CN202382495U - Heat storage phase change defrosting device - Google Patents
Heat storage phase change defrosting device Download PDFInfo
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- CN202382495U CN202382495U CN2011205552734U CN201120555273U CN202382495U CN 202382495 U CN202382495 U CN 202382495U CN 2011205552734 U CN2011205552734 U CN 2011205552734U CN 201120555273 U CN201120555273 U CN 201120555273U CN 202382495 U CN202382495 U CN 202382495U
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Abstract
The utility model provides a heat accumulation phase transition defroster, include: the heat storage phase change device is arranged on the refrigerant circulation pipeline, and further comprises a defrosting pipeline which is led out by the compressor, is converged with a heat supply pipeline sequentially passing through the four-way valve and the indoor heat exchanger through the outdoor heat exchanger, and returns to the compressor through the heat storage phase change device to form circulation. And a heat storage phase change defrosting apparatus comprising: the heat storage phase change device is arranged on the refrigerant circulating pipeline and can be respectively connected in series between the indoor heat exchanger and the outdoor heat exchanger and between the outdoor heat exchanger and the four-way valve and the compressor in an on-off mode. The utility model discloses use parallel heat supply pipeline and defrosting pipeline, do not influence the performance of former system, utilize the compressor waste heat, can make the defrosting time reduce greatly and continue to indoor heat supply.
Description
Technical field
The utility model relates to the defroster field, particularly a kind of accumulation of heat phase transformation defroster.
Background technology
The domestic Defrost mode that heat pump air conditioner and water heater adopted mostly is to utilize the delivery temperature of compressor to carry out the hot gas defrosting at present.Concrete defrost process is: get into defrosting mode-compressor to stop-cross valve switching-over-compressor start-hot gas defrosting-compressor stops-the cross valve switching-over-compressor start-end of spreading unfounded rumours-defrost.
The following weak point that prior art exists:
1, a defrost periods needs start and stop compressor 2 times, and it is high to start energy consumption, and electrical network is had bigger impact, and start and stop frequently reduce the life-span of compressor greatly;
2, a defrost periods cross valve commutates 2 times, and the slide block of inside easy to wear causes cross valve commutation failure rate to raise, the life-span of reduction cross valve;
3, the start and stop of cross valve switching-over and compressor need spend about 4 minutes, and whole defrost process need spend about 12 minutes, need the cost longer time under the adverse circumstances;
4, indoorly during defrost do not heat, also need put a period of time cold wind after defrost finishes could normally heat, and has a strong impact on indoor comfort;
5, defrost only relies on compressor air-discharging to carry out the hot gas defrosting, and energy source is in compressor work, and the highest the highest operate power that can only reach compressor of the energy that is used to defrost causes defrost time length or defrost unclean under the adverse circumstances;
6, wall and external environment are carried out heat exchange during compressor operating, and distribute heat causes delivery temperature to descend to some extent, wastes energy.
External some technology at present adopts the thermal storage defrosting mode.This method is to utilize when normally heating regenerative apparatus to draw and the heat radiation of store compressed machine, derives the heat in the regenerative apparatus during defrosting to be used for defrosting and heat supply again.Cross valve need not commutate during the defrosting of this Defrost mode, compressor do not quit work, and can partly solve the deficiency that above-mentioned domestic prior art exists.
But also there is weak point in this Defrost mode:
Cold-producing medium does not pass through throttling and evaporation when 1, defrosting, and does not have complete kind of refrigeration cycle, can not bring into play the effect that energy is carried in the cold-producing medium phase transformation.
2, cold-producing medium is flowed through becomes supercooled state behind the outdoor heat exchanger, becomes superheated steam behind the regenerative apparatus of flowing through, and it is bigger that both mix the back energy loss.
3, flow through and to be wet-steam phase after the refrigerant mixed of outdoor heat exchanger and storage heater, cause the compressor Wet Compression after getting into compressor, seriously shorten the service life of compressor, also can cause the strong vibrations of outer machine.
4, heat-storing material does not undergo phase transition, and heat storage capacity is relatively poor.Heat-storing material is in a liquid state, and is prone to take place to leak and volatilization.
