CN104075486A - Apparatus for dual heat pump - Google Patents
Apparatus for dual heat pump Download PDFInfo
- Publication number
- CN104075486A CN104075486A CN201310600966.4A CN201310600966A CN104075486A CN 104075486 A CN104075486 A CN 104075486A CN 201310600966 A CN201310600966 A CN 201310600966A CN 104075486 A CN104075486 A CN 104075486A
- Authority
- CN
- China
- Prior art keywords
- temperature side
- heat exchanger
- low temperature
- defrosting
- high temperature
- 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.)
- Granted
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B47/00—Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass
- F25B47/02—Defrosting cycles
- F25B47/022—Defrosting cycles hot gas defrosting
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B30/00—Heat pumps
- F25B30/02—Heat pumps of the compression type
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B41/00—Fluid-circulation arrangements
- F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
- F25B2313/021—Indoor unit or outdoor unit with auxiliary heat exchanger not forming part of the indoor or outdoor unit
- F25B2313/0211—Indoor unit or outdoor unit with auxiliary heat exchanger not forming part of the indoor or outdoor unit the auxiliary heat exchanger being only used during defrosting
Abstract
A binary heat pump device is provided to improve stability and heating efficiency of products by controlling a compressed capacity ratio between low-temperature and high-temperature side compressors in a binary refrigerating cycle. CONSTITUTION: An outlet of a high-temperature side compressor(220) is alternately connected to an inlet of a hot water heat exchanger(222) and an inlet of a hot gas defrosting heat exchanger(224) by electronic valve control. A low-temperature side outlet of a binary heat exchanger(211) is alternately connected to an inlet of a low-temperature side evaporator(217) and an inlet of a defrost compensation heat exchanger(215) by the electronic valve control. When an outlet of a high-temperature side compressor is connected to the inlet of the hot gas defrosting heat exchanger for defrosting, the low-temperature side outlet of the binary heat exchanger is connected to the inlet of the defrost compensation heat exchanger by the electronic valve control.
Description
Technical field
The present invention relates to heat pump assembly, specifically in binary refrigeration circulation, regulate the compression volume ratio of low temperature side and high temperature side compressor, the binary heat pump assembly of improving product stability and the efficiency of heating surface.
Background technology
Binary refrigeration circulation refers to the refrigeration system that uses different boiling cold-producing medium.This cold-producing medium is to be transformed into gas phase by its liquid phase before and after boiling point, or gas phase is transformed into liquid phase.
And being divided into the low temperature side of low-temperature refrigerant and the high temperature side of the high temperature refrigerant that use is easily seethed with excitement under higher temperature that use at low-temperature boiling, the condensation of described high temperature side cold-producing medium and described low temperature side cold-producing medium is to occur at a spray-type heat exchanger.Although therefore winter environment temperature is low, the cold-producing medium EGT that also can make high temperature side keeps 100 DEG C of above high temperature and effective to the production of hot water.
On the other hand, traditional heat pump assembly is that the compressor capacity of low temperature side and high temperature side differently forms, and adopts low temperature side compressor capacity and high temperature compressed machine capacity in the fixing mode of the ratio of 0.7: 1.Thereupon, in the winter time-15 DEG C of following freeze-ups because of the capacity of low temperature side compressor little, the evaporation efficiency on described spray-type heat exchanger reduces and reduces high temperature side hot water production efficiency.
On the contrary, the compressor capacity of low temperature side and high temperature side forms in the same manner, to changing according to the season that the temperature rises to after above zero, because excessive condensation load and pressure occur the high expansion temperature of low temperature side low-temperature refrigerant, and the load of compressor is excessive and significantly reduced by breakage or durability.
Traditional air heat exchanger is the effect of bringing into play condenser under refrigeration plant or defrosting mode, therefore under refrigeration hotsync pattern, do not use and can form kind of refrigeration cycle yet, but on described air heat exchanger, be equipped with the circulation pipe of low-temperature refrigerant, reduce the internal circulating load of low-temperature refrigerant, circulation becomes unstable and causes overvoltage or overheated, and the welding position that further causes kind of refrigeration cycle pipe is by damaged problem.
Formerly technical literature
Patent documentation
No. 2003-0071607th, (patent documentation 0001) Korea S's publication.
Summary of the invention
Technical problem
The technical problem to be solved in the present invention is to provide a kind of compression volume ratio that regulates low temperature side and high temperature side compressor in binary refrigeration circulation, the binary heat pump assembly of improving product stability and the efficiency of heating surface.
Technical scheme
For solving described problem, the technical solution adopted in the present invention is, a kind of binary heat pump assembly is provided, as being formed by low temperature side kind of refrigeration cycle and high temperature side kind of refrigeration cycle, and comprise the binary heat pump assembly of the binary heat exchanger that makes the combination of mutually carrying out heat exchange of low temperature side condenser and high temperature side evaporimeter; High temperature side compressor outlet side flows into end with the hot water heat exchanger being equipped with for the hot water of heat hot tank, and for defrosting and low temperature side evaporimeter carry out the inflow end of the hot gas defrosting heat exchanger that heat exchange is equipped with, mutually alternately connect and be equipped with by solenoid control; The low temperature side outlet side of described binary heat exchanger and low temperature side evaporimeter flow into end, and for carrying out with cold water the defrosting, compensating heat exchanger inflow end that heat exchange is equipped with, are mutually alternately connected and be equipped with by solenoid control; For defrosting, when described high temperature side compressor outlet side is connected with the inflow end of described hot gas defrosting heat exchanger, by the control of magnetic valve, the low temperature side outlet side of described binary heat exchanger is connected with described defrosting, compensating heat exchanger inflow end.
A part in the cold-producing medium of one of the described low temperature side evaporimeter inflow end that preferably, inflow is connected with the low temperature side outlet side of described binary heat exchanger and described defrosting, compensating heat exchanger inflow end is to be supplied to the recuperation of heat heat exchanger being connected with the low temperature side outlet side of described binary heat exchanger.
