under ice making operating mode, its refrigeration working medium outlet temperature reduces by 12 ~ 22 DEG C than the chilled water leaving water temperature of conventional refrigerant unit, and its evaporating temperature is corresponding reduction by 12 ~ 22 DEG C also.So that no matter in which way discharges heat, when condensation temperature is identical, large all more than conventional refrigerant unit of the compression ratio of the compressor of double duty chiller unit, Energy Efficiency Ratio is lower.And the double duty chiller unit of the high energy efficiency ratio that freezes, can reach under ice making two kinds of operating modes, not only technical requirement is high, and technological requirement is high, and cost intensive.Secondly, due to double duty chiller unit need to carry out freezing, the alternate run of ice making two kinds of operating modes, even need to carry out to freeze, run while ice making two kinds of operating modes, often kind of operating mode has different cooling temperatures and the requirement of semen donors, makes refrigeration unit be difficult to reach to run under all operating modes and all keep higher operational efficiency and operation stability.For reducing cost of investment, improve refrigerating efficiency, Chinese patent " a kind of dynamic ice cold-storage method and equipment " Authorization Notice No. CN100538221C, improve traditional ice technology, research and development have manufactured equipment, this equipment refrigeration manufactures ice in process and adopts refrigeration working medium direct evaporation endothermic ice making in water, and system COP is 4, reaches common air-conditioning level, system adopts water as refrigerating medium, reduce system investments maintenance cost, adopt refrigeration working medium ice making of the direct expansion to reduce ice storage tank volume, reduce manufacturing cost.But this equipment cannot independent operating, cold that common air-conditioning system produces must be depended on and serve as condenser cooling refrigeration working medium in equipment ice-making process.
Utility model content
The purpose of this utility model is to provide the single compressor the two-stage dynamic refrigeration and cold accumulation air-conditioning system that a kind of refrigerating efficiency is high, equipment once drops into and operating cost is low, reliability is high.
The purpose of this utility model is achieved in that and comprises compressor, gas-liquid separator I, condenser, reservoir, magnetic valve I, gas-liquid separator II, the blast pipe of described compressor is successively by gas-liquid separator I, condenser, reservoir is communicated with magnetic valve I, also comprise one-level refrigerating plant, two-stage system ice production apparatus, change cold cooling aircondition, the evaporimeter of described one-level refrigerating plant is immersed in heat exchanger, the outlet of described magnetic valve I and evaporimeter, be communicated with the entrance of gas-liquid separator II after cold accumulation bucket serial or parallel connection, the outlet of described heat exchanger is communicated with the entrance of magnetic valve II with cold accumulation bucket top by water pump I successively, the described outlet of cold accumulation bucket bottom is communicated with the entrance of heat exchanger, the liquid outlet of described cold accumulation bucket and liquid inlet respectively with the entrance and exit connected entrance changing cold cooling aircondition.
The utility model adopts single compressed machine compression refrigeration working medium, refrigeration working medium serial or parallel connection one-level refrigeration and secondary flow pattern realize the two-stage dynamic refrigeration and cold accumulation, one-level refrigeration equally dynamically with common refrigeration unit produces cold water, secondary refrigeration realizes dynamic ice-making for ice making of the direct expansion in the water of refrigeration working medium in cold accumulation bucket, changes cold cooling aircondition swap out cold for room temperature lowering finally by cold water.The utility model adopts the technology of refrigeration working medium directly evaporation in water to improve refrigerating efficiency, change cold cooling aircondition to be freezed by circulating chilled water, not only improve heat exchange efficiency, and reduce the consumption of refrigeration working medium, avoid refrigeration working medium to the corrosion of aircondition pipeline, thus the once investment of the equipment of saving and later stage use, maintenance cost, can effectively solve double duty chiller unit cost performance lower, later maintenance is a difficult problem frequently.Not only adopt serial or parallel connection pattern to realize refrigeration working medium and produce cold water but also ice making, abandon the common refrigeration unit that conventional refrigeration working medium direct-evaporation-type ice-making system must depend on, reduction two cover refrigeration compressor is single compressor, system cost can be reduced further, cold water cooling can also be realized and ice conserve cold two cover system coexists, reach the stable object improving the stability of a system for cold-peace.Therefore, the utility model has the advantages that refrigerating efficiency is high, equipment once drops into and operating cost is low, reliability is high.
