CN202792728U - Air conditioner and two-stage compression cycle heat pump system - Google Patents
Air conditioner and two-stage compression cycle heat pump system Download PDFInfo
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- CN202792728U CN202792728U CN201220444968.XU CN201220444968U CN202792728U CN 202792728 U CN202792728 U CN 202792728U CN 201220444968 U CN201220444968 U CN 201220444968U CN 202792728 U CN202792728 U CN 202792728U
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Abstract
The utility model provides a two-stage compression cycle heat pump system. A condenser and an evaporator are sequentially arranged in the heat pump system; a first flash-tank is arranged between the condenser and the evaporator; a refrigerant passes through the first flash-tank and is subjected to flash evaporation in the first flash-tank, one part of liquid refrigerant adsorbs heat of the other part of liquid refrigerant to be evaporated into gas, and the liquid refrigerant which is subjected to heat adsorption and temperature reduction flows out of the first flash-tank; the cooled refrigerant continuously flows into a second flash-tank connected in series with the first flash-tank to be subjected to flash evaporation, the liquid refrigerant is subjected to flash evaporation by two stages of flash-tanks, the content of a gas refrigerant mixture in the liquid refrigerant which is subjected to heat adsorption and temperature reduction again is very low, the degree of dryness of the throttled refrigerant becomes high, and the flow of the liquid refrigerant is increased; and due to small interference effect of a gas refrigerant on heat exchange in the evaporator, heat exchange efficiency is improved, so that finally, refrigerating capacity of the refrigerant is improved and refrigerating efficiency is improved. The utility model further provides an air conditioner with the two-stage compression cycle heat pump system.
Description
Technical field
The utility model relates to air-conditioning technical field, more particularly, relates to a kind of air-conditioner and two stages of compression circulating heat pump system.
Background technology
Along with growth in the living standard, people are more and more higher to the requirement of residential environment, and air-source heat pump air conditioning system is widely used in the family expenses central air-conditioning.
At present in the two stages of compression circulating heat pump system, be provided with a flash evaporation in the heat pump, therefore when environment temperature is low, keep easily more gas in the refrigerant, in refrigerant enters flash evaporation after, refrigerant temperature in flash evaporation further reduces, so that occur more gas in the flash evaporation, therefore refrigerant continue by the time, the obstruct heat exchange function influence of gas refrigerant further lower the temperature, cause the refrigerating capacity of refrigerant to descend.
Simultaneously, because the compressor efficiency reduction, so that the real system efficiency of air-conditioning system is lower than conventional single level system with efficient.
Therefore, how improving the refrigerating efficiency of refrigerant in the two stages of compression circulating heat pump system, is present those skilled in the art's problem demanding prompt solution.
The utility model content
In view of this, the utility model provides a kind of two stages of compression heat pump, to improve the refrigerating efficiency of refrigerant in the two stages of compression circulating heat pump system; The utility model also provides a kind of air-conditioner.
In order to achieve the above object, the utility model provides following technical scheme:
A kind of two stages of compression heat pump, comprise condenser and evaporimeter that order arranges, be provided with the first flash evaporation between described condenser and the described evaporimeter, also be provided with the second flash evaporation with described the first flash evaporation arranged in series between described condenser and the described evaporimeter.
Preferably, in above-mentioned two stages of compression heat pump, the throttling arrangement of the inlet setting of described the second flash evaporation is electric expansion valve.
Preferably, in above-mentioned two stages of compression heat pump, described throttling arrangement is the decompression capillary.
Preferably, in above-mentioned two stages of compression heat pump, the exhaust outlet of described the second flash evaporation is connected with the gas returning port of compressor in the heat pump.
Preferably, in above-mentioned two stages of compression heat pump, be provided with decompressor between the exhaust outlet of described the second flash evaporation and the described gas returning port.
Preferably, in above-mentioned two stages of compression heat pump, described decompressor is the decompression capillary.
Preferably, in above-mentioned two stages of compression heat pump, the exhaust outlet of described the first flash evaporation is connected with the gas supplementing opening of compressor in the heat pump, and is provided with magnetic valve between the exhaust outlet of described the first flash evaporation and the described gas supplementing opening.
Preferably, in above-mentioned two stages of compression heat pump, be provided with thermistor on the gas of the compressor of described the first flash evaporation, described the second flash evaporation, described evaporimeter, described condenser and heat pump or the liquid communication pipeline.