5, the heat exchanger tube in the storage heater is the snakelike shape of level, is difficult for bending.And its copper pipe is a light pipe, and exchange capability of heat is poor.
6, refrigerant gets into from the condenser bottom during defrost, and by the upwards defrost of condenser bottom, the water that frost is melted into flows down the heat of taking away the bottom from top, be unfavorable for defrost.
The utility model content
The utility model provides a kind of accumulation of heat phase transformation defroster, and the used heat that has utilized compressor to produce overcomes hot gas defrosting device of the prior art and reduces component life, wastes energy, and can not continue technical problems such as heat supply; And solve technical problems such as power consumption that existing phase transformation defroster refrigerant mixed causes and vibration.
The utility model is realized through following technical scheme: a kind of accumulation of heat phase transformation defroster; Comprise: be arranged on the accumulation of heat phase change device on the medium circulation pipeline, also comprise defroster duct; Draw by compressor; Through outdoor heat exchanger, converge with the heat supplying pipeline of order through cross valve and indoor heat exchanger, get back to compressor through the accumulation of heat phase change device again and form circulation.
Further; Defroster duct is drawn from compressor; Through the first magnetic valve communication chamber external heat exchanger; Be communicated with through electric expansion valve between indoor heat exchanger and the outdoor heat exchanger, between indoor heat exchanger on the heat supplying pipeline and accumulation of heat phase change device, be provided with second magnetic valve, be provided with the 3rd magnetic valve between cross valve and the compressor.
Further; Defroster duct is drawn from compressor; Through the first magnetic valve communication chamber external heat exchanger; Be communicated with through electric expansion valve between indoor heat exchanger and the outdoor heat exchanger, between outdoor heat exchanger and accumulation of heat phase change device, be provided with second magnetic valve, be provided with the 3rd magnetic valve between cross valve and the compressor.
Further, defroster duct is drawn from compressor, and through triple valve communication chamber external heat exchanger, cross valve is communicated with triple valve, between outdoor heat exchanger and accumulation of heat phase change device, is provided with second magnetic valve.
Further, but the accumulation of heat phase change device be connected on to break-make between indoor heat exchanger and the outdoor heat exchanger and between outdoor heat exchanger and the cross valve respectively.
Further, through throttling arrangement, throttling arrangement is capillary or electric expansion valve to defroster duct before getting into the accumulation of heat phase change device.
Further, the accumulation of heat phase change device comprises heat storage tank, heat-storing material and heat exchanger, and heat-storing material is seated in the heat storage tank, is equipped with heat exchanger in the heat-storing material of heat storage tank, and medium circulation pipeline is passed heat exchanger.
Further, heat storage tank is close to compressor, and fills heat conductive silica gel between the compressor.
Further, heat exchanger is taked any in the following form: bending light pipe or screwed tube heat exchanger, the finned tube parallel connection of U type or heat exchangers in series and micro-channel heat exchanger.
Further, heat-storing material is polyethylene glycol solid-liquid phase change material or paraffin, expanded graphite solid-solid phase change composite.
According to the utility model on the other hand; A kind of accumulation of heat phase transformation defroster is provided; Comprise: be arranged on the accumulation of heat phase change device on the medium circulation pipeline, but the accumulation of heat phase change device is connected on break-make respectively between indoor heat exchanger and the outdoor heat exchanger and between outdoor heat exchanger and cross valve and the compressor.
Pass through technique scheme; The major advantage of the utility model is, the utility model uses parallel heat supplying pipeline and defroster duct, do not influence the performance of original system and defrosting time is reduced greatly and continues to indoor heating; Utilize heat of compressor simultaneously, energy savings.