Accompanying drawing explanation
Fig. 1 is the cascaded structure schematic diagram of the utility model;
Fig. 2 is the parallel-connection structure schematic diagram of the utility model;
In figure: A-one-level refrigerating plant, B-two-stage system ice production apparatus, C-changes cold cooling aircondition, 1-compressor, 2-gas-liquid separator I, 3-condenser, 4-reservoir, 5-magnetic valve I, 6-choke valve I, 7-evaporimeter, 8-choke valve II, 9-gas-liquid separator II, 10-heat exchanger, 11-water pump I, 12-magnetic valve II, 13-cold accumulation bucket, 14-water pump II, 15-magnetic valve III, 16-check valve, 17-ratio adjusting valve I, 18-indoor apparatus of air conditioner, 19-ratio adjusting valve II, 20-controller, 21-choke valve III.
Detailed description of the invention
Be further described the utility model below in conjunction with drawings and Examples, but limited the utility model never in any form, any change done based on the utility model training centre or improvement, all belong to protection domain of the present utility model.
As illustrated in fig. 1 and 2, single compressor the two-stage dynamic refrigeration and cold accumulation air-conditioning system of the present utility model comprises compressor 1, gas-liquid separator I 2, condenser 3, reservoir 4, magnetic valve I 5, gas-liquid separator II 9, the blast pipe of described compressor 1 is successively by gas-liquid separator I 2, condenser 3, reservoir 4 is communicated with magnetic valve I 5, characterized by further comprising one-level refrigerating plant A, two-stage system ice production apparatus B, change cold cooling aircondition C, the evaporimeter 7 of described one-level refrigerating plant A is immersed in heat exchanger 10, the outlet of described magnetic valve I 5 and evaporimeter 7, be communicated with the entrance of gas-liquid separator II 9 after cold accumulation bucket 13 serial or parallel connection, the outlet of described heat exchanger 10 is communicated with the entrance of magnetic valve II 12 with cold accumulation bucket 13 top by water pump I 11 successively, the outlet of described cold accumulation bucket 13 bottom is communicated with the entrance of heat exchanger 10, the liquid outlet of described cold accumulation bucket 13 is communicated with the entrance and exit changing cold cooling aircondition C respectively with liquid inlet.
Described one-level refrigerating plant A also comprises choke valve I 6, the entrance of described choke valve I 6 and the outlet of magnetic valve I 5, the outlet of described choke valve I 6 is communicated with the entrance of cold accumulation bucket 13 by evaporimeter 7, choke valve II 8 successively, and the outlet of described cold accumulation bucket 13 is communicated with the entrance of gas-liquid separator II 9.
The outlet of described choke valve I 6 is communicated with the entrance on evaporimeter 7 top, the outlet of described evaporimeter 7 bottom is communicated with by the entrance of choke valve II 8 with cold accumulation bucket 13 bottom, the outlet at described cold accumulation bucket 13 top is communicated with the entrance of gas-liquid separator II 9, the outlet on described heat exchanger 10 top is communicated with the entrance of magnetic valve II 12 with cold accumulation bucket 13 top by water pump I 11 successively, and the outlet of described cold accumulation bucket 13 bottom is communicated with the entrance of heat exchanger 10 bottom.
Described one-level refrigerating plant A also comprises choke valve I 6, described magnetic valve I 5 is three-way magnetic valve, one of entrance and magnetic valve I 5 outlet of described choke valve 6, the outlet of described choke valve I 6 is directly communicated with the entrance of gas-liquid separator II 9 by evaporimeter 7, another outlet of described magnetic valve I 5 is communicated with by the entrance of choke valve III 21 with cold accumulation bucket 13, and the outlet of described cold accumulation bucket 13 is communicated with the entrance of gas-liquid separator II 9.