Preferably, while holding the first magnetic valve being equipped with open for connecting described high temperature side compressor outlet side and the inflow of described hot water heat exchanger, control magnetic valve, make low temperature side outlet side for connecting described binary heat exchanger and heat expansion valve and be connected the 3rd magnetic valve being equipped with by the opening that links.
Preferably, for connecting the second magnetic valve that the inflow end of described high temperature side compressor outlet side and described hot gas defrosting heat exchanger is equipped with when open, control magnetic valve, make the 4th magnetic valve that low temperature side outlet side for connecting described binary heat exchanger and defrosting expansion valve be equipped with by the opening that links.
Preferably, the low temperature side compressor of described low temperature side and high temperature side kind of refrigeration cycle and high temperature side compressor capacity are with 1.4 ~ 1.6: 1 composition of proportions; When testing environment temperature exceedes design temperature, reduce the boiling point of low-temperature refrigerant, control described low temperature side evaporimeter and prevent described low temperature side compressor generation overvoltage.
Beneficial effect
The invention has the beneficial effects as follows,
First, dynamically recycle to described hot water heat exchanger and hot gas defrosting heat exchanger from the described high temperature refrigerant of described high temperature side compressor discharge, and described high temperature refrigerant is mutually linked and is controlled to described hot gas defrosting heat exchanger circulation time, described low-temperature refrigerant is circulated to described defrosting, compensating heat exchanger, described low temperature side evaporimeter is defrosted with described high temperature refrigerant, and be the heat of evaporation that described binary heat exchanger compensates described high temperature refrigerant, described low-temperature refrigerant circulation and be convenient to supply the thermal source of described high temperature refrigerant, defrost fast, saving heats dwell time and the efficiency of heating surface of improving product.
The second, described low-temperature refrigerant is in the discharge that is condensed of described binary heat exchanger, and expand at described recuperation of heat expansion valve, in the described heat recovery exchanger evaporation being equipped with for underground heat to waste water thermal cycle, save the power consumption of described low temperature side evaporimeter and improving product efficiency.
Three, described low temperature side compressor and described high temperature side compressor capacity ratio are with 1.4 ~ 1.6: 1 composition of proportions, during severe winter by the ample supply of described binary heat exchanger for the thermal source of described high temperature refrigerant evaporation the efficiency of heating surface of improving product, and for to prevent the overvoltage of described low temperature side compressor according to environment temperature, control described low temperature side evaporimeter, prevent described low temperature side compressor load excessive, thus the stability of improving product.
Brief description of the drawings
Fig. 1 is the block diagram of the binary heat pump assembly of one embodiment of the invention;
Fig. 2 is the flow chart that represents that the binary heat pump assembly of one embodiment of the invention defrosts;
Fig. 3 is the block diagram of the binary heat pump assembly of second embodiment of the invention;
Fig. 4 is the block diagram of the binary heat pump assembly of third embodiment of the invention.
[symbol description]
100,200,300: binary heat pump assembly; 10,210,310: low temperature side compressor;
20,220,320: high temperature side compressor; 11,211,311: binary heat exchanger;
16,216,316: heat expansion valve; 13,213,313: the three magnetic valves;
13a, 213a, 313a: the 4th magnetic valve; 14,214,314: defrosting expansion valve;
15,215,315: defrosting, compensating heat exchanger; 17,217,317: low temperature side evaporimeter;
21,221,321: the first magnetic valves; 21a, 221a, 321a: the second magnetic valve;
22,222,322: hot water heat exchanger; 23,223,323: hot water storgae;
109,209,309: defrosting hot gas supply line; 330: cold rinse bank;
24,224,324: hot gas defrosting heat exchanger; 233,333: recuperation of heat heat exchanger.
Detailed description of the invention
Describe the binary heat pump assembly of the preferred embodiment of the present invention in detail below in conjunction with accompanying drawing.Binary heat pump assembly is at place supply volume hot water and cold water such as bathing pool or sauna bath, hot water swimming pools, the heat of simultaneously freezing, and the thermal efficiency is high, the refrigerating and heating apparatus of maintenance cost saving.
Fig. 1 is the block diagram of the binary heat pump assembly of one embodiment of the invention.
As shown in Figure 1, binary heat pump assembly 100 its compositions of one embodiment of the invention comprise low temperature side compressor 10, binary heat exchanger 11, low temperature side evaporimeter 17, defrosting, compensating heat exchanger 15, high temperature side compressor 20, hot water heat exchanger 22 and hot gas defrosting heat exchanger 24.
Binary heat pump assembly 100 is by using the low temperature side kind of refrigeration cycle of the low-temperature refrigerant seething with excitement at a lower temperature and using the high temperature side kind of refrigeration cycle that is easy to the high temperature refrigerant of boiling under higher temperature to form.For example, it is R-410a with the mix refrigerant of the synthetic HFC series than mixing of 50:50 that described low-temperature refrigerant can use R-32 and R-125, and described R-410a has the boiling point of-51 DEG C under 1 atmospheric pressure.Described high temperature refrigerant can use the R-134a of HFC series, and described R-134 has the boiling point of-26 DEG C under 1 atmospheric pressure.
On the other hand, described low temperature side compressor 10, under described low temperature side kind of refrigeration cycle, is sent into condenser and makes refrigerant circulation the described low-temperature refrigerant of the low-temp low-pressure flowing into from described low temperature side evaporimeter 17 is compressed into high temperature and high pressure gas.
Described binary heat exchanger 11 is mode combinations of the mutual heat exchange of evaporimeter in condenser and the described low temperature side kind of refrigeration cycle making in described low temperature side kind of refrigeration cycle.Now, the described low-temperature refrigerant that is compressed into HTHP in described low temperature side compressor 10 is the described high temperature refrigerant heat supply to described high temperature side kind of refrigeration cycle at described binary heat exchanger 11, and is condensed into liquid.
Described low temperature side evaporimeter 17 is to heat expansion valve 16 by power supply, and the described low-temperature refrigerant supply periphery heat declining to pressure and temperature is also vaporized and cooling periphery.
