CN1776325A - High-low temperature changeable graded evaporation air-conditioner heat pump water heater - Google Patents
High-low temperature changeable graded evaporation air-conditioner heat pump water heater Download PDFInfo
- Publication number
- CN1776325A CN1776325A CN 200510096424 CN200510096424A CN1776325A CN 1776325 A CN1776325 A CN 1776325A CN 200510096424 CN200510096424 CN 200510096424 CN 200510096424 A CN200510096424 A CN 200510096424A CN 1776325 A CN1776325 A CN 1776325A
- Authority
- CN
- China
- Prior art keywords
- magnetic valve
- air
- commutation
- water heater
- heat pump
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
Images
Landscapes
- Other Air-Conditioning Systems (AREA)
Abstract
The disclosed device includes refrigeration compressor, indoor water-cooled condenser (water heater), indoor air-cooling condenser (air heater), indoor air-cooling evaporator (air conditioner), and gas liquid separator etc. Based on different environment temperatures and different usages, setting each solenoid valve at different states realizes following switchable operation modes: heat pump cyclic mode of air heater at winter, heat pump cyclic mode of water heater at winter, refrigeration cycle mode of cold air and water heater at summer, refrigeration cycle mode of cold air at summer, heat pump cyclic mode of water heater at spring and autumn. The invention discloses environmental protection type multifunction equipment integrating air conditioner, heating and hot water.
Description
Technical field
The invention belongs to Engineering Thermophysics and using energy source ambit, relate to a kind of Teat pump boiler, particularly a kind of high-low temperature changeable graded evaporation air-conditioner heat pump water heater.
Background technology
Traditional steam compression heat pump and kind of refrigeration cycle all are contrary Rankine (Reversed Rankine) circulations.In circulation process, the cold-producing medium in the evaporimeter under low pressure evaporates, and absorbs the heat of lower temperature thermal source.By compressed machine compression formation of the low-pressure steam of evaporimeter outflow high pressure (high temperature) gas, emit heat by condenser then, be condensed into high pressure refrigerant liquid, then, highly pressurised liquid is through choke valve throttling, step-down, become the refrigerant air-liquid two-phase fluid of low-temp low-pressure, at last, absorb heat and gasify from low-temperature heat source again, realize a complete kind of refrigeration cycle, so move in circles the purpose that reaches refrigeration or heat.
Now, most air-conditionings, heat pump, refrigerator and refrigeration machine all are to adopt this traditional steam compression type refrigeration circulation form, have obtained great success.But, to put into practice and studies show that, this traditional kind of refrigeration cycle also also has its limitation.The difference that mainly is condensation temperature in the kind of refrigeration cycle and evaporating temperature can not be too big, otherwise can cause the high pressure of compressor and the compression ratio between the low pressure too big, delivery temperature is too high, pressure at expulsion is too high or pressure of inspiration(Pi) is low excessively, and problem such as restriction loss is too big, so that the Energy Efficiency Ratio of actual kind of refrigeration cycle reduces greatly, and the reliability of system and life-span reduce, and is serious even can't normally move.
For example, when traditional steam compression type refrigeration cycle applications during in following two kinds of situations, it is especially outstanding that above-mentioned defective just seems: the first is used for (being often referred to below-15 ℃) under the winter low temperature environment to indoor heating or heat supply water; It two is will obtain to be lower than-60 ℃ cryogenic temperature.Because the evaporating temperature that circulates under above-mentioned two kinds of situations and the temperature difference of condensation temperature be all greater than 80 ℃, this will cause the system can't operate as normal.Along with the fast development of the raising of people's living standard and science and technology, the application of this two aspect but more and more widely, demand is more and more urgent.How to break through the limitation of traditional vapor compression formula circulation, realization has the cryogenic refrigeration circulation of the difference of bigger condensation temperature and evaporating temperature, satisfying people's active demand, and reach environmental protection and purpose of energy saving simultaneously, this has become the hot issue of refrigeration and low temperature circle in the world.
