CN104848579A - Air conditioner and heat exchanging system thereof - Google Patents
Air conditioner and heat exchanging system thereof Download PDFInfo
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- CN104848579A CN104848579A CN201510224980.8A CN201510224980A CN104848579A CN 104848579 A CN104848579 A CN 104848579A CN 201510224980 A CN201510224980 A CN 201510224980A CN 104848579 A CN104848579 A CN 104848579A
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- heat exchanger
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- 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
- F25B13/00—Compression machines, plants or systems, with reversible cycle
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- 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
- F25B40/00—Subcoolers, desuperheaters or superheaters
- F25B40/02—Subcoolers
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- 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
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- Engineering & Computer Science (AREA)
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- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
Abstract
The invention discloses an air conditioner and a heat exchanging system thereof. By adding an outdoor supercooling device and an indoor supercooling device that are respectively corresponding to an indoor heat exchanger and an outdoor heat exchanger, a refrigerant from the outdoor exchanger is introduced into the outdoor supercooling device again for exchanging heat in a refrigeration mode, so as to increase the refrigerant supercooling degree flowing out from the outdoor heat exchanger, thereby increasing the refrigeration ability and the energy efficiency ratio; a refrigerant from the indoor heat exchanger is introduced into the indoor supercooling device again for exchanging the heat in a heating mode, so as to increase the refrigerant supercooling degree flowing out from the indoor heat exchanger, thereby increasing the heating ability and the performance coefficient. Therefore, a supercooling flow passage for increasing the refrigerant supercooling degree is respectively formed in the refrigeration mode and the heating model, accordingly allowing both the outdoor heat exchanger and the indoor heat exchanger to be utilized as much as possible, thereby increasing the refrigeration and heating abilities as well as the energy efficiency ratio of the entire air conditioner greatly.
Description
Technical field
The present invention relates to refrigeration technology field, particularly relate to a kind of air-conditioner and heat-exchange system thereof.
Background technology
Along with the development of air conditioner energy-saving technology, the optimum choice of the refrigerant flow of indoor and outdoor heat exchanger is never stopped.But, current line refrigerant flow mostly in the industry is fixed form, namely under refrigeration mode with heating mode, refrigerant flow is identical, and according to this fixed refrigerant flow, then under refrigeration mode and heating mode, indoor and outdoor heat exchanger is difficult to be fully used, easily occur that refrigerating capacity is excellent, and heating capacity is bad, or occur that refrigerating capacity is bad, the problem that heating capacity is excellent, refrigeration efficiency ratio and coefficient of performance in heating are difficult to reach optimum simultaneously, can not improve the integral working of air-conditioner.
Summary of the invention
Main purpose of the present invention is to provide a kind of heat-exchange system, is intended to solve the technical problem that existing refrigerant flow can not improve the integral working of air-conditioner.
For achieving the above object, the invention provides a kind of heat-exchange system, comprise the compressor that head and the tail connect to form refrigerant circulation circuit successively, reversing arrangement, outdoor heat exchanger, throttling arrangement and indoor heat exchanger, in described refrigerant circulation circuit between described outdoor heat exchanger and described indoor heat exchanger and with described compressor, the corresponding pipeline of reversing arrangement is the first pipeline, in described refrigerant circulation circuit between described outdoor heat exchanger with described indoor heat exchanger and the pipeline corresponding with described throttling arrangement is the second pipeline, described heat-exchange system also comprises the outdoor supercooling apparatus and indoor supercooling apparatus that are arranged in parallel with described second pipeline respectively, described outdoor supercooling apparatus is between described outdoor heat exchanger and described throttling arrangement, described indoor supercooling apparatus is between described indoor heat exchanger and described throttling arrangement, described second pipeline is provided with and is connected in parallel the first outdoor control valve between node at two of described outdoor supercooling apparatus, crossing on cold flow road of described outdoor supercooling apparatus is provided with the second outdoor control valve, described second pipeline is provided with and is connected in parallel the first indoor control valve between node at two of described indoor supercooling apparatus, crossing on cold flow road of described indoor supercooling apparatus is provided with the second indoor control valve.