The outlet of described choke valve I 6 is communicated with the entrance on evaporimeter 7 top, the outlet of described evaporimeter 7 bottom is communicated with the entrance of gas-liquid separator II 9, another outlet of described magnetic valve I 5 is communicated with by the entrance of choke valve III 21 with cold accumulation bucket 13 bottom, the outlet on described heat exchanger 10 top is communicated with the entrance of magnetic valve II 12 with cold accumulation bucket 13 top by water pump I 11 successively, and the outlet of described cold accumulation bucket 13 bottom is communicated with the entrance of heat exchanger 10 bottom.
Describedly change cold cooling aircondition C and comprise water pump II 14, magnetic valve III 15, check valve 16, ratio adjusting valve I 17, indoor apparatus of air conditioner 18, ratio adjusting valve II 19, controller 20, the liquid outlet of described cold accumulation bucket 13 is communicated with its liquid inlet with ratio adjusting valve II 19 by water pump II 14, magnetic valve III 15, check valve 16, ratio adjusting valve I 17, indoor apparatus of air conditioner 18 successively, and described controller 20 is electrically connected with compressor 1, magnetic valve I 5, magnetic valve II 12, magnetic valve III 15, water pump I 11 and water pump II 14 respectively.
Described compressor 1 is any one in screw compressor, rotor compressor, helical-lobe compressor, piston compressor.
Described condenser 3 is air-cooled condenser, water-cooled condenser or evaporative condenser.
Described choke valve I 6, choke valve II 8 and/or choke valve III 21 is any one in heating power expansion valve, capillary, hand expansion valve, electric expansion valve.
Refrigeration working medium is compressed into that temperature is 35 ~ 45 DEG C, pressure is the Compressed Gas of 1.2 ~ 1.8MPa by described compressor 1.
Refrigeration working medium is condensed into that temperature is 25 ~ 35 DEG C, pressure is 1.2 ~ 1.8MPa liquid by described condenser 3.
Refrigeration working medium throttling is become that temperature is 3 ~ 7 DEG C, pressure is the refrigerant of 0.4 ~ 0.6MPa by described choke valve I 6.
The refrigeration working medium absorption refrigeration of inflow becomes temperature to be 8 ~ 12 DEG C by described evaporimeter 7, and pressure is the gas of 0.6 ~ 0.8MPa.
Described choke valve III 21 becomes the liquid of 0 ~ 1 DEG C through refrigeration working medium throttling.
utility model works principle and the course of work:
The utility model adopts single compressed machine compression refrigeration working medium, refrigeration working medium serial or parallel connection one-level refrigeration and secondary flow pattern realize the two-stage dynamic refrigeration and cold accumulation, one-level refrigeration equally dynamically with common refrigeration unit produces cold water, secondary refrigeration realizes dynamic ice-making for ice making of the direct expansion in the water of refrigeration working medium in cold accumulation bucket, changes cold cooling aircondition swap out cold for room temperature lowering finally by cold water.Refrigeration working medium series flow pattern is adopted to be conducive to simplifying the control of refrigeration and ice making; Particularly magnetic valve I is set to three-way solenoid valve, refrigeration working medium is with one-level refrigeration and secondary ice making parallel flow pattern, the independent Effec-tive Function producing cold water and ice-making process can be realized further, realize producing separately cold water, separately ice making, first produce cold water after ice making and produce cold water and four kinds of mode of operations are carried out in ice making simultaneously, and magnetic valve I can also regulate the flow velocity of refrigeration working medium according to cooling needs, realize refrigeration and cooling optimum Match.The utility model adopts the direct evaporation technique of refrigeration working medium to improve refrigerating efficiency, change cold cooling aircondition to be freezed by circulating chilled water, not only reduce the consumption of refrigeration working medium, and avoid the corrosion of refrigeration working medium to aircondition pipeline, thus saved the once investment of equipment and the later stage uses, maintenance cost, can effectively solve double duty chiller unit cost performance lower, later maintenance is a difficult problem frequently.Not only adopt serial or parallel connection pattern to realize refrigeration working medium and produce cold water but also ice making, abandon the common refrigeration unit that conventional refrigeration working medium direct-evaporation-type ice-making system must depend on, reduction two cover refrigeration compressor is single compressor, system cost can be reduced further, cold water cooling can also be realized and ice conserve cold two cover system coexists, reach the stable object improving the stability of a system for cold-peace.Therefore, the utility model has the advantages that refrigerating efficiency is high, equipment once drops into and operating cost is low, reliability is high.