Manufacture the refrigerating operaton of cooling water or remove white defrosting on described low temperature side evaporimeter 17 while carrying out for refrigeration, on described binary heat exchanger 11, the described low-temperature refrigerant of condensation flows into described defrosting, compensating heat exchanger 15.Now, be to seize the heat of water supply and make the evaporation of described low-temperature refrigerant at described defrosting, compensating heat exchanger 15.
Described high temperature side compressor 20 is compressed into high temperature and high pressure gas described high temperature refrigerant.The described high temperature refrigerant of the low-temp low-pressure evaporating from described binary heat exchanger 11 in described kind of refrigeration cycle is be compressed into high temperature and high pressure gas and circulate to described hot water heat exchanger 22 or described hot gas defrosting heat exchanger 24 at described high temperature side compressor 20.
Heat or hot water generate time, the described high temperature refrigerant compressing at described high temperature side compressor 20 flows into described hot water heat exchanger 22.Now, to the heat occurring by the condensation of described high temperature refrigerant to the hot water supply of described hot water heat exchanger 22 inner loop at hot water storgae 23.
When defrosting is carried out, on described high temperature side compressor 20, the described high temperature refrigerant of compression is to flow into described hot gas defrosting heat exchanger 24 by defrosting hot gas supply line 109 to remove the frostwork or the frost etc. that on described low temperature side evaporimeter 17, form.
The outlet side that is discharged of described high temperature refrigerant of compression on described high temperature side compressor 20 and the described hot water heat exchanger 22 configuring for the hot water of heat hot tank 23 flow into end and the inflow end of the hot gas defrosting heat exchanger 24 that can heat exchange configures for defrosting and low temperature side evaporimeter 17, can mutually alternately connect by solenoid control.
When the hot water of heat hot tank 23, be to open and close described high temperature side compressor 20 outlet sides and described hot water heat exchanger 22 to flow into the first magnetic valve 21 that between end, pipeline is equipped with open, when defrosting is carried out, open for opening and closing the second magnetic valve 21a that between described high temperature side compressor 20 outlet sides and the inflow end of described hot gas defrosting heat exchanger 24, pipeline is equipped with.
The so-called meaning mutually alternately connecting refers to described in described the first magnetic valve 21 is when open that the second magnetic valve 21a is closed, when described the second magnetic valve 21a is open described in the first magnetic valve 21 be closed.Thereupon, the pipeline of described high temperature refrigerant is opened to a direction, by the compression of described high temperature side compressor 20, cold-producing medium is circulated smoothly.
Described solenoid control is according to user's input, need to heat or drive when heat hot water, implement the action of open described the first magnetic valve 21, according to environment temperature and the required state of heating operation time judgement defrosting, automatically close described the first magnetic valve 21, the action of open described the second magnetic valve 21a is advisable.
Solenoid control is the first magnetic valve 21 for connecting that described high temperature side compressor 20 outlet sides and described hot water heat exchanger 22 flow into that end is equipped with when open, makes to open for connecting described binary heat exchanger 11 low temperature side outlet sides and heating the 3rd electromagnetic valve linking that expansion valve 16 is equipped with.
Specifically, enforcement heats or hot water heating when operation, and described low temperature side kind of refrigeration cycle has by low temperature side compressor 10, oil eliminator 10a, binary heat exchanger 11, liquid reservoir 12, heats the loop structure that expansion valve 16, low temperature side evaporimeter 17, liquid separator 19 form.
Described high temperature side kind of refrigeration cycle is to have the loop structure being made up of high temperature side compressor 20, oil eliminator 20a, hot water heat exchanger 22, liquid reservoir 25, high temperature expansion valve 27, binary heat exchanger 11, liquid separator 29.
Now, on described high temperature side compressor 20, the described high temperature refrigerant of compression is at described high temperature side compressor 20 outlet sides process oil eliminator 20a, flows into end mobile to described hot water heat exchanger 22.And at the mobile pipeline of the interior described high temperature refrigerant of described hot water heat exchanger 22 with by adjacent the pipeline of heated hot water flow outfit and described high temperature refrigerant is condensed, and the heat occurring after condensation is sent to described hot water and heat hot water.
Described high temperature refrigerant to described hot water heat transfer and condensation is to move to the inflow end of described binary heat exchanger 11 through liquid reservoir 25.Described high temperature refrigerant is to expand and become the liquid condition of low-temp low-pressure in described high temperature expansion valve 27, flashes to gaseous state in the heat of the described low-temperature refrigerant of the interior absorption of described binary heat exchanger 11.
Being connected in the 6th magnetic valve 26 being equipped with on the pipeline of high temperature expansion valve at the outlet side of described hot water heat exchanger 22 outlet sides and described hot gas defrosting heat exchanger 24 is along with the operation automatic opening of described high temperature side compressor 20 is advisable.
Described high temperature refrigerant in described binary heat exchanger 11 interior evaporations flows into described high temperature side compressor 20 and circulates through liquid separator 29.
Check that described low-temperature refrigerant dispels the heat in the interior condensation of described binary heat exchanger 11 in the circulation of the interior described low-temperature refrigerant conducting heat to described high temperature refrigerant of described binary heat exchanger 11.Now, the pipeline that described low-temperature refrigerant is mobile and the mobile pipeline of described high temperature refrigerant are for being mutually easy to carry out heat exchange in abutting connection with being equipped with, and are formed as suitable with materials such as the high copper of thermal conductivity.
The described low-temperature refrigerant of condensation is to flow into described cryogenic vaporizer 17 at the low temperature side outlet side of described binary heat exchanger 11 through liquid reservoir 12.Here, open for opening and closing described binary heat exchanger 11 outlet sides and heating the 3rd magnetic valve 13 that between expansion valve 16, pipeline is equipped with, close to be advisable for opening and closing the 4th magnetic valve 13a that between described binary heat exchanger 11 outlet sides and described defrosting expansion valve 14, pipeline is equipped with.
The described low-temperature refrigerant of condensation is to expand with low-temp low-pressure at the described expansion valve 16 that heats, and flows into described low temperature side evaporimeter 17 vaporization and the heat of absorption periphery.