Summary of the invention
At above-mentioned traditional existing defective of air source heat pump refrigeration system or deficiency, the objective of the invention is to, a kind of novel high-low temperature changeable graded evaporation air-conditioner heat pump water heater is provided.The present invention has used non-vapor of mixture refrigeration working medium therein, be intended to utilize non-vapor of mixture refrigeration working medium can carry out the principle of stage evaporation and fractional condensaion, it had both had in the characteristics high than Energy Efficiency Ratio under the high ambient temperature, have again less than the compression ratio of low ambient temperature lower compression machine, the circulation condensation and the bigger unique advantage of the temperature difference of evaporation.Therefore, this novel changeable, stage evaporation air-conditioner heat pump water heater not only is applicable to the hot environment temperature but also be applicable to the low temperature environment temperature, it can increase the poor of condensation temperature in the circulation and evaporating temperature greatly, has avoided that the difference of condensing pressure and evaporating pressure increases excessively in the circulation simultaneously again.In addition, because the present invention adopts the alternative refrigerant that helps environment, can reach the purpose of environmental protection simultaneously.
For above-mentioned task, the present invention adopts following technical scheme:
A kind of high-low temperature changeable graded evaporation air-conditioner heat pump water heater comprises refrigeration compressor, it is characterized in that, the refrigeration working medium of refrigeration compressor is a hybrid refrigeration working medium;
The high-pressure exhaust of refrigeration compressor is connected with gs-oil separator, the first commutation three-way magnetic valve, first magnetic valve, indoor air-cooled condenser or indoor air-cooled evaporimeter, second magnetic valve in turn; Indoor air-cooled condenser or indoor air-cooled evaporimeter are connected with the commutation four way solenoid valve by second magnetic valve, and are connected with the rectifying gas-liquid separator by this commutation four way solenoid valve; The top of rectifying gas-liquid separator directly is connected with the gas pipeline arrival end of heat exchanger; The bottom of rectifying gas-liquid separator is connected with the fluid pipeline arrival end of first throttle valve, the second commutation three-way magnetic valve and heat exchanger successively by tube connector; The fluid pipeline port of export of heat exchanger directly is connected with the low pressure air suction mouth of refrigeration compressor; The gas pipeline port of export of heat exchanger is connected with the second commutation three-way magnetic valve on the one hand by second choke valve on the pipeline, is connected with the commutation four way solenoid valve on the other hand;
Also by being connected with the output of indoor water-cooled condenser with the 7th magnetic valve, the input of indoor water-cooled condenser is connected with the first commutation three-way magnetic valve by the 6th magnetic valve second magnetic valve;
An interface of commutation four way solenoid valve is connected with a port of outdoor air-cooled evaporimeter or outdoor air-cooled condenser by the 3rd magnetic valve on the pipeline, perhaps is connected with the port of export of indoor water-cooled condenser by the 9th magnetic valve;
Another port of outdoor air-cooled evaporimeter or outdoor air-cooled condenser is connected with the arrival end of indoor water-cooled condenser with the 8th magnetic valve by the 4th magnetic valve, perhaps is connected with the fluid pipeline arrival end of heat exchanger with the 5th magnetic valve by the 4th magnetic valve;
The fluid pipeline arrival end of heat exchanger also is connected with the first commutation three-way magnetic valve by the tenth magnetic valve.
Changeable, the stage evaporation air-conditioner heat pump water heater of high low temperature of the present invention, be provided with commutation three-way magnetic valve and four way solenoid valve switching device shifter especially, make this heat pump in-15 ℃～40 ℃ ambient temperature ranges, all keep refrigeration performance preferably, but become both heat supply in winter, but summer air-conditioning again, but and the four seasons environmental protection and energy saving product of hot water is provided.