As shown in Figure 1, the cascade refrigeration course of work of the present utility model is as follows:
The refrigeration working medium that gas-liquid separator II 9 is sent into is compressed into that temperature is 40 DEG C, pressure is the Compressed Gas of 1.5MPa by compressor 1, is condensed into that temperature is 30 DEG C, pressure is that 1.5MPa liquid is flowed into reservoir 4 and controlled by magnetic valve I 5 and store after gas-liquid separator I 2, condenser 3;
According to refrigeration demand electromagnetic valve for adjusting I 5 openings of sizes, refrigeration working medium is temperature through choke valve I 6 throttling is 5 DEG C, pressure is the refrigerant of 0.5MPa, in inflow evaporimeter 7, absorption refrigeration becomes temperature is 10 DEG C, pressure is the gas of 0.7MPa, evaporimeter 7 is immersed in and is full of in the heat exchanger 10 of refrigerating medium water, then the cold water in heat exchanger 10 is pumped in cold accumulation bucket 13 by water pump I 11 and magnetic valve II 12 and store, realize one-level and produce cold water;
Refrigeration working medium after one-level being freezed is the refrigerant of 0 ~ 1 DEG C through choke valve II 8 throttling, flow in cold accumulation bucket 13 sweat cooling that directly absorbs heat, until after in cold accumulation bucket 13, water all becomes ice, close down compressor 1, the refrigeration working medium being evaporated to gaseous state flows out and enters gas-liquid separator II 9 above cold accumulation bucket 13, realizes secondary ice making;
As required the cold water in cold accumulation bucket 13 is extracted out through water pump II 14, then flow into and blow out to room temperature lowering by cold through magnetic valve III 15, check valve 16, ratio adjusting valve I 17 in indoor apparatus of air conditioner 18, the water having exchanged cold flows in cold accumulation bucket 13 through ratio adjusting valve II 19 draws cold.
Controller 20 controls compressor 1, magnetic valve I 5, magnetic valve II 12 and magnetic valve III 15, simultaneously also regulable control water pump I 11 and water pump II 14.
As shown in Figure 2, to produce separately the cold water course of work as follows in the utility model parallel connection:
The refrigeration working medium that gas-liquid separator II 9 is sent into is compressed into that temperature is 45 DEG C, pressure is the Compressed Gas of 1.8MPa by compressor 1, after gas-liquid separator I 2, condenser 3, be condensed into that temperature is 35 DEG C, pressure be that 1.8MPa liquid flows into reservoir 4, and by three-way solenoid valve I 5 control refrigeration working medium the flow direction and respectively to the flow velocity of stream;
To control three-way solenoid valve I 5 be temperature by whole refrigeration working medium through choke valve I 6 throttling is 7 DEG C, pressure is the refrigerant of 0.6MPa, in inflow evaporimeter 7, absorption refrigeration becomes temperature is 12 DEG C, pressure is the gas of 0.8MPa, evaporimeter 7 is immersed in and is full of in the heat exchanger 10 of refrigerating medium water, then the cold water in heat exchanger 10 is pumped in cold accumulation bucket 13 by water pump I 11 and magnetic valve II 12 and store, the refrigeration working medium being evaporated to gaseous state in evaporimeter 7 flows into gas-liquid separator II 9, realizes one-level and produces cold water;
Do not open the opening of three-way solenoid valve I 5 pairs of cold accumulation buckets 13, thus do not carry out ice making;
As required the cold water in cold accumulation bucket 13 is extracted out through water pump II 14, then flow into and blow out to room temperature lowering by cold through magnetic valve III 15, check valve 16, ratio adjusting valve I 17 in indoor apparatus of air conditioner 18, the water having exchanged cold flows in cold accumulation bucket 13 through ratio adjusting valve II 19 draws cold.