Preferably, described outdoor heat exchanger comprises the refrigerant flow that multi-channel parallel is arranged, the cold flow road of crossing of described outdoor supercooling apparatus comprises the first outdoor branch road and the second outdoor branch road that are arranged in parallel, any refrigerant flow in described outdoor heat exchanger forms described first outdoor branch road, described first outdoor branch road is provided with the 3rd outdoor control valve between itself and the refrigerant distribution node being connected in parallel node and described outdoor heat exchanger of described second outdoor branch road, described second outdoor control valve is positioned on described second outdoor branch road.
Preferably, described outdoor heat exchanger also comprises the first outdoor three-way pipe and the second outdoor three-way pipe, one end of described second outdoor branch road is connected with described first outdoor branch road by described first outdoor three-way pipe, and the other end is connected with described second pipeline by described second outdoor three-way pipe.
Preferably, described outdoor heat exchanger also comprises the second coolant distributor that each refrigerant flow of drawing from described outdoor heat exchanger collects by the first coolant distributor and being used for of entering described outdoor heat exchanger for refrigerant being divided into multichannel, described first outdoor control valve is connected in parallel between node and described second coolant distributor described second outdoor branch road and described second pipeline, and described 3rd outdoor control valve is connected in parallel between node and described first coolant distributor described first outdoor branch road and described second outdoor branch road.
Preferably, described first outdoor control valve is check valve or single-pass magnetic valve, and described second outdoor control valve is check valve or single-pass magnetic valve, and described 3rd outdoor control valve is check valve or single-pass magnetic valve.
Preferably, described indoor heat exchanger comprises the refrigerant flow that multi-channel parallel is arranged, the cold flow road of crossing of described indoor supercooling apparatus comprises the first indoor branch road and the second indoor branch road that are arranged in parallel, any refrigerant flow in described indoor heat exchanger forms described first indoor branch road, described first indoor branch road is provided with the 3rd indoor control valve between itself and the refrigerant distribution node being connected in parallel node and described indoor heat exchanger of described second indoor branch road, described second indoor control valve is positioned on described second indoor branch road.
Preferably, described indoor heat exchanger also comprises the first indoor three-way pipe and the second indoor three-way pipe, one end of described second indoor branch road is connected with described first indoor branch road by described first indoor three-way pipe, and the other end is connected with described second pipeline by described second indoor three-way pipe.
Preferably, described indoor heat exchanger also comprises the 4th coolant distributor that each refrigerant flow of drawing from described indoor heat exchanger collects by the 3rd coolant distributor and being used for that enters described indoor heat exchanger for refrigerant being divided into multichannel, described first indoor control valve is connected in parallel between node and described 3rd coolant distributor described second indoor branch road and described second pipeline, and described 3rd indoor control valve is connected in parallel between node and described 4th coolant distributor described first indoor branch road and described second indoor branch road.
Preferably, described first indoor control valve is check valve or single-pass magnetic valve, and described second indoor control valve is check valve or single-pass magnetic valve, and described 3rd indoor control valve is check valve or single-pass magnetic valve.
In addition, for achieving the above object, the present invention also provides a kind of air-conditioner, and described air-conditioner comprises the heat-exchange system described in above-mentioned any one technical scheme.
A kind of heat-exchange system provided by the present invention, by increasing the outdoor supercooling apparatus that arrange corresponding to indoor and outdoor heat exchanger and indoor supercooling apparatus respectively, when refrigeration mode, refrigerant from outdoor heat exchanger is reintroduced back to heat exchange in outdoor supercooling apparatus, to increase the refrigerant degree of supercooling flowed out in heat exchanger outdoor, improve refrigerating capacity and Energy Efficiency Ratio; When heating mode, the refrigerant from indoor heat exchanger is reintroduced back to heat exchange in indoor supercooling apparatus, to increase the refrigerant degree of supercooling flowed out in heat exchanger indoor, improves heating capacity and the coefficient of performance.Therefore, cross cold flow road by forming one when refrigeration mode and heating mode respectively for increasing refrigerant degree of supercooling, thus make outdoor heat exchanger and indoor heat exchanger all can obtain the utilization of maximal efficiency, substantially increase cooling and warming ability and the Energy Efficiency Ratio of complete machine.