Temperature rise flows into described low temperature side compressor 10 and circulates through liquid separator 19 to the described low-temperature refrigerant of certain level.
Flow into the 3rd magnetic valve 13 that is equipped with between end and described binary heat exchanger 11 outlet sides and described defrosting, compensating heat exchanger 15 at described binary heat exchanger 11 outlet sides and described low temperature side evaporimeter 17 and flow into the 4th magnetic valve 13a being equipped with between end and should mutually replace to open and close and be advisable, but can open as required simultaneously.
In other words, heat or when heat hot water described in the 3rd magnetic valve 13 open, described low-temperature refrigerant evaporates and absorbs external heat from described low temperature side evaporimeter 17, while defrosting for removing the frost that generates from described low temperature side evaporimeter 17 or frostwork, flow into described defrosting, compensating heat exchanger 15 and evaporate.Now, carry out heat exchange heat absorption and vaporize at low-temperature refrigerant described in described defrosting, compensating heat exchanger 15 and cold water.
And refrigeration time can be used described defrosting, compensating heat exchanger 15 to generate cooling water.Now, if cooling water generates too much, open the 3rd magnetic valve 13 that opens and closes pipeline between described binary heat exchanger 11 and described low temperature side evaporimeter 17 regulates circulating mass of refrigerant.
Described the 3rd magnetic valve 13 and described the 4th magnetic valve 13a are controlled by magnetic valve, heat or when heat hot water, open described the 3rd magnetic valve 13, close described the 4th magnetic valve 13a, and defrosting should be automatically controlled open described the 4th magnetic valve 13a while carrying out, close described the 3rd magnetic valve 13 and be advisable.
The low temperature side compressor 10 of described low temperature side and high temperature side kind of refrigeration cycle and high temperature side compressor 20 capacity are preferably with 1.4 ~ 1.6: 1 composition of proportions.
Winter environment temperature reaches-15 DEG C of following severe cold periods, be to keep 7 DEG C of evaporating temperatures between air poor by the described described low-temperature refrigerant that heats expansion valve 16, discharge with the temperature of-22 DEG C, but as the cold-producing medium-51 DEG C of evaporations, fully absorb extraneous air heat and cold-producing medium is all evaporated at described low temperature side evaporimeter 17.
And, described low temperature side compressor 10 is 1.4 ~ 1.6: 1 with the Capacity Ratio of described high temperature side compressor 20, after dividing compression the refrigerant charging of evaporation, send into described binary heat exchanger 11, therefore in described high temperature side kind of refrigeration cycle, fully absorb heat, promote the temperature of the hot water of storage in described hot water storgae 23.
Specifically, for making successfully to be implemented in the evaporation of the described high temperature refrigerant of described hot water heat exchanger 22 heat exchanges, on described binary heat exchanger 11, to carry out the temperature of described low-temperature refrigerant of heat exchange particularly important with described high temperature refrigerant.
Described binary heat exchanger 11 in high temperature side kind of refrigeration cycle is to form described high temperature refrigerant by described high temperature expansion valve 27 with about 5 DEG C evaporations in the winter time, and the described high temperature refrigerant that finishes evaporation carries out after heat exchange condensation at described hot water heat exchanger 22 and the hot water of described hot water storgae 23 after being sucked compression with the temperature of approximately 10 DEG C of left and right by described high temperature side compressor 20, be because of pressure drop through liquid reservoir 25 after high temperature expansion valve 27 expands by throttling arrangement, in described binary heat exchanger 11 process evaporation processes, again the continuous circulation being sucked by high temperature side compressor 20.Thereupon, described hot water is to be heated to form 65 DEG C ~ 70 DEG C temperature to be housed in described hot water storgae 23 afterwards.
The compression volume deficiency of described low temperature side compressor 10, the evaporation of the described high temperature refrigerant by described low-temperature refrigerant cannot be implemented and the efficiency of heating surface declines smoothly.According to experimental result, when the Capacity Ratio of low temperature side compressor and high temperature hot pressing contracting machine is 1:1, show the COP(coefficient of performance of refrigeration machine performance) be 2.52, when the Capacity Ratio of low temperature side compressor and high temperature side compressor is 1.5:1, COP is shown as more than 2.75.
On the other hand, when the external temperature detecting reaches the temperature having arranged when above, for reducing the boiling point of described low-temperature refrigerant, prevent the overvoltage of described low temperature side compressor 10, described low temperature side evaporimeter 17 is implemented to controls.For example, under the environment temperature of changing according to the season more than 10 DEG C, it is more that described low-temperature refrigerant absorbs heat because high-temperature is poor on described low temperature side evaporimeter 17.
Now, described low-temperature refrigerant is that compression ratio heat needs more strength when low, and described low temperature side compressor 10 there will be the excessive phenomenon of load.Therefore when environment temperature exceedes design temperature, limit the rotation number of described low temperature side evaporimeter 17 blower fans, control described low-temperature refrigerant and suitably absorb heat.
Table 1
Above-mentioned table 1 is the actual use heat that represents winter heating circulation, after the compressor capacity that demonstrates low temperature side and high temperature side forms in the same manner with 1.5:1, and the operation characteristic of the blower fan rotation quantity of described low temperature side evaporimeter 17 during with variation of ambient temperature.
As shown in Table 1 above, traditional before improving is no matter environment temperature is how many, the number of revolutions of described low temperature side evaporimeter 17 is consistent, discharges heat more approaches normal temperature and more sharply reduces and lower efficiency, on the contrary, regulate the rotation quantity of described low temperature side evaporimeter 17, while regulating the boiling point of described low-temperature refrigerant, no matter the variation of environment temperature, heat exhaust all can be consistent.
And more approaching normal temperature, the rotation quantity of described low temperature side evaporimeter 17 more reduces and required drive reduction, reduces the power consumption of changing according to the season period, and improve heat but the heat of discharging and hiemal aspect are same.
Fig. 2 is the Defrost operation flow chart of the binary heat pump assembly of one embodiment of the invention.
As shown in Figure 2, described binary heat pump assembly 100 is on described low temperature side evaporimeter 17, to produce frost or frostwork defrosts.