Controller 20 controls compressor 1, magnetic valve I 5, magnetic valve II 12 and magnetic valve III 15, simultaneously also regulable control water pump I 11 and water pump II 14.
As shown in Figure 2, the utility model independent ice making course of work in parallel is as follows:
The refrigeration working medium that gas-liquid separator II 9 is sent into is compressed into that temperature is 35 DEG C, pressure is the Compressed Gas of 1.2MPa by compressor 1, after gas-liquid separator I 2, condenser 3, be condensed into that temperature is 25 DEG C, pressure be that 1.2MPa liquid flows into reservoir 4, and by three-way solenoid valve I 5 control refrigeration working medium the flow direction and respectively to the flow velocity of stream;
Do not open the opening of three-way solenoid valve I 5 pairs of evaporimeters 7, thus do not carry out producing cold water;
Control the refrigerant that the whole refrigeration working mediums after compression condensation through choke valve III 21 throttling are 0 ~ 1 DEG C by three-way solenoid valve I 5, flow in cold accumulation bucket 13 sweat cooling that directly absorbs heat, until after in cold accumulation bucket 13, water all becomes ice, close down compressor 1, the refrigeration working medium being evaporated to gaseous state in cold accumulation bucket 13 flows out and enters gas-liquid separator II 9 above cold accumulation bucket 13, realizes secondary ice making;
As required the cold water in cold accumulation bucket 13 is extracted out through water pump II 14, then flow into and blow out to room temperature lowering by cold through magnetic valve III 15, check valve 16, ratio adjusting valve I 17 in indoor apparatus of air conditioner 18, the water having exchanged cold flows in cold accumulation bucket 13 through ratio adjusting valve II 19 draws cold.
Controller 20 controls compressor 1, magnetic valve I 5, magnetic valve II 12 and magnetic valve III 15, simultaneously also regulable control water pump I 11 and water pump II 14.
As shown in Figure 2, the utility model parallel connection first freeze after the ice making course of work as follows:
The refrigeration working medium that gas-liquid separator II 9 is sent into is compressed into that temperature is 35 DEG C, pressure is the Compressed Gas of 1.8MPa by compressor 1, after gas-liquid separator I 2, condenser 3, be condensed into that temperature is 25 DEG C, pressure be that 1.8MPa liquid flows into reservoir 4, and by three-way solenoid valve I 5 control refrigeration working medium the flow direction and respectively to the flow velocity of stream;
To control three-way solenoid valve I 5 be temperature by whole refrigeration working medium through choke valve I 6 throttling is 5 DEG C, pressure is the refrigerant of 0.5MPa, in inflow evaporimeter 7, absorption refrigeration becomes temperature is 10 DEG C, pressure is the gas of 0.8MPa, evaporimeter 7 is immersed in and is full of in the heat exchanger 10 of refrigerating medium water, then the cold water in heat exchanger 10 is pumped in cold accumulation bucket 13 by water pump I 11 and magnetic valve II 12 and store, the refrigeration working medium being evaporated to gaseous state in evaporimeter 7 flows into gas-liquid separator II 9, realizes one-level and produces cold water;
Then the refrigerant that the whole refrigeration working mediums after compression condensation through choke valve III 21 throttling are 0 ~ 1 DEG C by three-way solenoid valve I 5 is controlled, flow in cold accumulation bucket 13 sweat cooling that directly absorbs heat, until after in cold accumulation bucket 13, water all becomes ice, close down compressor 1, the refrigeration working medium being evaporated to gaseous state flows out and enters gas-liquid separator II 9 above cold accumulation bucket 13, realizes secondary ice making;
As required the cold water in cold accumulation bucket 13 is extracted out through water pump II 14, then flow into and blow out to room temperature lowering by cold through magnetic valve III 15, check valve 16, ratio adjusting valve I 17 in indoor apparatus of air conditioner 18, the water having exchanged cold flows in cold accumulation bucket 13 through ratio adjusting valve II 19 draws cold.
Controller 20 controls compressor 1, magnetic valve I 5, magnetic valve II 12 and magnetic valve III 15, simultaneously also regulable control water pump I 11 and water pump II 14.