Preferably, in above-mentioned two stages of compression heat pump, described the second flash evaporation is arranged between described the first flash evaporation and the described evaporimeter.
A kind of air-conditioner comprises the heat pump of the section of setting within it, and described heat pump is the described two stages of compression heat pump of above-mentioned any one.
The two stages of compression heat pump that the utility model provides, be sequentially set with condenser and evaporimeter in the heat pump, be provided with the first flash evaporation between condenser and the evaporimeter, when refrigerant circulates between condenser and evaporimeter, refrigerant is by the first flash evaporation, and through primary temperature-fall period, the refrigerant after the cooling is by flowing out in the first flash evaporation in the first flash evaporation; Also be provided with the second flash evaporation with the first flash evaporation arranged in series between condenser and the evaporimeter, after refrigerant after the cooling continues to flow to the second flash evaporation, the secondary temperature-fall period of refrigerant process this moment, so that the increase of the refrigerating capacity of refrigerant, simultaneously, when refrigerant enters the second flash evaporation after the cooling, refrigerant for the second time air-breathing temperature reduces, and can reduce harmful overheated when air-breathing, has reduced the mass dryness fraction after the refrigerant outflow, increase the flow of liquid coolant, improved refrigerating efficiency.
Description of drawings
In order to be illustrated more clearly in the utility model embodiment or technical scheme of the prior art, the below will do to introduce simply to the accompanying drawing of required use in embodiment or the description of the Prior Art, apparently, accompanying drawing in the following describes only is embodiment more of the present utility model, for those of ordinary skills, under the prerequisite of not paying creative work, can also obtain according to these accompanying drawings other accompanying drawing.
The structural representation of the two stages of compression heat pump that Fig. 1 provides for the utility model;
The Mathematical Modeling figure of the two stages of compression heat pump that Fig. 2 provides for the utility model.
The specific embodiment
The utility model discloses a kind of two stages of compression heat pump, improved the refrigerating efficiency of refrigerant in the two stages of compression circulating heat pump system; The utility model also provides a kind of air-conditioner.
Below in conjunction with the accompanying drawing among the utility model embodiment, the technical scheme among the utility model embodiment is carried out clear, complete description, obviously, described embodiment only is the utility model part embodiment, rather than whole embodiment.Based on embodiment of the present utility model, those of ordinary skills are not making the every other embodiment that obtains under the creative work prerequisite, all belong to the scope of the utility model protection.
As shown in Figure 1, the structural representation of the two stages of compression heat pump that provides for the utility model of Fig. 1.
The utility model provides a kind of two stages of compression heat pump, be sequentially set with condenser 3 and evaporimeter 10 in the heat pump, be provided with the first flash evaporation 5 between condenser 3 and the evaporimeter 10, when refrigerant circulates between condenser 3 and evaporimeter 10, refrigerant is by the first flash evaporation 5, and carry out shwoot in the first flash evaporation 5, the operative liquid refrigerant absorbs the heat of another part liquid refrigerants and flashes to gaseous state, by the liquid refrigerants behind the absorbing and cooling temperature by flowing out in the first flash evaporation 5; Also be provided with the second flash evaporation 7 with the first flash evaporation 5 arranged in series between condenser 3 and the evaporimeter 10, continued to flow to the second flash evaporation 7 by the liquid refrigerants behind the absorbing and cooling temperature and carry out shwoot, carry out shwoot, the operative liquid refrigerant absorbs the heat of another part liquid refrigerants and flashes to gaseous state, this moment since gaseous coolant through twice shwoot and the gas-liquid separation of the first flash evaporation 5, the second flash evaporation 7, again considerably less by gaseous coolant mixture content in the liquid refrigerants behind the absorbing and cooling temperature, mass dryness fraction after the throttling uprises, and this liquid refrigerants flow increases; And owing to the interference effect of gaseous coolant to heat exchange in the evaporimeter reduces, so that the heat exchange efficiency raising is final so that the refrigerating capacity increase of refrigerant.
After flowing out, refrigerant flows into the second flash evaporation 7 when interior in by the first flash evaporation 5, refrigerant itself has larger pressure, for fear of refrigerant in flow process, because the variation of the flowing space need to make refrigerant keep more stable pressure in flow process so that the pressure of refrigerant liquid has greatly changed.