Accompanying drawing explanation
Fig. 1 is the structural representation of heat-exchange system first embodiment of the present invention, and wherein this heat-exchange system is in kind of refrigeration cycle state;
Fig. 2 and Fig. 1 is similar, and wherein this heat-exchange system is in and heats recurrent state;
Fig. 3 is the structural representation of heat-exchange system second embodiment of the present invention, and wherein this heat-exchange system is in kind of refrigeration cycle state;
Fig. 4 and Fig. 3 is similar, and wherein this heat-exchange system is in and heats recurrent state.
The realization of the object of the invention, functional characteristics and advantage will in conjunction with the embodiments, are described further see accompanying drawing.
Detailed description of the invention
Should be appreciated that specific embodiment described herein only in order to explain the present invention, be not intended to limit the present invention.
The invention provides a kind of heat-exchange system, see Fig. 1 and Fig. 2, in a first embodiment, this heat-exchange system comprises the compressor 100 that head and the tail connect to form refrigerant circulation circuit successively, reversing arrangement 110, outdoor heat exchanger 120, throttling arrangement 130 and indoor heat exchanger 140, wherein reversing arrangement 110 can be cross valve, by the commutation of reversing arrangement 110, refrigerant is flowed in described refrigerant circulation circuit forward or backwards, thus realize refrigeration and heat-production functions, throttling arrangement 130 can be electric expansion valve, also can be the throttle mechanism such as capillary or choke valve.In the present embodiment, in refrigerant circulation circuit between outdoor heat exchanger 120 with indoor heat exchanger 140 and the pipeline corresponding with compressor 100, reversing arrangement 110 is the first pipeline P1, in refrigerant circulation circuit between outdoor heat exchanger 120 with indoor heat exchanger 140 and the pipeline corresponding with throttling arrangement 130 is the second pipeline P2.
This heat-exchange system also comprises the outdoor supercooling apparatus A and indoor supercooling apparatus B that are arranged in parallel with the second pipeline P2 respectively, wherein outdoor supercooling apparatus A is between outdoor heat exchanger 120 and throttling arrangement 130, and indoor supercooling apparatus B is between indoor heat exchanger 140 and throttling arrangement 130; In addition, the second pipeline P2 is provided with and is connected in parallel the first outdoor control valve 125 between node at two of outdoor supercooling apparatus A, crossing on cold flow road of outdoor supercooling apparatus A is provided with the second outdoor control valve 127; Second pipeline P2 is provided with and is connected in parallel the first indoor control valve 145 between node at two of indoor supercooling apparatus B, crossing on cold flow road of indoor supercooling apparatus B is provided with the second indoor control valve 147.The flow direction of refrigerant can be selected by the first outdoor control valve 125 and the second outdoor control valve 127, selected the flow direction of refrigerant by the first indoor control valve 145 and the second indoor control valve 147.Particularly, this heat-exchange system is when refrigeration mode, first outdoor control valve 125 is closed, second outdoor control valve 127 conducting, therefore the refrigerant from outdoor heat exchanger 120 is reintroduced back to heat exchange in outdoor supercooling apparatus A, to increase the refrigerant degree of supercooling flowed out in heat exchanger 120 outdoor, improve refrigerating capacity and Energy Efficiency Ratio; This heat-exchange system is when heating mode, first indoor control valve 145 is closed, second indoor control valve 147 conducting, therefore the refrigerant from indoor heat exchanger 140 is reintroduced back to heat exchange in indoor supercooling apparatus B, to increase the refrigerant degree of supercooling flowed out in heat exchanger 140 indoor, improve heating capacity and the coefficient of performance.