In, the stage evaporation air-conditioner heat pump water heater system changeable at high low temperature of the present invention, in order to realize winter operation steam air heater endless form, winter operation water heater endless form, summer operation cold wind device and water heater endless form, summer operation cold wind device endless form and move mutual switching between the water heater mode spring and autumn that the present invention is provided with the first commutation three-way magnetic valve, the second commutation three-way magnetic valve and commutation four way solenoid valve especially; Be provided with indoor air-cooled condenser (being steam air heater) or indoor air-cooled evaporimeter (being the cold wind device), outdoor air-cooled evaporimeter or outdoor air-cooled condenser, indoor water-cooled condenser (instant heating hydrophone) especially; Be provided with the rectifying gas-liquid separator that higher boiling working medium is separated with low boiling working fluid especially, be provided with especially the first throttle valve of higher boiling throttling and second choke valve that low boiling working fluid is carried out throttling; Being provided with especially after gas-liquid separator can be at-15 ℃～heat exchanger that moves in the low temperature environment temperature below-20 ℃, wet body in the low boiling working fluid high pressure of separating from gas-liquid separator with liquefaction; Two ends at indoor air-cooled condenser (being steam air heater) or indoor air-cooled evaporimeter (being the cold wind device) are provided with first magnetic valve and second magnetic valve especially, to realize the function conversion between indoor air-cooled condenser (being steam air heater) and the indoor air-cooled evaporimeter (being the cold wind device); Be provided with the 3rd magnetic valve and the 4th magnetic valve especially at the two ends of outdoor air-cooled evaporimeter or outdoor air-cooled condenser, to realize the function conversion between outdoor air-cooled evaporimeter or the outdoor air-cooled condenser; In addition, after outdoor air-cooled evaporimeter or outdoor air-cooled condenser, also be provided with the 5th magnetic valve especially, so that in the higher boiling worker quality liquid passage in the introducing of the refrigeration working medium behind the sweat cooling in the outdoor air-cooled evaporimeter heat exchanger, to make full use of its remaining cold, low boiling working fluid gas before the throttling is carried out precooling, thereby can significantly improve the performance of the restriction effect and the refrigeration compressor of low boiling working fluid gas.
The present invention can be widely used in fields such as family, school, hospital, scientific research, national defence, industry, agricultural, Aero-Space, can according to summer or winter different environment temperatures select air-conditioning or heating operation mode, indoor temperature in the control building, and can provide required hot water for people throughout the year.
Description of drawings
Fig. 1 is a general structure schematic diagram of the present invention;
Fig. 2 is the first embodiment of the present invention, i.e. winter operation steam air heater heat pump cycle mode structural representation.
Fig. 3 is a second embodiment of the present invention winter operation water heater heat pump cycle mode structural representation.
Fig. 4 is the third embodiment of the present invention, i.e. summer operation cold wind device and water heater kind of refrigeration cycle mode structural representation.
Fig. 5 is a fourth embodiment of the present invention summer operation cold wind device kind of refrigeration cycle mode structural representation.
Fig. 6 is the fifth embodiment of the present invention, i.e. spring and autumn operation water heater heat pump ring mode structural representation.
The specific embodiment
Below in conjunction with accompanying drawing circulatory system structural principle of the present invention and operation principle are elaborated.
Referring to Fig. 1, high low temperature of the present invention is changeable, the stage evaporation air-conditioner heat pump water heater comprises refrigeration compressor 1, gs-oil separator 2, the first commutation three-way magnetic valve 3, indoor air-cooled condenser (being steam air heater) or indoor air-cooled evaporimeter (being the cold wind device) 4, commutation four way solenoid valve 5, rectifying gas-liquid separator 6, first throttle valve 7, the second commutation three-way magnetic valve 8, heat exchanger 9, second choke valve 10, outdoor air-cooled evaporimeter or outdoor air-cooled condenser 11, indoor water-cooled condenser (instant heating hydrophone) 12, first magnetic valve 13, second magnetic valve 14, the 3rd magnetic valve 15, the 4th magnetic valve 16, the 5th magnetic valve 17, the 6th magnetic valve 18, the 7th magnetic valve 19, the 8th magnetic valve 20, the 9th magnetic valve 21 and the tenth magnetic valve 22 are formed.