In the utility model one specific embodiment, the inlet of the second flash evaporation 7 is provided with throttling arrangement 6.Throttling arrangement 6 mainly plays the effect of throttling and step-down.By throttling arrangement 6, so that refrigerant liquid flow in flow process reduces, limited liquid and entered flow in the second flash evaporation 7, thereby kept keeping in the liquid flow process more stable pressure.
Particularly, throttling arrangement 6 is set to electric expansion valve.Electric expansion valve is the regulating element of regulating the evaporimeter liquid supply rate according to pre-set programs, can provide preferably flow regulating function in low temperature environment.Certainly, throttling arrangement 6 also can be set to capillary, and capillary is as the throttle part in the refrigeration system, is adapted to liquid and flows into the second flash evaporation 7 throttling and hypotensive effect to liquid when interior.Certainly, throttling arrangement 6 can also be set to throttle expansion valve.
Refrigerant is when flowing into the second flash evaporation 7 inside, the pressure that the refrigerant that flows into is subject to diminishes, therefore a part of gas in the compressed refrigerant is discharged, so that the temperature of refrigerant further reduces, simultaneously, because gas is further discharged in the refrigerant, so that the temperature of refrigerant further reduces, thereby further reached cooling effect to refrigerant.When yet gas was discharged in the refrigerant, the gas in the second flash evaporation 7 was the gas with lower temperature, if when this portion gas directly discharges, can cause undoubtedly the waste of energy.
In the utility model one specific embodiment, the gas returning port of the compressor 1 in the exhaust outlet of the second flash evaporation 7 and the heat pump is connected.Compressor is promoted to high pressure with low-pressure gas when work, in this process, compressor 1 drives piston by motor rotation refrigerant gas is compressed.Be connected with the gas returning port of compressor 1 by the exhaust outlet with the second flash evaporation 7, gaseous coolant after heat absorption heats up is delivered directly to the gas returning port of compressor 1, by with the opposing steam flow in the second flash evaporation 7, can avoid gas to rest in the second flash evaporation 7 and reduce the heat exchange property of liquid coolant, reduce linear loss, improve refrigerant circulation, improve refrigerating capacity and refrigerating efficiency.
Because what the exhaust outlet by the second flash evaporation 7 was discharged be the high-temperature gas refrigerant, when this portion gas is directly inputted by the gas returning port of compressor 1, can the normal operation of compressor be exerted an influence.
Affect the normal operation of compressor 1 for fear of the high-temperature gas refrigerant of being discharged by the second flash evaporation 7, in the utility model one specific embodiment, be provided with decompressor 9 between the exhaust outlet of the second flash evaporation 7 and the gas returning port.The high-temperature gas refrigerant of the second flash evaporation 7 interior generations, through decompressor 9 decompression coolings, become the gas returning port that is delivered to again compressor 1 behind the lower gaseous coolant of temperature, the high-temperature gas refrigerant that comes with process evaporimeter heat exchange mixes, reduced the temperature of the gaseous coolant of final inflow compressor 1, namely reduce suction, the delivery temperature of compressor, guaranteed the job stability of two stages of compression heat pump.
Particularly, decompressor 9 is the decompression capillary.Certainly, decompressor 9 can also be set to choke valve, so that gas purging amount in the second flash evaporation is controlled.
Compressor 1 in the course of the work, when moving under low evaporating temperature, along with the variation of capacity, inspiratory volume increases, refrigerant circulation reduces, and the problem that heating capacity descends occurs; During work, because the compressor pressure ratio increases, volumetric efficiency descends, and compressor displacement and efficiency also can significantly descend, and in order to guarantee the normal working performance of compressor 1, avoids because the variation of capacity reduces the work efficiency of compressor 1.
In the utility model one specific embodiment, the exhaust outlet of the first flash evaporation 5 communicates with the gas supplementing opening of compressor 1 in the heat pump, refrigerant is during through the first flash evaporation 5, gaseous coolant after heat absorption heats up is transported to compressor 1 inside through the exhaust outlet of the first flash evaporation 5, by the tonifying Qi effect to compressor 1, guaranteed 1 normal operation of compressor; Simultaneously, between the exhaust outlet of the first flash evaporation 5 and gas supplementing opening, magnetic valve 8 is set, compressor 1 in the course of the work, the tonifying Qi action is by regularly carrying out, guarantee to have enough capacities in the compressor 1, by magnetic valve 8 is set, so that the first flash evaporation moves and can continue to carry out the tonifying Qi of compressor within the predetermined cycle, so that in heat pump, play according to actual needs the first flash evaporation to compressor tonifying Qi regulating action.