In addition, heat-exchange system when heating mode, the first outdoor control valve 125 conducting, the second outdoor control valve 127 is closed, and therefore can not change the refrigerant flow of outdoor heat exchanger 120; Heat-exchange system is when refrigeration mode, and the first indoor control valve 145 conducting, the second indoor control 147 is closed, and therefore can not change the refrigerant flow of indoor heat exchanger 140.The each road refrigerant realizing indoor heat exchanger 140 under outdoor heat exchanger 120 and refrigeration mode under heating mode synchronously enters evaporating state, reduces the flow resistance of refrigerant, effectively ensure that evaporation effect.
It should be noted that, outdoor supercooling apparatus A can form a part for outdoor heat exchanger 120, also can independent of outdoor heat exchanger 120.In like manner, indoor supercooling apparatus B can form a part for indoor heat exchanger 140, also can independent of indoor heat exchanger 140.Obviously, refrigeration pipe and the refrigeration part of configuration can be reduced when supercooling apparatus and heat exchanger are combined as a whole, thus improve the utilization rate of existing heat-exchange system building block.
See Fig. 3 and Fig. 4, in the preferred embodiment, outdoor supercooling apparatus A and outdoor heat exchanger 120 are combined as a whole, indoor supercooling apparatus B and indoor heat exchanger 140 are combined as a whole, the object making the refrigerant of outflow have certain degree of supercooling is reached by the refrigerant flow of switching chamber external heat exchanger 120 and indoor heat exchanger 140, and can ensure that each the road refrigerant in heat exchanger synchronously enters evaporating state, thus improve the service behaviour of complete machine.
Particularly, outdoor heat exchanger 120 comprises the refrigerant flow that multi-channel parallel is arranged, the cold flow road of crossing of outdoor supercooling apparatus A comprises the first outdoor branch road 128 and the second outdoor branch road 129 be arranged in parallel, any refrigerant flow in outdoor heat exchanger 120 forms the first outdoor branch road 128, and the 3rd outdoor control valve 122 the first outdoor branch road 128 is provided with between itself and the refrigerant distribution node being connected in parallel node and outdoor heat exchanger 120 of the second outdoor branch road 129, second outdoor control valve 127 is positioned on the second outdoor branch road 129, by closing the first outdoor control valve 125 and the 3rd outdoor control valve 122, and the outdoor control valve 127 of conducting second, can make to be pooled to the first outdoor branch road 128 in all the other refrigerant flows except the first outdoor branch road 128, and reenter outdoor heat exchanger 120 via the second outdoor branch road 129 and carry out secondary heat exchange, refrigerant enters in refrigerant circulation circuit and continues circulation after the certain degree of supercooling of increase thus.
Indoor heat exchanger 140 comprises the refrigerant flow that multi-channel parallel is arranged, the cold flow road of crossing of indoor supercooling apparatus B comprises the first indoor branch road 148 and the second indoor branch road 149 be arranged in parallel, any refrigerant flow in indoor heat exchanger 140 forms the first indoor branch road 148, and the 3rd indoor control valve 142 the first indoor branch road 148 is provided with between itself and the refrigerant distribution node being connected in parallel node and indoor heat exchanger 140 of the second indoor branch road 149, second indoor control valve 147 is positioned on the second indoor branch road 149, by closing the first indoor control valve 145 and the 3rd indoor control valve 142, and the indoor control valve 147 of conducting second, can make to be pooled to the first indoor branch road 148 in all the other refrigerant flows except the first indoor branch road 148, and reenter indoor heat exchanger 140 via the second indoor branch road 149 and carry out secondary heat exchange, refrigerant enters in refrigerant circulation circuit and continues circulation after the certain degree of supercooling of increase thus.
It should be noted that, the structure of three outdoor control valves can be identical, also can be different, and be all such as check valve or single-pass magnetic valve, such as wherein one or two is check valve again, and remaining is single-pass magnetic valve, can select flexibly during embody rule.In like manner, the structure of three indoor control valves can be identical, also can be different, and be all such as check valve or single-pass magnetic valve, such as wherein one or two is check valve again, and remaining is single-pass magnetic valve, can select flexibly during embody rule.As shown in Figure 3 and Figure 4, in a preferred embodiment, all control valves are check valve, thus the design of simplified control system, make the reliability of heat-exchange system higher.