The refrigeration working medium of refrigeration compressor 1 is a hybrid refrigeration working medium;
The high pressure gas end of refrigeration compressor 1 is connected with gs-oil separator 2, the first commutation three-way magnetic valve 3, first magnetic valve 13, indoor air-cooled condenser or indoor air-cooled evaporimeter 4, second magnetic valve 14 in turn; Indoor air-cooled condenser or indoor air-cooled evaporimeter 4 are connected with commutation four way solenoid valve 5 on the one hand by second magnetic valve 14, and are connected with rectifying gas-liquid separator 6 by this commutation four way solenoid valve 5; The top of rectifying gas-liquid separator 6 directly is connected with a gas pipeline arrival end of heat exchanger 9; The bottom of rectifying gas-liquid separator 6 is connected with the arrival end of another fluid pipeline of first throttle valve 7, the second commutation three-way magnetic valve 8 and heat exchanger 9 successively by tube connector; The port of export of the fluid pipeline of heat exchanger 9 directly is connected with the low pressure air suction end of refrigeration compressor 1; The port of export of the gas pipeline of heat exchanger 9 is connected with the second commutation three-way magnetic valve 8 on the one hand by second choke valve 10 on the pipeline, is connected with commutation four way solenoid valve 5 on the other hand;
Second magnetic valve 14 also is connected by the port of export of the 7th magnetic valve 19 with indoor water-cooled condenser (12), and the arrival end of indoor water-cooled condenser 12 is connected with the first commutation three-way magnetic valve 3 by the 6th magnetic valve 18;
An interface of commutation four way solenoid valve 5 is connected with outdoor air-cooled evaporimeter or outdoor air-cooled condenser 11 by the 3rd magnetic valve 15 on the pipeline, perhaps is connected with indoor water-cooled condenser 12 ports of export by the 9th magnetic valve 21;
The left port of outdoor air-cooled evaporimeter or outdoor air-cooled condenser 11 is connected with the arrival end of indoor water-cooled condenser 12 with the 8th magnetic valve 20 by the 4th magnetic valve 16, perhaps is connected with the arrival end of the fluid pipeline of heat exchanger 9 with the 5th magnetic valve 17 by the 4th magnetic valve 16;
The arrival end of the fluid pipeline of heat exchanger 9 also is connected with the first commutation three-way magnetic valve 3 by the tenth magnetic valve 22.
In order to overcome single refrigeration working medium low excessively defective of evaporating pressure under low ambient temperature, the present invention chooses working medium in following three groups of working medium, forms hybrid refrigeration working medium.Three groups of working medium is divided into higher boiling, mid-boiling point, three groups of working medium of low boiling by its standard vaporization temperature (a standard physical atmospheric pressure under saturated evaporating temperature).The hybrid refrigeration working medium of being formed can comprise higher boiling, mid-boiling point, three kinds of working medium of low boiling, they are chosen in higher boiling group, mid-boiling point group, low boiling group respectively, also can be only therein the higher boiling group and the low boiling group in choose, form bi-component or three components or mostly be the environment-friendly type hybrid refrigeration working medium of four components most:
1) higher boiling refrigeration working medium (abbreviation high temperature refrigerant) group: R123, R600, RC318, R142b etc.In hybrid refrigeration working medium, can in this group, choose one or both working medium, its total mol composition accounts for overall (10～65) % of hybrid refrigeration working medium.
2) mid-boiling point refrigeration working medium (warm working medium in the abbreviation) group: R134a, R152a, R124, R142, R161, R227ea.Choose one or both working medium in hybrid refrigeration working medium, also can not choose the working medium in this group in this group, its mol composition accounts for overall (1～50) % of hybrid refrigeration working medium.
3) low boiling refrigeration working medium (abbreviation cryogenic fluid) group: R23, R774, R116, R32, R125, R1270, R143, R290 etc.In hybrid refrigeration working medium, can in this group, choose one or both working medium, its total mol composition accounts for overall (25～70) % of hybrid refrigeration working medium.
In non-azeotropic mixed working medium, selected low boiling working fluid is under the outdoor environment temperature of (15～-20) ℃, and its evaporating temperature can be hanged down and be reached (20～-40) ℃, but its evaporating pressure can be up to (0.2～0.4) MPa; And high temperature refrigerant is when condensation temperature is 70 ℃ or above temperature, and its condensing pressure but only is about 2MPa, and the high pressure of compressor only is about 4～12 with the ratio of low pressure, obviously, can realize normal heat pump or kind of refrigeration cycle fully at this compression ratio lower compression machine.When forming hybrid refrigeration working medium, the effect of mid-boiling point component wherein only is heat transfer and the pressure balance that improves whole refrigeration system.Therefore, also can select it for use in some cases.
Various cold-producing mediums in above higher boiling group, mid-boiling point group and the low boiling group all can buy on market easily.
Below be the embodiment that the inventor provides:
Referring to Fig. 2, be first embodiment of the present invention winter operation steam air heater heat pump cycle mode structural representation.