Description of drawings
The accompanying drawing that constitutes the part of the utility model is used to provide the further understanding to the utility model, and illustrative examples of the utility model and explanation thereof are used to explain the utility model, do not constitute the improper qualification to the utility model.In the accompanying drawings:
Fig. 1 a shows the pipeline of accumulation of heat phase transformation defroster of first embodiment that comprises the utility model at the sketch map of refrigeration mode;
Fig. 1 b shows the pipeline of accumulation of heat phase transformation defroster of first embodiment that comprises the utility model at the sketch map of heating mode;
Fig. 1 c shows the pipeline of accumulation of heat phase transformation defroster of first embodiment that comprises the utility model at the sketch map of heat supply defrosting mode;
Fig. 1 d shows the pipeline of accumulation of heat phase transformation defroster of first embodiment that comprises the utility model at the sketch map of quickly defrosting pattern;
Fig. 2 a shows the pipeline of accumulation of heat phase transformation defroster of second embodiment that comprises the utility model at the sketch map of refrigeration mode;
Fig. 2 b shows the pipeline of accumulation of heat phase transformation defroster of second embodiment that comprises the utility model at the sketch map of heating mode;
Fig. 2 c shows the pipeline of accumulation of heat phase transformation defroster of second embodiment that comprises the utility model at the sketch map of heat supply defrosting mode;
Fig. 3 a shows the pipeline of accumulation of heat phase transformation defroster of the 3rd embodiment that comprises the utility model at the sketch map of refrigeration mode;
Fig. 3 b shows the pipeline of accumulation of heat phase transformation defroster of the 3rd embodiment that comprises the utility model at the sketch map of heating mode;
Fig. 3 c shows the pipeline of accumulation of heat phase transformation defroster of the 3rd embodiment that comprises the utility model at the sketch map of heat supply defrosting mode;
Fig. 3 d shows the pipeline of accumulation of heat phase transformation defroster of the 3rd embodiment that comprises the utility model at the sketch map of quickly defrosting pattern;
Fig. 4 a shows the pipeline of accumulation of heat phase transformation defroster of the 4th embodiment that comprises the utility model at the sketch map of refrigeration mode;
Fig. 4 b shows the pipeline of accumulation of heat phase transformation defroster of the 4th embodiment that comprises the utility model at the sketch map of heating mode;
Fig. 4 c shows the pipeline of accumulation of heat phase transformation defroster of the 4th embodiment that comprises the utility model at the sketch map of heat supply defrosting mode; And
Fig. 4 d shows the pipeline of accumulation of heat phase transformation defroster of the 4th embodiment that comprises the utility model at the sketch map of quickly defrosting pattern.
The specific embodiment
Embodiment to the utility model is elaborated below in conjunction with accompanying drawing, but the multitude of different ways that the utility model can be defined by the claims and cover is implemented.
Refrigeration system pipeline flow process with the utility model is improved on common refrigeration system basis, adds magnetic valve and regenerative apparatus and pipeline thereof.Normal cooling and warming circulation does not have difference with usual used cooling and warming circulation.The system pipeline of the utility model has four kinds of working methods, is respectively: refrigeration mode, heating mode, heat supply defrosting mode, quickly defrosting pattern.In the following respective drawings that specifies, mark the refrigerant flow path with triangle.
First embodiment:
Refrigeration mode: shown in Fig. 1 a; First magnetic valve 81 and second magnetic valve 82 are closed, the 3rd magnetic valve 83 is opened, cross valve 20 outages, accomplish process of refrigerastion thereby get into indoor heat exchanger 50 evaporation heat absorptions through electric expansion valve 40 throttlings after HTHP gaseous coolant inlet chamber external heat exchanger 30 condensations that compressor 10 is discharged.
Heating mode: shown in Fig. 1 b; First magnetic valve 81 and second magnetic valve 82 are closed, the 3rd magnetic valve 83 is opened, cross valve 20 energisings; The HTHP gaseous coolant that compressor 10 is discharged evaporates heat absorption through electric expansion valve 40 throttling inlet chamber external heat exchangers 30 after getting into indoor heat exchanger 50 condensation heat releases, accomplishes the process that heats.