Outdoor heat exchanger 120 also comprises the second coolant distributor 124 that each refrigerant flow of drawing in heat exchanger 120 outdoor collects by the first coolant distributor 121 and being used for of entering outdoor heat exchanger 120 for refrigerant being divided into multichannel, wherein the first coolant distributor 121 and the second coolant distributor 124 all have and gather interface and gather multiple points of stream interfaces of orifice with this, gather interface to be connected with refrigerant circulation circuit, by a point stream interface, refrigerant is divided into multichannel; Indoor heat exchanger 140 comprises the 4th coolant distributor 144 that each refrigerant flow of drawing in heat exchanger 140 indoor collects by the 3rd coolant distributor 141 and being used for that enters indoor heat exchanger 140 for refrigerant being divided into multichannel, wherein the 3rd coolant distributor 141 and the 4th coolant distributor 144 all have and gather interface and gather multiple points of stream interfaces of orifice with this, gather interface to be connected with refrigerant circulation circuit, by a point stream interface, refrigerant is divided into multichannel.
Be to be understood that, the function of the first coolant distributor 121 and the second coolant distributor 124 can be exchanged, the function of the 3rd coolant distributor 141 and the 4th coolant distributor 144 can be exchanged, as shown in Figure 3, when this heat-exchange system is in refrigeration mode (flow direction of refrigerant is see shown by arrow), first coolant distributor 121 enters outdoor heat exchanger 120 for refrigerant being divided into multichannel, second coolant distributor 124 is for pooling together the multichannel refrigerant from outdoor heat exchanger 120, 4th coolant distributor 144 enters indoor heat exchanger 140 for refrigerant being divided into multichannel, 3rd coolant distributor 141 is for pooling together the multichannel refrigerant from indoor heat exchanger 140, as shown in Figure 3, when this heat-exchange system is in heating mode (flow direction of refrigerant is see shown by arrow), 3rd coolant distributor 141 enters indoor heat exchanger 140 for refrigerant being divided into multichannel, 4th coolant distributor 144 is for pooling together the multichannel refrigerant from indoor heat exchanger 140, second coolant distributor 124 is divided into multichannel for refrigerant and enters outdoor heat exchanger 120, and the first coolant distributor 121 is for pooling together the multichannel refrigerant from outdoor heat exchanger 120.
In better embodiment, this outdoor heat exchanger 120 also comprises the first outdoor three-way pipe 123 and the second outdoor three-way pipe 126, one end of second outdoor branch road 129 is connected with the first outdoor branch road 128 by the first outdoor three-way pipe 123, the other end is connected with the second pipeline P2 by the second outdoor three-way pipe 126, namely the 3rd outdoor control valve 122 is between the first coolant distributor 121 and the first outdoor three-way pipe 123, and the first outdoor control valve 125 is between the second coolant distributor 124 and the second outdoor three-way pipe 126.
In like manner, this indoor heat exchanger 140 also comprises the first indoor three-way pipe 143 and the second indoor three-way pipe 146, one end of second indoor branch road 149 is connected with the first indoor branch road 148 by the first indoor three-way pipe 143, the other end is connected with the second pipeline P2 by the second indoor three-way pipe 146, namely the 3rd indoor control valve 142 is between the 3rd coolant distributor 141 and the first indoor three-way pipe 143, and the first indoor control valve 145 is between the 4th coolant distributor 144 and the second indoor three-way pipe 146.