For defrosting, described high temperature side compressor 20 outlet sides are connected in the inflow end of described hot gas defrosting heat exchanger 24, and the low temperature side outlet side of described binary heat exchanger 11, by solenoid control, flows into end with described defrosting, compensating heat exchanger 15 and is connected.
When winter heating, on described low temperature side evaporimeter 17, produce frost or frostwork, hinder the blower fan rotation of described low temperature side evaporimeter 17, or hinder described low-temperature refrigerant heat absorption and reduction heating efficiency, therefore for the frost of removing on described low temperature side evaporimeter 17 is implemented a series of actions.
For heating or heat hot water, described high temperature side compressor 20 drives after (step S10), and described the 6th magnetic valve 26 and described the first magnetic valve 21 are open, and described the second magnetic valve 21a closes and described high temperature refrigerant circulates to described hot water heat exchanger 22.
In addition, described low temperature side compressor 10 is for conducting heat to described high temperature refrigerant at described binary heat exchanger 11, compresses described low-temperature refrigerant and discharges.Now, evaporate described low-temperature refrigerant and described the 3rd magnetic valve 13 openings from described low temperature side evaporimeter 17, the 4th magnetic valve 13a closes.
Thereupon, described high temperature refrigerant and described low-temperature refrigerant circulate through overcompression, condensation, expansion, evaporation stage, and the heat occurring in the condensation phase of described high temperature refrigerant is to be transmitted to described hot water in described hot water heat exchanger 22.The heat occurring in the condensation phase of described low-temperature refrigerant is the required thermal source of evaporation that is used as described high temperature refrigerant in described binary heat exchanger 11.
When environment temperature is reduced to the defrosting temperature following (step S20) of having set, whether the time that relatively heats reaches the defrosting required time (step S30) of having set judges whether to defrost later.For example, the described defrosting temperature of having set preferably calculates winter severe cold phase generation frost or white time spent according to test run result, automatically arranges according to the result generating run defrosting automatic control algorithm calculating.
Test run result humidity between 0 DEG C to 7 DEG C above freezing is the highest, and long-pending frost is more and reduce the operational efficiency of described low temperature side evaporimeter, and-1 DEG C of humidity when following is lower than 40%, and long-pending white phenomenon occurs few, and heating needs to move 90 points and just need above to defrost.
Therefore, according to described Defrost operation automatic control algorithm, can be in environment temperature lower than below 9 DEG C, described low temperature side evaporator outlet temperature, lower than below-1 DEG C, defrosts when before evaporation, after cryogenic temperature and evaporation, cryogenic temperature deviation reaches more than 3 DEG C.And preferably according to ambient humidity, defrost according to the heating operation time.
Now, can be arranged to ambient humidity and more than 35%, heat each run 90 minutes, ambient humidity reaches more than 45% and heats each run 70 minutes, ambient humidity reaches more than 55% and heats each run 50 minutes, ambient humidity reaches 65% and heats each run 45 minutes, ambient humidity reaches more than 70% and heats each run 38 minutes, ambient humidity reaches more than 75% and heats each run 33 minutes, ambient humidity reaches 80% and heats each run 25 minutes, ambient humidity reaches more than 85% and heats each run 22 minutes, ambient humidity reaches while more than 90% heating each run 20 minutes and defrosts.
As mentioned above, according to described operation defrosting automatic control algorithm, can prevent the long-pending frost that produces because of on described low temperature side evaporimeter, there is overload and heat the phenomenon stopping in described low temperature side compressor, thus the stability of improving product.
In other words, in the time that phase in severe winter environment temperature reaches below 8 DEG C, if determine the time of heating and ambient humidity, need to defrost according to the described operation defrosting automatic control algorithm judgement of correspondence.
And judgement need to defrost after (step S40), described binary heat pump assembly 100 is to stop heating, and implements the required a series of actions that defrosts.
First, operation defrosting is to carry out 160 seconds according to the setting value of having set.Now, the blower fan of described low temperature side evaporimeter 17 and described low temperature side compressor 10 can stop about 40 seconds.Therefore, described low-temperature refrigerant circulation time, is absorbed external heat and for effectively defrosting, is prevented described low-temperature refrigerant circulation by described low temperature side evaporimeter 17.
Described low temperature side compressor 10 is operation afterwards at 40 seconds, and simultaneously described low-temperature refrigerant circulates to described defrosting, compensating heat exchanger 15, the described high temperature refrigerant supplying high temperature that high temperature side compressor 20 and described hot gas defrosting heat exchanger 24 circulate described in subtend.
Thereupon, described high temperature refrigerant continues to obtain heat, as long as therefore defrosting is to carry out can completing defrosting in 160 seconds according to the setting value set, all machines normally move and produce hot water.Because the Defrost operation of the described high temperature refrigerant of high temperature is to utilize the method that shortens defrosting time to prevent energy loss.
When described Defrost operation, solenoid control is as follows.
For described high temperature refrigerant is circulated to the described hot gas defrosting heat exchanger 24 possessing on described low temperature side evaporimeter, close described the first magnetic valve 21, open the second magnetic valve 21a(step S50).Thereupon, on described high temperature side compressor 20, the high temperature refrigerant of compression flows into described hot gas defrosting heat exchanger 24, makes defrosting be implemented to described low temperature side evaporimeter 17 heat supplies.
Described hot gas defrosting heat exchanger 24 and described low temperature side evaporimeter 17 are preferably equipped to one or adjacency is advisable.
In other words, for connecting the second magnetic valve 21a that the inflow end of described high temperature side compressor 20 outlet sides and described hot gas defrosting heat exchanger 24 is equipped with when open, control magnetic valve, make to open for the 4th magnetic valve 13a that connects described binary heat exchanger 11 low temperature side outlet sides and the expansion valve 14 that defrosts is equipped with.
Described hot gas defrosting heat exchanger 24 and described low temperature side evaporimeter 17 are to form with light pipeline circle.Especially, to the heat of the described high temperature refrigerant of the light pipe coil circulation of described hot gas defrosting heat exchanger 24 preferably indirect transfer in the light pipe coil of described low temperature side evaporimeter 17.