The heat supply defrosting mode: shown in Fig. 1 c, first magnetic valve 81 and second magnetic valve 82 are opened, the 3rd magnetic valve 83 cuts out, electric expansion valve 40 is closed, cross valve 20 energisings.The HTHP gaseous coolant of being discharged by compressor 10 divides two-way, and one the tunnel flows into from outdoor heat exchanger 30 bottoms via first magnetic valve 81 and to be used for defrost, and another road gets into indoor heat exchangers 50 via cross valve 20 and is used for heat supply.The two-way refrigerant converges after the heat that entering regenerative apparatus 70 absorption regenerative apparatuses 70 store after capillary 60 throttlings offers outdoor heat exchanger 30 defrosting and indoor heat exchanger 50 heat supplies.Converting heat supply defrosting mode cross valve 20 into by heating mode does not need switching-over, and compressor 10 does not need start and stop yet.
The quickly defrosting pattern: shown in Fig. 1 d, first magnetic valve 81 is opened, second magnetic valve 82 and the 3rd magnetic valve 83 cuts out, 20 energisings of electric expansion valve 40 full cut-offs, cross valve.The HTHP gaseous coolant that compressor 10 is discharged is used for defrosting via the 81 whole inlet chamber external heat exchanger 30 condensation heat releases of first magnetic valve and accomplishes quickly defrosting after get back to compressor 10 by the heat that stores in the capillary 60 throttlings entering regenerative apparatus 70 evaporation absorption regenerative apparatuses 70.The heat that stores in 10 works of this pattern lower compression machine and the regenerative apparatus 70 is used for defrosting entirely, and converts quickly defrosting pattern cross valve 20 into by heating mode and do not need switching-over, compressor 10 not to need start and stop, shortens defrosting time greatly.
The advantage of the scheme of first embodiment is can close the 3rd magnetic valve return-air is heated with raising through regenerative apparatus and the suction and discharge temperature when defrosting.Its shortcoming also clearly from the beginning of condenser bottom, has adverse effect to defrosting during defrosting, uses three magnetic valves, and the high control of cost is complicated.
Second embodiment:
Refrigeration mode: shown in Fig. 2 a, first magnetic valve 81 and second magnetic valve 82 are opened, cross valve 20 outages.Evaporate the process cross valve 20 that absorbs heat again through second magnetic valve 82 through electric expansion valve 40 throttlings entering evaporimeter 50 after the HTHP gaseous coolant process cross valve 20 of compressor 10 discharges and the 30 condensation heat releases of first magnetic valve, 81 entering condensers and get back to compressor 10 completion process of refrigerastions.
Heating mode: shown in Fig. 2 b, first magnetic valve 81 and second magnetic valve 82 are opened, cross valve 20 energisings.The HTHP gaseous coolant that compressor 10 is discharged gets into evaporimeter 50 condensation heat releases through cross valve 20 and accomplishes the process that heats after electric expansion valve 40 throttlings are got back to compressor 10 through first magnetic valve 81 and cross valve 20 again through the 30 evaporation heat absorptions of second magnetic valve, 82 entering condensers.
The heat supply defrosting mode: shown in Fig. 2 c, first magnetic valve 81 and second magnetic valve 82 are closed, cross valve 20 energisings.The HTHP gaseous coolant that compressor 10 is discharged gets into evaporimeter 50 condensation heat releases through cross valve 20 after electric expansion valve 40 throttlings get into storage heater 70 evaporations draws heat in the regenerative apparatuses 70 and flow into condenser 30 then and be used for defrost, and the supercooled liquid refrigerant that comes out from condenser 30 flows into the evaporation heat absorption of damming of regenerative apparatus 70 secondaries once more and gets back to compressor 10 and accomplish the heat supplies defrosting.
The scheme of this embodiment does not have the quickly defrosting pattern, can reduce electric expansion valve of use but compare first embodiment, can also substitute first magnetic valve with check valve and can reach normal cooling and warming and heat supply defrosting equally.Can improve simultaneously and heat and the suction and discharge temperature when defrosting, make to heat and defrosting reaches better effect.The shortcoming of second embodiment is to need second throttle, and the pressure of system is not easy control.Have partial discharge when freezing simultaneously and flow into storage heater, influential slightly to system's refrigeration.