As shown in Figure 2, to carry out the course of work as follows simultaneously for the utility model parallel connection refrigeration and ice making:
The refrigeration working medium that gas-liquid separator II 9 is sent into is compressed into that temperature is 40 DEG C, pressure is the Compressed Gas of 1.2MPa by compressor 1, after gas-liquid separator I 2, condenser 3, be condensed into that temperature is 30 DEG C, pressure be that 1.2MPa liquid flows into reservoir 4, and by three-way solenoid valve I 5 control refrigeration working medium the flow direction and respectively to the flow velocity of stream;
To control three-way solenoid valve I 5 be temperature by a part of refrigeration working medium through choke valve I 6 throttling is 3 DEG C, pressure is the refrigerant of 0.4MPa, in inflow evaporimeter 7, absorption refrigeration becomes temperature is 8 DEG C, pressure is the gas of 0.6MPa, evaporimeter 7 is immersed in and is full of in the heat exchanger 10 of refrigerating medium water, then the cold water in heat exchanger 10 is pumped in cold accumulation bucket 13 by water pump I 11 and magnetic valve II 12 and store, the refrigeration working medium being evaporated to gaseous state in evaporimeter 7 flows into gas-liquid separator II 9, realizes one-level and produces cold water;
Control the refrigerant that the other a part of refrigeration working medium after compression condensation through choke valve III 21 throttling is 0 ~ 1 DEG C by three-way solenoid valve I 5, flow in cold accumulation bucket 13 sweat cooling that directly absorbs heat, until after in cold accumulation bucket 13, water all becomes ice, close down compressor 1, the refrigeration working medium being evaporated to gaseous state flows out and enters gas-liquid separator II 9 above cold accumulation bucket 13, realizes secondary ice making;
As required the cold water in cold accumulation bucket 13 is extracted out through water pump II 14, then flow into and blow out to room temperature lowering by cold through magnetic valve III 15, check valve 16, ratio adjusting valve I 17 in indoor apparatus of air conditioner 18, the water having exchanged cold flows in cold accumulation bucket 13 through ratio adjusting valve II 19 draws cold.
Controller 20 controls compressor 1, magnetic valve I 5, magnetic valve II 12 and magnetic valve III 15, simultaneously also regulable control water pump I 11 and water pump II 14.
Claims (6)
1. a single compressor the two-stage dynamic refrigeration and cold accumulation air-conditioning system, comprise compressor (1), gas-liquid separator I (2), condenser (3), reservoir (4), magnetic valve I (5), gas-liquid separator II (9), the blast pipe of described compressor (1) is successively by gas-liquid separator I (2), condenser (3), reservoir (4) is communicated with magnetic valve I (5), characterized by further comprising one-level refrigerating plant (A), two-stage system ice production apparatus (B), change cold cooling aircondition (C), the evaporimeter (7) of described one-level refrigerating plant (A) is immersed in heat exchanger (10), the outlet of described magnetic valve I (5) and evaporimeter (7), be communicated with the entrance of gas-liquid separator II (9) after cold accumulation bucket (13) serial or parallel connection, the outlet of described heat exchanger (10) is communicated with the entrance of magnetic valve II (12) with cold accumulation bucket (13) top by water pump I (11) successively, the outlet of described cold accumulation bucket (13) bottom is communicated with the entrance of heat exchanger (10), the liquid outlet of described cold accumulation bucket (13) is communicated with the entrance and exit changing cold cooling aircondition (C) respectively with liquid inlet.
2. refrigeration and cold accumulation air-conditioning system according to claim 1, it is characterized in that described one-level refrigerating plant (A) also comprises choke valve I (6), the entrance of described choke valve I (6) and the outlet of magnetic valve I (5), the outlet of described choke valve I (6) is communicated with the entrance of cold accumulation bucket (13) by evaporimeter (7), choke valve II (8) successively, and the outlet of described cold accumulation bucket (13) is communicated with the entrance of gas-liquid separator II (9).