On the other hand, the Defrost operation time, while exceeding the defrosting, compensating time above (step S60) of having set, drives described low temperature side compressor 10, closes described the 3rd magnetic valve 13, open described the 4th magnetic valve 13a.
Specifically, the described defrosting, compensating time of having set is to be arranged to be advisable about 120 seconds.Described high temperature refrigerant is not received the condensation heat of described low-temperature refrigerant at described binary heat exchanger 11, and circulates about 40 seconds, because described high temperature refrigerant vaporization causes the heat source insufficiency in described binary heat exchanger 11.
Therefore,, for defrosting as early as possible, to described binary heat exchanger 11 supplied heat source, make the evaporation of described high temperature refrigerant and absorb heat carry out smoothly and described low-temperature refrigerant is circulated.Now, described low-temperature refrigerant is from described low temperature side evaporimeter 17 evaporations, the temperature continuous decrease of described low temperature side evaporimeter 17 and cannot defrosting, therefore, turn off described the 3rd magnetic valve 13, open described the 4th magnetic valve 13a, makes described low-temperature refrigerant to defrosting heat exchanger 15 circulate (step S70).
Described low-temperature refrigerant expands from described defrosting expansion valve 14, in described defrosting, compensating heat exchanger 15 heat absorption evaporations.Described defrosting, compensating heat exchanger 15 is connected with feed pipe and supplies the evaporation thermal source of described low-temperature refrigerant.
The defrosting time of carrying out, while exceeding the Defrost operation time of having set (step S80), described binary heat pump assembly completed Defrost operation, for heating or generating hot water drives (step S90).Now, the described Defrost operation time of having set should be set as being advisable about 160 seconds.
As mentioned above, the described high temperature refrigerant of compression on described high temperature side compressor 20 is fed to described hot gas defrosting heat exchanger 24 by described defrosting hot gas supply line 109, described low temperature side evaporimeter 17 is defrosted, and continue effectively to defrost fast for being applied to the thermal source of described high temperature refrigerant evaporation, thereby the efficiency of heating surface of improving product.
Fig. 3 is the block diagram of the binary heat pump assembly of second embodiment of the invention.
As shown in Figure 3, in the second embodiment, except recuperation of heat is with heat exchanger 233, other basic structure is identical with an above-mentioned embodiment, therefore identical structure is no longer described in detail in detail.
Described recuperation of heat is to utilize underground heat or waste water heat with heat exchanger 233, supply the heat of evaporation of described low-temperature refrigerant, and while utilizing described underground heat, described recuperation of heat is embedded in underground with heat exchanger 233, while utilizing described waste water heat, water circulating pipe under bathing pool is assemblied in to described recuperation of heat heat exchanger 233 inside and the heat of evaporation of supplying described low-temperature refrigerant is advisable.
Flowing into the described cryogenic vaporizer 217 being connected with the low temperature side outflow end of described binary heat exchanger 211, to flow into a part in the cold-producing medium that end and described defrosting, compensating heat exchanger (in Fig. 1 15) inflow one of holds be the heat exchanger 233 for recuperation of heat that inflow is connected with the low temperature side outflow end of described binary heat exchanger 211.
Specifically, described low-temperature refrigerant is to described high temperature refrigerant transfer of heat, from described binary heat exchanger 211 low temperature side outlet sides discharges in described binary heat exchanger 211 condensations.Described low-temperature refrigerant is to circulate to described low temperature side evaporimeter 217 for evaporation through liquid reservoir 212.
Here, close described the 3rd magnetic valve 213 by solenoid control, open connect the 5th magnetic valve 231 being equipped with on the low temperature side outlet side of described binary heat exchanger 211 and the pipeline of recuperation of heat expansion valve 232 and described low-temperature refrigerant circulates to described recuperation of heat heat exchanger 233.
Thereupon, can utilize the heat of evaporation of the described low-temperature refrigerant of described underground heat or waste water heat supply, save the electric power of described low temperature side evaporimeter 217 and improving product efficiency.Described the 3rd magnetic valve 213 and described the 5th magnetic valve 231 are alternately to open and close, but according to the supply of underground heat or waste water heat, when evaporation heat source insufficiency, preferably open or regularly alternately switching simultaneously, to pass through described low temperature side evaporimeter 217, to described low-temperature refrigerant heat supply.
Fig. 4 is the block diagram of the binary heat pump assembly of third embodiment of the invention.
As shown in Figure 4, in the 3rd embodiment except recuperation of heat with heat exchanger 333 with produce basic structure cold water by described defrosting, compensating heat exchanger 315 identical with an above-mentioned embodiment and its concrete structure is no longer described in detail in detail.
Here, described low-temperature refrigerant be in described binary heat exchanger 311 condensations to described high temperature refrigerant transfer of heat, discharge and by liquid reservoir 312 from the low temperature side outlet side of described binary heat exchanger 311.
Described the 3rd magnetic valve 313 can make described low-temperature refrigerant circulate to described low temperature side evaporimeter 317, described the 4th magnetic valve 313a makes described low-temperature refrigerant circulate to described defrosting, compensating heat exchanger 315, and described the 5th magnetic valve 331 is that described low-temperature refrigerant is circulated to described recuperation of heat heat exchanger 333.
On described defrosting, compensating heat exchanger 315, be equipped with from storage the pipeline to described defrosting, compensating heat exchanger 315 interior circulations for the cold rinse bank 330 that freezes, and the pipeline of the described low-temperature refrigerant circulation of discharging from the low temperature side discharge pipe of described binary heat exchanger 311.
Specifically, summer, the use amount of hot water can reduce, therefore described high temperature side kind of refrigeration cycle is to move by spells, make to reach keeping warm mode in described hot water storgae 323, or out of service, on the contrary, described low temperature side kind of refrigeration cycle is to convert refrigeration to and actively operation.