The 3rd embodiment:
Refrigeration mode: shown in Fig. 3 a; First magnetic valve 81 and second magnetic valve 82 are closed, the 3rd magnetic valve 83 is opened, cross valve 20 outages, accomplish process of refrigerastion thereby get into indoor heat exchanger 50 evaporation heat absorptions through electric expansion valve 40 throttlings after high temperature and high pressure gas inlet chamber external heat exchanger 30 condensations that compressor 10 is discharged.There is not refrigerant to flow the not too large refrigeration that influences under the refrigeration mode in the regenerative apparatus 70.
Heating mode: shown in Fig. 3 b; First magnetic valve 81 and second magnetic valve 82 are closed, the 3rd magnetic valve 83 is opened, cross valve 20 energisings; The HTHP gaseous coolant that compressor is discharged evaporates heat absorption through electric expansion valve 40 throttling inlet chamber external heat exchangers 30 after getting into indoor heat exchanger 50 condensation heat releases, accomplishes the process that heats.Do not have refrigerant to flow under the heating mode in the regenerative apparatus, can not take away the heat in the regenerative apparatus, make the interior heat of regenerative apparatus be able to store and be used for defrosting, can too much influence not arranged yet heating effect.
The heat supply defrosting mode: shown in Fig. 3 c, first magnetic valve 81 and second magnetic valve 82 are opened, the 3rd magnetic valve 83 cuts out, 20 energisings of electric expansion valve 40 standard-sized sheets, cross valve.The HTHP gaseous coolant of being discharged by compressor 10 divides two-way, and one the tunnel flows into from outdoor heat exchanger 30 tops via first magnetic valve 81 and to be used for defrost, and another road gets into indoor heat exchangers 50 via cross valve 20 and is used for heat supply.The two-way refrigerant converges after the heat that entering regenerative apparatus 70 absorption regenerative apparatuses store after second magnetic valve 82 and capillary 60 throttlings offers outdoor heat exchanger 30 defrosting and indoor heat exchanger 50 heat supplies.Converting heat supply defrosting mode cross valve into by heating mode does not need switching-over, and compressor does not need start and stop yet.
The quickly defrosting pattern: shown in Fig. 3 d, first magnetic valve 81 and second magnetic valve 82 are opened, the 3rd magnetic valve 83 cuts out, 20 energisings of electric expansion valve 40 full cut-offs, cross valve.The HTHP gaseous coolant that compressor 10 is discharged is used for defrosting via the 81 whole inlet chamber external heat exchanger 30 condensation heat releases of first magnetic valve and gets back to compressor 10 completion quickly defrostings after get into the heat that stores in the regenerative apparatus 70 evaporation absorption regenerative apparatuses 70 by second magnetic valve 82 and capillary 60 throttlings.The heat that stores in 10 works of this pattern lower compression machine and the regenerative apparatus 70 is used for defrosting entirely, and converts quickly defrosting pattern cross valve into by heating mode and do not need switching-over, compressor not to need start and stop, shortens defrosting time greatly.
The 3rd embodiment than the first and second embodiment biggest advantage is, begin to be beneficial to defrosting during defrosting from condenser top mobile with refrigerant, during defrosting cross valve do not commutate, not start and stop of compressor, shorten defrosting time greatly.Heat supply when defrosting can be through regulating electric expansion valve aperture adjustment condenser and evaporimeter in the flow proportional of refrigerant, do not have flow to flow through the accumulation of heat that regenerative apparatus is beneficial to regenerative apparatus during cooling and warming normally.Can rely on oneself alternative wherein two magnetic valves of two-port valve perhaps with alternative three magnetic valves of two six-way valves with two pressure reduction.
The 4th embodiment:
This scheme is a preferred version.Three-way solenoid valve 90 outage default locations are: outdoor heat exchanger 30 links to each other with cross valve 20.Energising back outdoor heat exchanger 30 links to each other with compressor 10 exhausts.