Whether the two stages of compression heat pump by the monitoring to its each several part operating temperature, can in running orderly be judged it in the course of the work, has played the effect that the duty of heat pump is monitored, and guarantees that the safety of its duty is carried out.
In the utility model one specific embodiment, be provided with thermistor on the gas of the compressor 1 of the first flash evaporation 5, the second flash evaporation 7, evaporimeter 10, condenser 3 and heat pump or the liquid communication pipeline.On the first flash evaporation 5 and the second flash evaporation 7 gas exhaust pipings thermistor is set all, so that the flash evaporation effluent air temp is monitored, and can be communicated with by thermistor the control system of heat pump, the real-time working state of the flash evaporation by thermistor monitoring is made adjusting to the work of system.
Similarly, the thermistor that arranges on the connecting pipeline of the compressor 1 of evaporimeter 10, condenser 3 and heat pump, can be to flowing through three or monitored by the real-time working situation that compressor 1 is discharged refrigerant, and by monitored data the duty of counter structure is regulated, thereby keep the job stability of whole system.
In the utility model one specific embodiment, the second flash evaporation 7 is arranged between the first flash evaporation and the evaporimeter 10.Then in the structure chart of two levels of thermal pumping system, compressor 1 connects a cross valve 2, and in the clockwise direction, condenser 3, the first flash evaporation 5, the second flash evaporation 7 and evaporimeter 10 set gradually.
Take process of refrigerastion as example, compressor 1 is transported to outdoor condenser 3 by cross valve 2 with the high-pressure gaseous refrigerant and carries out heat exchange, and the refrigerant after the cooling enters in the first flash evaporation 5 through throttling arrangement 4.Be provided with two branch roads on the first flash evaporation 5, article one, be the circulation branch road of gas, when refrigerant flowed into, its pressure reduced inner a part of gas and discharges, realized the further cooling of refrigerant, the magnetic valve that the gas of discharge arranges on branch road is got back to the gas supplementing opening of compressor; Another is the circulation branch road of refrigerant, when refrigerant continues to be circulated to the second flash evaporation 7, gas in the refrigerant is further discharged, thereby so that the temperature of refrigerant further reduces, similarly, be provided with gas on the second flash evaporation 7, two branch roads of liquid, the gas of discharging directly is discharged into the gas returning port of compressor, and refrigerant continues to enter evaporimeter 10, this moment, so that evaporimeter 10 has obtained better heat transfer effect, refrigerant entered the gas-liquid separator of compressor 1 after the circulation through cross valve 2 owing to have less gas and lower temperature in the refrigerant, enter again compressor through gas-liquid separator, thereby continue next circulation.
Same, under heating mode, compressor 1 is discharged the high-pressure gaseous refrigerant according to the reverse circulated of process of refrigerastion, and by the acting in conjunction of the first flash evaporation 5 and the second flash evaporation 7, the refrigerant that obtains lower temperature has played better heat transfer effect.
When the tonifying Qi state, magnetic valve 8 is opened, and the gas of the first flash evaporation 5 interior violent shwoots mixes by the intermediate cavity that the tonifying Qi pipeline enters compressor 1, enters to continue compression in the two-stage compression chamber again; The gas of the second flash evaporation 7 interior shwoots flows into the compressor air suction chamber by decompression capillary return-air, so that more gas is discharged in the second flash evaporation, avoid gas to reduce the transsexual energy of the second flash evaporation 7 interior liquid refrigerants, reduce linear loss, improved refrigerant circulation.
As shown in Figure 2, the Mathematical Modeling figure of the two stages of compression heat pump that provides for the utility model of Fig. 2.
Among the figure, abscissa is than enthalpy h, and the ordinate axle is the logarithm value lgp of absolute pressure.In the figure, q
0What the curve at place represented is process of refrigerastion and refrigerating capacity in the one-level shwoot system; q
0Process of refrigerastion and refrigerating capacity in the secondary shwoot system that ` represents, the change of process of refrigerastion appears in one-level shwoot system and secondary shwoot system at the A place, by can draw among the figure the time, there are the difference DELTA q=q of a refrigerating capacity in one-level shwoot system and secondary shwoot system
0`-q
0, therefore, secondary shwoot system has increased the refrigerating capacity of heat pump than one-level shwoot system.