For generating the cold water for freezing, the described low-temperature refrigerant compressing at described low temperature side compressor 310 is in described binary heat exchanger 311 condensations.Now, cryocondensation is transmitted in described high temperature refrigerant and for hot water production.
Described low-temperature refrigerant is through liquid reservoir 312 pipeline being connected by described low temperature side evaporimeter 317 or described recuperation of heat heat exchanger 333, described defrosting, compensating heat exchanger 315 that circulates, for producing cold water, described the 3rd magnetic valve 313 and described the 5th magnetic valve 331 are closed, and described the 4th magnetic valve 313a is open.
Described the 4th magnetic valve 313a when open described in low-temperature refrigerant be to expand in defrosting expansion valve 314, the described defrosting, compensating heat exchanger 315 that circulates, seizes the heat of the cold water circulating at described cold rinse bank 330, makes the cooling vaporization of cold water.
By the circulation of described low-temperature refrigerant, on described cold rinse bank 330 in store cooling water and for refrigeration.
Described high temperature refrigerant is to circulate to described hot water heat exchanger 322 or described hot gas defrosting heat exchanger 324.
While needing hot water, the first magnetic valve 321 is opened for described hot water heat exchanger 322 circulates, and while not needing hot water, the second magnetic valve 321a is open, is advisable to described hot gas defrosting heat exchanger 324 circulations.Now, described high temperature refrigerant is seized heat and is condensed by the extraneous air of the blower fan supply in described hot gas defrosting heat exchanger 324, circulates and evaporates after described high temperature expansion valve 326 expands through liquid reservoir 325 to described binary heat exchanger 311.
As mentioned above, because can produce cooling cold water and heat with hot water simultaneously, change according to the season and wait while needing refrigeration and hot water simultaneously, prevent that product load is excessive, and saving power consumption and improving product efficiency.
Above embodiment and accompanying drawing only, in order to technical scheme of the present invention to be described, are not intended to limit; Although the present invention is had been described in detail with reference to previous embodiment, those of ordinary skill in the art is to be understood that: it still can be modified to the technical scheme described in aforementioned each embodiment, or part technical characterictic is wherein equal to replacement; And these amendments or replacement do not make the essence of appropriate technical solution depart from the scope of technical scheme described in various embodiments of the present invention.Protection scope of the present invention should make an explanation according to described claim scope, and all technical schemes in its equal scope should all belong to claim scope of the present invention.
Claims (5)
1. a binary heat pump assembly, is characterized in that,
As being formed by low temperature side kind of refrigeration cycle and high temperature side kind of refrigeration cycle, and comprise the binary heat pump assembly of the binary heat exchanger that makes the combination of mutually carrying out heat exchange of low temperature side condenser and high temperature side evaporimeter;
High temperature side compressor outlet side flows into end with the hot water heat exchanger being equipped with for the hot water of heat hot tank, and for defrosting and low temperature side evaporimeter carry out the inflow end of the hot gas defrosting heat exchanger that heat exchange is equipped with, mutually alternately connect and be equipped with by solenoid control;
The low temperature side outlet side of described binary heat exchanger and low temperature side evaporimeter flow into end, and for carrying out with cold water the defrosting, compensating heat exchanger inflow end that heat exchange is equipped with, are mutually alternately connected and be equipped with by solenoid control;
For defrosting, when described high temperature side compressor outlet side is connected with the inflow end of described hot gas defrosting heat exchanger, by the control of magnetic valve, the low temperature side outlet side of described binary heat exchanger is connected with described defrosting, compensating heat exchanger inflow end.
2. binary heat pump assembly according to claim 1, is characterized in that,
A part in the cold-producing medium of one of the described low temperature side evaporimeter inflow end that inflow is connected with the low temperature side outlet side of described binary heat exchanger and described defrosting, compensating heat exchanger inflow end is to be supplied to the recuperation of heat heat exchanger being connected with the low temperature side outlet side of described binary heat exchanger.
3. binary heat pump assembly according to claim 1, is characterized in that,
While holding the first magnetic valve being equipped with open for connecting described high temperature side compressor outlet side and the inflow of described hot water heat exchanger, control magnetic valve, make low temperature side outlet side for connecting described binary heat exchanger and heat expansion valve and be connected the 3rd magnetic valve being equipped with by the opening that links.
4. binary heat pump assembly according to claim 1, is characterized in that,
For connecting the second magnetic valve that the inflow end of described high temperature side compressor outlet side and described hot gas defrosting heat exchanger is equipped with when open, control magnetic valve, make the 4th magnetic valve that low temperature side outlet side for connecting described binary heat exchanger and defrosting expansion valve be equipped with by the opening that links.