For the refrigerant flow of outside, when heat-exchange system is in refrigeration mode, first outdoor control valve 125 and the 3rd outdoor control valve 122 are all closed, and the second outdoor control valve 127 conducting, therefore refrigerant is first divided into multichannel by the first coolant distributor 121 and enters outdoor heat exchanger 120 heat exchange (now refrigerant does not flow through the first outdoor branch road 128), outdoor heat exchanger 120 heat exchange is reentered via the first outdoor branch road 128 and the second outdoor branch road 129 successively after being collected by the second coolant distributor 124 again, enter in refrigerant circulation circuit finally by the second outdoor three-way pipe 126 and continue circulation, when heat-exchange system is in heating mode, first outdoor control 125 and all conductings of the 3rd outdoor control valve 122, and the second outdoor control valve 127 is closed, therefore refrigerant is first divided into multichannel by the second coolant distributor 124 and enters outdoor heat exchanger 120 heat exchange, enter refrigerant circulation circuit after being collected by the first coolant distributor 121 again and continue circulation, therefore refrigerant does not flow through the second outdoor branch road 129 when entering outdoor heat exchanger 120 and evaporating, to guarantee that each road refrigerant synchronously enters evaporating state.
For the refrigerant flow of indoor, when heat-exchange system is in refrigeration mode, first indoor control valve 145 and all conductings of the 3rd indoor control valve 142, and the second indoor control valve 147 is closed, therefore refrigerant is first divided into multichannel by the 4th coolant distributor 144 and enters indoor heat exchanger 140 heat exchange, enter after being collected by the 3rd coolant distributor 141 in refrigerant circulation circuit again and continue circulation, refrigerant does not flow through the second indoor branch road 149 when entering indoor heat exchanger 140 and evaporating; When heat-exchange system is in heating mode, first indoor control valve 145 and the 3rd indoor control valve 142 are all closed, and the second indoor control valve 147 conducting, therefore refrigerant is first divided into multichannel by the 3rd coolant distributor 141 and enters indoor heat exchanger 140 heat exchange (now refrigerant does not flow through the first indoor branch road 148), reenter indoor heat exchanger 140 heat exchange via the first indoor branch road 148 and the second indoor branch road 149 successively after being collected by the 4th coolant distributor 144 again, enter in refrigerant circulation circuit finally by the outer three-way pipe 146 of fourth ventricle and continue circulation.All flow through one in the condensation link that refrigerant circulates at cooling and warming and cross cold flow road, thus increase refrigerant degree of supercooling after condensation, and the refrigerant flow that refrigerant is all put by first wife in the evaporation link of cooling and warming circulates, therefore the increase second outdoor branch road 129 and the second indoor branch road 149 have neither part nor lot in evaporation link, guarantee that each refrigerant flow of outdoor heat exchanger 120 and indoor heat exchanger 140 all synchronously enters evaporating state, thus improve complete machine service behaviour.
To sum up, no matter this heat-exchange system is be in refrigeration mode, still heating mode is in, equal can be formed one for increasing refrigerant degree of supercooling cross cold flow road, thus make outdoor heat exchanger 120 and indoor heat exchanger 140 all can obtain the utilization of maximal efficiency, substantially increase cooling and warming ability and the Energy Efficiency Ratio of complete machine.Further, by increasing the degree of supercooling of refrigerant, the bubble be mingled in refrigerant can be reduced, substantially reduce loss when entering in throttling arrangement 130 and carrying out throttling, be conducive to the service behaviour promoting complete machine.
The present invention also provides a kind of air-conditioner, and in one embodiment, this air-conditioner comprises heat-exchange system, is realized the transfer of indoor and outdoor heat, thus realize temp regulating function by this heat-exchange system.Certainly, this air-conditioner also comprises that other are indispensable but be the building block of prior art, and such as indoor and outdoor blower fan, housing etc., therefore not to repeat here.
This air-conditioner embodiment comprises whole technical schemes of the whole embodiment of above-mentioned heat-exchange system, and the technique effect reached is also identical, does not repeat them here.
These are only the preferred embodiments of the present invention; not thereby the scope of the claims of the present invention is limited; every utilize description of the present invention and accompanying drawing content to do equivalent structure or equivalent flow process conversion; or be directly or indirectly used in other relevant technical fields, be all in like manner included in scope of patent protection of the present invention.