Refrigeration mode: shown in Fig. 4 a; Three-way solenoid valve 90 outages, magnetic valve 80 are closed, cross valve 20 outages, accomplish process of refrigerastion thereby get into indoor heat exchanger 50 evaporation heat absorptions through electric expansion valve 40 throttlings after high temperature and high pressure gas inlet chamber external heat exchanger 30 condensations that compressor 10 is discharged.There is not refrigerant to flow the not too large refrigeration that influences under the refrigeration mode in the regenerative apparatus 70.
Heating mode: shown in Fig. 4 b; Three-way solenoid valve 90 outages, magnetic valve 80 are closed, cross valve 20 energisings; The HTHP gaseous coolant that compressor 10 is discharged evaporates heat absorption through electronic expansion 40 valve throttling inlet chamber external heat exchangers 30 after getting into indoor heat exchanger 50 condensation heat releases, accomplishes the process that heats.Do not have refrigerant to flow under the heating mode in the regenerative apparatus 70, can not take away the heat in the regenerative apparatus, make the interior heat of regenerative apparatus be able to store and be used for defrosting, can too much influence not arranged yet heating effect.
The heat supply defrosting mode: shown in Fig. 4 c, three-way solenoid valve 90 energising, magnetic valve 80 are opened, electric expansion valve 40 standard-sized sheets, cross valve 20 energisings.The HTHP gaseous coolant of being discharged by compressor 10 divides two-way, and one the tunnel flows into from outdoor heat exchanger 30 tops via three-way solenoid valve 90 and to be used for defrost, and another road gets into indoor heat exchangers 50 via cross valve 20 and is used for heat supply.The two-way refrigerant converges after the heat that entering regenerative apparatus 70 absorption regenerative apparatuses 70 store after magnetic valve 80 and capillary 60 throttlings offers outdoor heat exchanger 30 defrosting and indoor heat exchanger 50 heat supplies.Converting heat supply defrosting mode cross valve into by heating mode does not need switching-over, and compressor does not need start and stop yet.
The quickly defrosting pattern: shown in Fig. 4 d, three-way solenoid valve 90 energising, magnetic valve 80 are opened, electric expansion valve 40 full cut-offs, cross valve 20 energisings.The HTHP gaseous coolant that compressor 10 is discharged is used for defrosting via the whole inlet chamber external heat exchanger 50 condensation heat releases of three-way solenoid valve and gets back to compressor completion quickly defrosting after get into the heat that stores in the regenerative apparatus 70 evaporation absorption regenerative apparatuses 70 by magnetic valve 80 and capillary 60 throttlings.The heat that stores in 10 works of this pattern lower compression machine and the regenerative apparatus 70 is used for defrosting entirely, and converts quickly defrosting pattern cross valve into by heating mode and do not need switching-over, compressor not to need start and stop, shortens defrosting time greatly.
The 4th embodiment has inherited the advantage of the 3rd embodiment scheme: begin to be beneficial to defrosting during defrosting from condenser top mobile with refrigerant, during defrosting cross valve do not commutate, not start and stop of compressor, shorten defrosting time greatly.Heat supply when defrosting can be through regulating electric expansion valve aperture adjustment condenser and evaporimeter in the flow proportional of refrigerant, do not have flow to flow through the accumulation of heat that regenerative apparatus is beneficial to regenerative apparatus during cooling and warming normally.
Preferably, among the 4th embodiment, substitute two magnetic valves, promptly simplified control and reduced cost again with a three-way solenoid valve.Can also use a two-position five-way to substitute three-way solenoid valve and magnetic valve equally.
The magnetic valve that has certain throttling after capillary in all above schemes and the magnetic valve before the stream thereof all can adopt normally closed no flow, energising to open substitutes, and can simplify pipeline.
The accumulation of heat phase change device of the utility model comprises heat storage tank, heat-storing material, regenerative apparatus heat exchanger and attached pipeline and valve member thereof.
Heat storage tank: the arc-shaped slot shape, be close to the compressor outer wall, and solid with the band binding.Available engineering plastics or panel beating casting, heat conduction is good.Seal cover is arranged, good seal, carrying liquid does not leak.Heat storage tank and compressor chamber are filled to strengthen heat conduction with heat conductive silica gel.