Simultaneously, secondary shwoot system can make the suction temperature of refrigerant reduce, and it is air-breathing harmful overheated to reduce, and reduces the mass dryness fraction of evaporator inlet refrigerant, increases the flow of liquid coolant.
Based on the two stages of compression heat pump that provides in above-described embodiment, the utility model also provides a kind of air-conditioner, and its inside is provided with heat pump, the two stages of compression heat pump of this heat pump for providing in above-described embodiment.
Because this air-conditioner has adopted the two stages of compression heat pump of above-described embodiment, so this air-conditioner please refer to above-described embodiment by the beneficial effect that the two stages of compression heat pump brings.
To the above-mentioned explanation of the disclosed embodiments, make this area professional and technical personnel can realize or use the utility model.Multiple modification to these embodiment will be apparent concerning those skilled in the art, and General Principle as defined herein can in the situation that does not break away from spirit or scope of the present utility model, realize in other embodiments.Therefore, the utility model will can not be restricted to these embodiment shown in this article, but will meet the widest scope consistent with principle disclosed herein and features of novelty.
Claims (10)
1. two stages of compression heat pump, comprise condenser (3) and evaporimeter (10) that order arranges, be provided with the first flash evaporation (5) between described condenser (3) and the described evaporimeter (10), it is characterized in that, also be provided with the second flash evaporation (7) with described the first flash evaporation (5) arranged in series between described condenser (3) and the described evaporimeter (10).
2. two stages of compression heat pump according to claim 1 is characterized in that, the throttling arrangement (6) that the inlet of described the second flash evaporation (7) arranges is electric expansion valve.
3. two stages of compression heat pump according to claim 2 is characterized in that, described throttling arrangement (6) is the decompression capillary.
4. two stages of compression heat pump according to claim 1 is characterized in that, the exhaust outlet of described the second flash evaporation (7) is connected with the gas returning port of compressor (1) in the heat pump.
5. two stages of compression heat pump according to claim 4 is characterized in that, is provided with decompressor (9) between the exhaust outlet of described the second flash evaporation (7) and the described gas returning port.
6. two stages of compression heat pump according to claim 5 is characterized in that, described decompressor (9) is the decompression capillary.
7. two stages of compression heat pump according to claim 1, it is characterized in that, the exhaust outlet of described the first flash evaporation (5) is connected with the gas supplementing opening of compressor (1) in the heat pump, and is provided with magnetic valve (8) between the exhaust outlet of described the first flash evaporation (5) and the described gas supplementing opening.
8. two stages of compression heat pump according to claim 1, it is characterized in that, be provided with thermistor on the gas of the compressor (1) of described the first flash evaporation (5), described the second flash evaporation (7), described evaporimeter (10), described condenser (3) and heat pump or the liquid communication pipeline.
9. the described two stages of compression heat pump of any one is characterized in that according to claim 1-8, and described the second flash evaporation (7) is arranged between described the first flash evaporation (5) and the described evaporimeter (10).
10. air-conditioner comprises the heat pump of the section of setting within it it is characterized in that described heat pump is the described two stages of compression heat pump of claim 1-9 any one.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201220444968.XU CN202792728U (en) | 2012-08-31 | 2012-08-31 | Air conditioner and two-stage compression cycle heat pump system |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201220444968.XU CN202792728U (en) | 2012-08-31 | 2012-08-31 | Air conditioner and two-stage compression cycle heat pump system |
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| CN202792728U true CN202792728U (en) | 2013-03-13 |
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| CN201220444968.XU Expired - Lifetime CN202792728U (en) | 2012-08-31 | 2012-08-31 | Air conditioner and two-stage compression cycle heat pump system |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103673417A (en) * | 2012-08-31 | 2014-03-26 | 珠海格力电器股份有限公司 | Air conditioner and two-stage compression cycle heat pump system |
-
2012
- 2012-08-31 CN CN201220444968.XU patent/CN202792728U/en not_active Expired - Lifetime
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103673417A (en) * | 2012-08-31 | 2014-03-26 | 珠海格力电器股份有限公司 | Air conditioner and two-stage compression cycle heat pump system |
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| GR01 | Patent grant | ||
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| CX01 | Expiry of patent term |
Granted publication date: 20130313 |