Claims (10)
1. a heat-exchange system, comprise the compressor that head and the tail connect to form refrigerant circulation circuit successively, reversing arrangement, outdoor heat exchanger, throttling arrangement and indoor heat exchanger, in described refrigerant circulation circuit between described outdoor heat exchanger and described indoor heat exchanger and with described compressor, the corresponding pipeline of reversing arrangement is the first pipeline, in described refrigerant circulation circuit between described outdoor heat exchanger with described indoor heat exchanger and the pipeline corresponding with described throttling arrangement is the second pipeline, it is characterized in that, described heat-exchange system also comprises the outdoor supercooling apparatus and indoor supercooling apparatus that are arranged in parallel with described second pipeline respectively, described outdoor supercooling apparatus is between described outdoor heat exchanger and described throttling arrangement, described indoor supercooling apparatus is between described indoor heat exchanger and described throttling arrangement, described second pipeline is provided with and is connected in parallel the first outdoor control valve between node at two of described outdoor supercooling apparatus, crossing on cold flow road of described outdoor supercooling apparatus is provided with the second outdoor control valve, described second pipeline is provided with and is connected in parallel the first indoor control valve between node at two of described indoor supercooling apparatus, crossing on cold flow road of described indoor supercooling apparatus is provided with the second indoor control valve.
2. heat-exchange system as claimed in claim 1, it is characterized in that, described outdoor heat exchanger comprises the refrigerant flow that multi-channel parallel is arranged, the cold flow road of crossing of described outdoor supercooling apparatus comprises the first outdoor branch road and the second outdoor branch road that are arranged in parallel, any refrigerant flow in described outdoor heat exchanger forms described first outdoor branch road, described first outdoor branch road is provided with the 3rd outdoor control valve between itself and the refrigerant distribution node being connected in parallel node and described outdoor heat exchanger of described second outdoor branch road, described second outdoor control valve is positioned on described second outdoor branch road.
3. heat-exchange system as claimed in claim 2, it is characterized in that, described outdoor heat exchanger also comprises the first outdoor three-way pipe and the second outdoor three-way pipe, one end of described second outdoor branch road is connected with described first outdoor branch road by described first outdoor three-way pipe, and the other end is connected with described second pipeline by described second outdoor three-way pipe.
4. heat-exchange system as claimed in claim 2, it is characterized in that, described outdoor heat exchanger also comprises the second coolant distributor that each refrigerant flow of drawing from described outdoor heat exchanger collects by the first coolant distributor and being used for of entering described outdoor heat exchanger for refrigerant being divided into multichannel, described first outdoor control valve is connected in parallel between node and described second coolant distributor described second outdoor branch road and described second pipeline, described 3rd outdoor control valve is connected in parallel between node and described first coolant distributor described first outdoor branch road and described second outdoor branch road.
5. the heat-exchange system as described in claim 2,3 or 4, it is characterized in that, described first outdoor control valve is check valve or single-pass magnetic valve, and described second outdoor control valve is check valve or single-pass magnetic valve, and described 3rd outdoor control valve is check valve or single-pass magnetic valve.
6. heat-exchange system as claimed in claim 1, it is characterized in that, described indoor heat exchanger comprises the refrigerant flow that multi-channel parallel is arranged, the cold flow road of crossing of described indoor supercooling apparatus comprises the first indoor branch road and the second indoor branch road that are arranged in parallel, any refrigerant flow in described indoor heat exchanger forms described first indoor branch road, described first indoor branch road is provided with the 3rd indoor control valve between itself and the refrigerant distribution node being connected in parallel node and described indoor heat exchanger of described second indoor branch road, described second indoor control valve is positioned on described second indoor branch road.
7. heat-exchange system as claimed in claim 6, it is characterized in that, described indoor heat exchanger also comprises the first indoor three-way pipe and the second indoor three-way pipe, one end of described second indoor branch road is connected with described first indoor branch road by described first indoor three-way pipe, and the other end is connected with described second pipeline by described second indoor three-way pipe.
8. heat-exchange system as claimed in claim 6, it is characterized in that, described indoor heat exchanger also comprises the 4th coolant distributor that each refrigerant flow of drawing from described indoor heat exchanger collects by the 3rd coolant distributor and being used for that enters described indoor heat exchanger for refrigerant being divided into multichannel, described first indoor control valve is connected in parallel between node and described 3rd coolant distributor described second indoor branch road and described second pipeline, described 3rd indoor control valve is connected in parallel between node and described 4th coolant distributor described first indoor branch road and described second indoor branch road.