Heat-storing material: adopt polyethylene glycol solid-liquid phase change material or paraffin, expanded graphite solid-solid phase change composite; Be filled in the heat storage tank; The heat radiation that when the compressor operate as normal, absorbs compressor undergoes phase transition, and when needs are used for defrosting and heat supply, undergoes phase transition and emits heat.
The regenerative apparatus heat exchanger can have following form: 1, snakelike bending light pipe or screwed pipe, adopt the radius bend lengthening total length of trying one's best little to strengthen heat exchange; 2, also compacting paraffin, expanded graphite composite are filled in the many parallelly connected or series connection of U type finned tube between fin; 3, small micro channel heat exchanger is filled also compacting paraffin, expanded graphite composite between the microchannel.
Pipeline and valve element design: the high temperature and high pressure gas that compressor is discharged divides two-way, and one the tunnel through the heat supply of cross valve entering indoor heat exchanger, and another road is through the defrost from top to bottom of magnetic valve inlet chamber external heat exchanger.The heat exchange of two-way refrigerant finishes and is supercooled liquid and converges through getting into the heat that the regenerative apparatus evaporation draws in the regenerative apparatus behind the capillary-compensated and become superheated steam.
According to the utility model, have following beneficial effect:
The defrost process cross valve is switching-over not, normal cooling and warming circulation and usual used cooling and warming circulation basically identical.Use the utility model not influence the performance of original system and defrosting time was reduced to 5 minutes greatly and continues to indoor heating.
The preferred embodiment that the above is merely the utility model is not limited to the utility model, and for a person skilled in the art, the utility model can have various changes and variation.All within the spirit and principle of the utility model, any modification of being done, be equal to replacement, improvement etc., all should be included within the protection domain of the utility model.
Claims (10)
1. accumulation of heat phase transformation defroster comprises: be arranged on the accumulation of heat phase change device (70) on the medium circulation pipeline,
It is characterized in that, also comprise,
Defroster duct is drawn by compressor (10), through outdoor heat exchanger (30), converges with the heat supplying pipeline of order through cross valve (20) and indoor heat exchanger (50), gets back to said compressor (10) through said accumulation of heat phase change device (70) again and forms circulation.
2. accumulation of heat phase transformation defroster according to claim 1; It is characterized in that; Said defroster duct is drawn from said compressor (10); Be communicated with said outdoor heat exchanger (30) through first magnetic valve (81), between the above indoor heat exchanger of said heat supplying pipeline (50) and said accumulation of heat phase change device (70), be provided with second magnetic valve, be provided with the 3rd magnetic valve (83) between said cross valve (20) and the said compressor (10).
3. accumulation of heat phase transformation defroster according to claim 1; It is characterized in that; Said defroster duct is drawn from compressor (10); Through first magnetic valve (81) communication chamber external heat exchanger (30), between said outdoor heat exchanger (30) and said accumulation of heat phase change device (70), be provided with second magnetic valve (82), be provided with the 3rd magnetic valve (83) between said cross valve (20) and the said compressor (10).
4. accumulation of heat phase transformation defroster according to claim 1; It is characterized in that; Said defroster duct is drawn from compressor (10); Be communicated with said outdoor heat exchanger (30) through triple valve (90), said cross valve (20) also is communicated with said triple valve (90), between said outdoor heat exchanger (50) and said accumulation of heat phase change device (70), is provided with magnetic valve (80).
5. accumulation of heat phase transformation defroster according to claim 1 is characterized in that, said defroster duct passes through throttling arrangement before at the said accumulation of heat phase change device of entering (70), and said throttling arrangement is capillary (60) or electric expansion valve.
6. accumulation of heat phase transformation defroster according to claim 1; It is characterized in that; Said accumulation of heat phase change device (70) comprises heat storage tank, heat-storing material and heat exchanger; Said heat-storing material is seated in the said heat storage tank, is equipped with heat exchanger in the heat-storing material of said heat storage tank, and said medium circulation pipeline is passed said heat exchanger.
7. accumulation of heat phase transformation defroster according to claim 6 is characterized in that said heat storage tank is close to said compressor (10), and fills heat conductive silica gel between the said compressor (10).