5. binary heat pump assembly according to claim 1, is characterized in that,
Low temperature side compressor and the high temperature side compressor capacity of described low temperature side and high temperature side kind of refrigeration cycle are with 1.4 ~ 1.6: 1 composition of proportions;
When testing environment temperature exceedes design temperature, reduce the boiling point of low-temperature refrigerant, control described low temperature side evaporimeter and prevent described low temperature side compressor generation overvoltage.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| KR10-2013-0031838 | 2013-03-26 | ||
| KR1020130031838A KR101262927B1 (en) | 2013-03-26 | 2013-03-26 | Apparatus for dual heat pump |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN104075486A true CN104075486A (en) | 2014-10-01 |
| CN104075486B CN104075486B (en) | 2018-02-23 |
Family
ID=48665936
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201310600966.4A Expired - Fee Related CN104075486B (en) | 2013-03-26 | 2013-11-25 | Binary heat pump assembly |
Country Status (2)
| Country | Link |
|---|---|
| KR (1) | KR101262927B1 (en) |
| CN (1) | CN104075486B (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105180536A (en) * | 2015-08-27 | 2015-12-23 | 广东美的暖通设备有限公司 | Defrosting device for heat pump water heater and method for defrosting through device |
| CN106152645A (en) * | 2016-07-27 | 2016-11-23 | 山东华旗新能源科技有限公司 | The defrosting control system of heat sink and method |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR101657664B1 (en) * | 2016-04-15 | 2016-09-19 | 주식회사 신우종합에너지 | air conditioning apparatus for dual heat pump |
| KR101835786B1 (en) | 2017-05-17 | 2018-04-19 | (주)대호냉각기 | Driving Transfer System of Air Heat-Binary Cycle Heat Pump |
Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0359369A (en) * | 1989-07-26 | 1991-03-14 | Nishi Nippon Seiki Seisakusho:Kk | Defrosting device in two-dimensional cryogenic refrigerator |
| FR2825143A1 (en) * | 2001-05-28 | 2002-11-29 | Energie Transfert Thermique | Monobloc system and hot and cold water production installation, for air conditioning, uses a programmable automatic three way valve to control fluid circulating in principal and auxiliary circuits |
| KR20030071607A (en) * | 2003-08-01 | 2003-09-03 | 오원길 | Heat pump system of cooling, heating and hot water using binary refrigerating machine with two stage cascade refrigeration |
| JP2006017376A (en) * | 2004-07-01 | 2006-01-19 | Daikin Ind Ltd | Water heater |
| CN201508074U (en) * | 2009-02-19 | 2010-06-16 | 薛天鹏 | Air source combined cycle refrigeration low-temperature heat pump machine set |
| KR20110130086A (en) * | 2010-05-27 | 2011-12-05 | 김종석 | The heat pump system have to double pipe type evaporater for of cooling and heating water production to very stability the same time driving mode heat pump cycle |
| CN102818308A (en) * | 2011-06-10 | 2012-12-12 | 三星电子株式会社 | Water supply apparatus |
-
2013
- 2013-03-26 KR KR1020130031838A patent/KR101262927B1/en active IP Right Grant
- 2013-11-25 CN CN201310600966.4A patent/CN104075486B/en not_active Expired - Fee Related
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0359369A (en) * | 1989-07-26 | 1991-03-14 | Nishi Nippon Seiki Seisakusho:Kk | Defrosting device in two-dimensional cryogenic refrigerator |
| FR2825143A1 (en) * | 2001-05-28 | 2002-11-29 | Energie Transfert Thermique | Monobloc system and hot and cold water production installation, for air conditioning, uses a programmable automatic three way valve to control fluid circulating in principal and auxiliary circuits |
| KR20030071607A (en) * | 2003-08-01 | 2003-09-03 | 오원길 | Heat pump system of cooling, heating and hot water using binary refrigerating machine with two stage cascade refrigeration |
| JP2006017376A (en) * | 2004-07-01 | 2006-01-19 | Daikin Ind Ltd | Water heater |
| CN201508074U (en) * | 2009-02-19 | 2010-06-16 | 薛天鹏 | Air source combined cycle refrigeration low-temperature heat pump machine set |
| KR20110130086A (en) * | 2010-05-27 | 2011-12-05 | 김종석 | The heat pump system have to double pipe type evaporater for of cooling and heating water production to very stability the same time driving mode heat pump cycle |
| CN102818308A (en) * | 2011-06-10 | 2012-12-12 | 三星电子株式会社 | Water supply apparatus |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105180536A (en) * | 2015-08-27 | 2015-12-23 | 广东美的暖通设备有限公司 | Defrosting device for heat pump water heater and method for defrosting through device |
| CN105180536B (en) * | 2015-08-27 | 2018-02-06 | 广东美的暖通设备有限公司 | A kind of heat pump water-heating machine defroster and the method for application device defrosting |
| CN106152645A (en) * | 2016-07-27 | 2016-11-23 | 山东华旗新能源科技有限公司 | The defrosting control system of heat sink and method |
| CN106152645B (en) * | 2016-07-27 | 2019-03-29 | 山东华旗新能源科技有限公司 | The defrosting control system and method for heat sink |
Also Published As
| Publication number | Publication date |
|---|---|
| KR101262927B1 (en) | 2013-05-13 |
| CN104075486B (en) | 2018-02-23 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| WO2017063321A1 (en) | Air source heat pump spray defrosting device based on super-hydrophobic finned tube heat exchanger | |
| US20120312040A1 (en) | Air conditioner in electric vehicle | |
| CN203132224U (en) | Air conditioner | |
| CN104949409B (en) | A kind of flexible air source heat pump defrosting system and method that need not start compressor | |
| CN110319617B (en) | Gas heat pump device based on heat source tower | |
| CN102798214A (en) | Air source heat pump water heater unit with phase change heat accumulation | |
| JP2002228258A (en) | Heat pump water heater | |
| CN107917562A (en) | Hot gas and electric heating mixing defrosting system and method for low-temperature air-cooling refrigeration system | |
| CN106322595A (en) | Refrigeration and dehumidification system, refrigeration and dehumidification method and refrigeration and dehumidification air conditioner for data centres | |
| CN107110544A (en) | Heat storage type air conditioner | |
| CN104075486A (en) | Apparatus for dual heat pump | |
| CN109203912A (en) | A kind of air-conditioning system and its control method and pure electric vehicle Cold Chain Logistics vehicle | |
| CN104990295B (en) | Air conditioner controlling device, air conditioner and air-conditioner control method | |
| KR101593481B1 (en) | Economic cooling system utilzing free cooling and refrigerating cycle | |
| CN206145903U (en) | Air -conditioning device | |
| KR20130087219A (en) | Heat pump system with effective defrosting circuit using hot gas bypass method | |
| KR20100064751A (en) | Heat pump system of two step compression type | |
| KR100816450B1 (en) | Air conditioning method and system using brine heat exchanger | |
| KR100698578B1 (en) | Hot water generating apparatus using heat pump | |
| JP2012251667A (en) | Defrosting method and defrosting device of air refrigerant type freezing apparatus | |
| CN208983653U (en) | A kind of multifunction refrigeration system | |
| CN203489560U (en) | Dual-system heat pump defroster | |
| CN210004618U (en) | evaporative cold space energy double-source heat pump heat recovery unit | |
| KR20030082822A (en) | The Combined Cooling and Heating Ice Regenerative System | |
| KR100345579B1 (en) | The combined Compact Refrigerative / Regenerative Heat-Pump System |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20180223 Termination date: 20191125 |