9. the heat-exchange system as described in claim 6,7 or 8, it is characterized in that, described first indoor control valve is check valve or single-pass magnetic valve, and described second indoor control valve is check valve or single-pass magnetic valve, and described 3rd indoor control valve is check valve or single-pass magnetic valve.
10. an air-conditioner, is characterized in that, comprises the heat-exchange system according to any one of claim 1 to 9.
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|---|---|---|---|---|
| CN105202740A (en) * | 2015-10-14 | 2015-12-30 | 珠海格力电器股份有限公司 | Heat pump air conditioner and heat exchanger thereof |
| CN105466083A (en) * | 2015-12-24 | 2016-04-06 | 珠海格力电器股份有限公司 | Heat pump air conditioner heat exchanger with variable flow path and control method thereof |
| CN106705217A (en) * | 2016-11-30 | 2017-05-24 | 美的集团股份有限公司 | Control method and system used for improving heating effect of air conditioner and air conditioner |
| CN106766330A (en) * | 2016-11-30 | 2017-05-31 | 美的集团股份有限公司 | A kind of air-conditioning system, its control method and air-conditioner |
| CN106766329A (en) * | 2016-11-30 | 2017-05-31 | 美的集团股份有限公司 | A kind of air-conditioning system, its control method and air-conditioner |
| CN107062580A (en) * | 2017-03-21 | 2017-08-18 | 珠海格力电器股份有限公司 | Control method for reducing noise of indoor unit of air conditioner and multi-split air conditioner |
Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5259213A (en) * | 1991-12-19 | 1993-11-09 | Gary Phillippe | Heat pump efficiency enhancer |
| JP2002243301A (en) * | 2001-02-14 | 2002-08-28 | Daikin Ind Ltd | Heat exchanging unit and air conditioner |
| CN2670856Y (en) * | 2003-12-05 | 2005-01-12 | 山东康特姆新能源有限公司 | Evaporator of hot pump with supercooling flow procedure |
| CN101776308A (en) * | 2009-01-13 | 2010-07-14 | 珠海格力电器股份有限公司 | Energy-saving air conditioner |
| CN102109202A (en) * | 2009-12-25 | 2011-06-29 | 株式会社富士通将军股份有限公司 | Air conditioner |
| CN203533967U (en) * | 2013-09-04 | 2014-04-09 | 南京国睿博拉贝尔环境能源有限公司 | Air source heat pump unit with bi-directional supercooling section |
| CN204678735U (en) * | 2015-05-05 | 2015-09-30 | 广东美的制冷设备有限公司 | Air-conditioner and heat-exchange system thereof |
-
2015
- 2015-05-05 CN CN201510224980.8A patent/CN104848579B/en active Active
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5259213A (en) * | 1991-12-19 | 1993-11-09 | Gary Phillippe | Heat pump efficiency enhancer |
| JP2002243301A (en) * | 2001-02-14 | 2002-08-28 | Daikin Ind Ltd | Heat exchanging unit and air conditioner |
| CN2670856Y (en) * | 2003-12-05 | 2005-01-12 | 山东康特姆新能源有限公司 | Evaporator of hot pump with supercooling flow procedure |
| CN101776308A (en) * | 2009-01-13 | 2010-07-14 | 珠海格力电器股份有限公司 | Energy-saving air conditioner |
| CN102109202A (en) * | 2009-12-25 | 2011-06-29 | 株式会社富士通将军股份有限公司 | Air conditioner |
| CN203533967U (en) * | 2013-09-04 | 2014-04-09 | 南京国睿博拉贝尔环境能源有限公司 | Air source heat pump unit with bi-directional supercooling section |
| CN204678735U (en) * | 2015-05-05 | 2015-09-30 | 广东美的制冷设备有限公司 | Air-conditioner and heat-exchange system thereof |
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