3. refrigeration and cold accumulation air-conditioning system according to claim 2, it is characterized in that the outlet of described choke valve I (6) is communicated with the entrance on evaporimeter (7) top, the outlet of described evaporimeter (7) bottom is communicated with by the entrance of choke valve II (8) with cold accumulation bucket (13) bottom, the outlet at described cold accumulation bucket (13) top is communicated with the entrance of gas-liquid separator II (9), the outlet on described heat exchanger (10) top is communicated with the entrance of magnetic valve II (12) with cold accumulation bucket (13) top by water pump I (11) successively, the outlet of described cold accumulation bucket (13) bottom is communicated with the entrance of heat exchanger (10) bottom.
4. refrigeration and cold accumulation air-conditioning system according to claim 1, it is characterized in that described one-level refrigerating plant (A) also comprises choke valve I (6), described magnetic valve I (5) is three-way magnetic valve, one of entrance and magnetic valve I (5) outlet of described choke valve (6), the outlet of described choke valve I (6) is directly communicated with the entrance of gas-liquid separator II (9) by evaporimeter (7), another outlet of described magnetic valve I (5) is communicated with by the entrance of choke valve III (21) with cold accumulation bucket (13), the outlet of described cold accumulation bucket (13) is communicated with the entrance of gas-liquid separator II (9).
5. refrigeration and cold accumulation air-conditioning system according to claim 4, it is characterized in that the outlet of described choke valve I (6) is communicated with the entrance on evaporimeter (7) top, the outlet of described evaporimeter (7) bottom is communicated with the entrance of gas-liquid separator II (9), another outlet of described magnetic valve I (5) is communicated with by the entrance of choke valve III (21) with cold accumulation bucket (13) bottom, the outlet on described heat exchanger (10) top is communicated with the entrance of magnetic valve II (12) with cold accumulation bucket (13) top by water pump I (11) successively, the outlet of described cold accumulation bucket (13) bottom is communicated with the entrance of heat exchanger (10) bottom.
6. the refrigeration and cold accumulation air-conditioning system according to claim 1 to 5 any one, change cold cooling aircondition (C) described in it is characterized in that and comprise water pump II (14), magnetic valve III (15), check valve (16), ratio adjusting valve I (17), indoor apparatus of air conditioner (18), ratio adjusting valve II (19), controller (20), the liquid outlet of described cold accumulation bucket (13) is successively by water pump II (14), magnetic valve III (15), check valve (16), ratio adjusting valve I (17), indoor apparatus of air conditioner (18) is communicated with its liquid inlet with ratio adjusting valve II (19), described controller (20) respectively with compressor (1), magnetic valve I (5), magnetic valve II (12), magnetic valve III (15), water pump I (11) and water pump II (14) electrical connection.
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| Application Number | Priority Date | Filing Date | Title |
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| CN201520735741.4U CN204963276U (en) | 2015-09-22 | 2015-09-22 | Single compressor second grade developments refrigeration cold -storage air conditioning system |
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| CN201520735741.4U CN204963276U (en) | 2015-09-22 | 2015-09-22 | Single compressor second grade developments refrigeration cold -storage air conditioning system |
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105135725A (en) * | 2015-09-22 | 2015-12-09 | 云南智谷新能源技术开发有限公司 | Single-compressor secondary dynamic refrigeration cold-storage air-conditioning system and refrigeration method thereof |
| CN107289654A (en) * | 2016-04-11 | 2017-10-24 | 青月村燊股份有限公司 | Refrigerator with deposit refrigerating capacity |
-
2015
- 2015-09-22 CN CN201520735741.4U patent/CN204963276U/en not_active Expired - Fee Related
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105135725A (en) * | 2015-09-22 | 2015-12-09 | 云南智谷新能源技术开发有限公司 | Single-compressor secondary dynamic refrigeration cold-storage air-conditioning system and refrigeration method thereof |
| CN105135725B (en) * | 2015-09-22 | 2017-08-25 | 云南智谷新能源技术开发有限公司 | A kind of single compressor the two-stage dynamic refrigeration and cold accumulation air-conditioning system and its refrigerating method |
| CN107289654A (en) * | 2016-04-11 | 2017-10-24 | 青月村燊股份有限公司 | Refrigerator with deposit refrigerating capacity |
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