8. accumulation of heat phase transformation defroster according to claim 6 is characterized in that said heat exchanger is taked any in the following form: heat exchanger, micro-channel heat exchanger that bending light pipe or screwed tube heat exchanger, the parallel connection of U type finned tube or series connection form.
9. accumulation of heat phase transformation defroster according to claim 6 is characterized in that, said heat-storing material is polyethylene glycol solid-liquid phase change material or paraffin, expanded graphite solid-solid phase change composite.
10. accumulation of heat phase transformation defroster; Comprise: be arranged on the accumulation of heat phase change device (70) on the medium circulation pipeline; It is characterized in that, said accumulation of heat phase change device (70) but be connected on to break-make between indoor heat exchanger (50) and the outdoor heat exchanger (30) respectively and said outdoor heat exchanger (50) and cross valve (20) and compressor (10) between.
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| CN2011205552734U CN202382495U (en) | 2011-12-26 | 2011-12-26 | Heat storage phase change defrosting device |
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| CN2011205552734U CN202382495U (en) | 2011-12-26 | 2011-12-26 | Heat storage phase change defrosting device |
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| CN202382495U true CN202382495U (en) | 2012-08-15 |
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Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN102829589A (en) * | 2012-09-21 | 2012-12-19 | 青岛海尔空调电子有限公司 | Air conditioning system with defroster and central air conditioning hot water system |
| CN103175354A (en) * | 2011-12-26 | 2013-06-26 | 珠海格力电器股份有限公司 | Heat storage phase change defrosting device |
| CN104236177A (en) * | 2013-06-20 | 2014-12-24 | 青岛海尔空调电子有限公司 | Phase-change heat storage and coolant supercooling heat exchanger and air conditioning system with same |
| CN104251580A (en) * | 2013-06-26 | 2014-12-31 | 珠海格力电器股份有限公司 | Air conditioning system |
| CN104390400A (en) * | 2014-10-20 | 2015-03-04 | 苏州大美节能科技有限公司 | Heat pump product with novel defrosting heat exchange device |
| CN104633836A (en) * | 2013-11-14 | 2015-05-20 | 珠海格力电器股份有限公司 | Defrosting control method for air conditioner |
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- 2011-12-26 CN CN2011205552734U patent/CN202382495U/en not_active Expired - Lifetime
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| CN103175354A (en) * | 2011-12-26 | 2013-06-26 | 珠海格力电器股份有限公司 | Heat storage phase change defrosting device |
| CN103175354B (en) * | 2011-12-26 | 2016-03-02 | 珠海格力电器股份有限公司 | Heat storage phase change defrosting device |
| CN102829589A (en) * | 2012-09-21 | 2012-12-19 | 青岛海尔空调电子有限公司 | Air conditioning system with defroster and central air conditioning hot water system |
| CN102829589B (en) * | 2012-09-21 | 2015-06-03 | 青岛海尔空调电子有限公司 | Air conditioning system with defroster and central air conditioning hot water system |
| CN104236177A (en) * | 2013-06-20 | 2014-12-24 | 青岛海尔空调电子有限公司 | Phase-change heat storage and coolant supercooling heat exchanger and air conditioning system with same |
| CN104236177B (en) * | 2013-06-20 | 2017-03-01 | 青岛海尔空调电子有限公司 | A kind of phase-transition heat-storage, coolant are crossed cold-heat-exchanging exchange system and are adopted its air conditioning system |
| CN104251580A (en) * | 2013-06-26 | 2014-12-31 | 珠海格力电器股份有限公司 | Air conditioning system |
| CN104633836A (en) * | 2013-11-14 | 2015-05-20 | 珠海格力电器股份有限公司 | Defrosting control method for air conditioner |
| CN104633836B (en) * | 2013-11-14 | 2017-05-31 | 珠海格力电器股份有限公司 | Defrosting control method for air conditioner |
| CN104390400A (en) * | 2014-10-20 | 2015-03-04 | 苏州大美节能科技有限公司 | Heat pump product with novel defrosting heat exchange device |
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