Referring to Fig. 2, when system of the present invention is in winter operation steam air heater heat pump cycle mode, c interface in the 6th magnetic valve 18, the 7th magnetic valve 19, the 8th magnetic valve 20, the 9th magnetic valve 21, the tenth magnetic valve 22, the first commutation three-way magnetic valve 3, f interface and the indoor water-cooled condenser (instant heating hydrophone) 12 in the second commutation three-way magnetic valve 8 are in the closed condition, and remaining part and magnetic valve etc. all is in opening;
In Fig. 2, discharge by the high pressure gas end of refrigeration compressor 1 through the HTHP mixed working fluid gas after refrigeration compressor 1 compression, after gs-oil separator 2 carries out oil, gas separation, flow to the b interface by a interface in the first commutation three-way magnetic valve 3, through first magnetic valve 13, flow into indoor air-cooled condenser (being steam air heater) 4 interior condensations then and become HTHP mixed working fluid fluid, meanwhile, the heat that HTHP mixed working fluid fluid is discharged when condensation is the room heating with air heat.After cooled HTHP mixed working fluid fluid (fluid-mixing of higher boiling worker quality liquid and low boiling working fluid gas composition) flows out from indoor air-cooled condenser (being steam air heater) 4, flow through m interface and the n interface passage that form of commutation in the cross valve 5 through second magnetic valve 14, flow into from the top and carry out in the rectifying gas-liquid separator 6 that rectifying is gentle, liquid separates; Higher boiling worker quality liquid after the separation collects in the bottom of rectifying gas-liquid separator 6, and low boiling working fluid gas collects in the top of rectifying gas-liquid separator 6;
The higher boiling worker quality liquid of separating is flowed out by the bottom of rectifying gas-liquid separator 6, after 7 throttlings of first throttle valve, flow to the g interface by the e interface in the second commutation three-way magnetic valve 10, then in the higher boiling worker quality liquid passage in the inflow heat exchanger 9, evaporation becomes the higher boiling Working medium gas, the heat that absorbs low boiling working fluid gas simultaneously makes low boiling working fluid condensation of gas, liquefaction, and last, the higher boiling Working medium gas after the evaporation returns the low pressure air suction end of refrigeration compressor 1;
The low boiling working fluid gas of separating is flowed out by the top of rectifying gas-liquid separator 6, then in the low boiling working fluid gas pipeline in the inflow heat exchanger 9, the high pressure low boiling working fluid liquid of liquefaction for (5～15) ℃ being condensed, low pressure low boiling working fluid fluid is flowed out by heat exchanger 9, become the low pressure low boiling working fluid liquid of (20～-40) ℃ by 10 throttlings of second choke valve, follow the passage that forms by o interface in the commutation four way solenoid valve 5 and p interface, flow into evaporation in outdoor air-cooled evaporimeter or the outdoor air-cooled condenser 11 by the 3rd magnetic valve 15, heat in the while absorbing environmental air source, then, passing through the 4th magnetic valve 16 and the 5th magnetic valve 17, converge with higher boiling working medium fluid from first throttle valve 7, together in the higher boiling worker quality liquid passage in the inflow heat exchanger 9, at last, turn back to the low pressure air suction end of refrigeration compressor 1, begin new kind of refrigeration cycle.Like this, can make full use of the residue cold of low boiling working fluid fluid after outdoor air-cooled evaporimeter 11 evaporations under the low pressure, not only can carry out precooling to the high pressure low boiling working fluid gas that enters in the heat exchanger 9, also can make the low pressure low boiling working fluid fluid that returns refrigeration compressor 1 obtain preheating, can improve the performance of compressor and safe and reliable purpose energy-conservation, again thereby reach.
When system of the present invention is in winter operation steam air heater heat pump cycle mode, hybrid refrigeration working medium absorbs heat by outdoor air-cooled evaporimeter or outdoor air-cooled condenser 11 from the low temperature environment of (20～-30) ℃, and provide warm braw to the room by indoor air-cooled condenser (being steam air heater) or indoor air-cooled evaporimeter (cold wind device) 5, at this moment, the function of indoor air-cooled condenser in the system of the present invention (being steam air heater) or indoor air-cooled evaporimeter (cold wind device) 5 is a steam air heater, and the function of outdoor air-cooled evaporimeter or outdoor air-cooled condenser 11 is air-cooled evaporimeter.
Referring to Fig. 3, be second embodiment of the present invention winter operation water heater endless form structural representation.
Referring to Fig. 3, embodiments of the invention are all identical on structure is formed with first embodiment, its difference only is that the opening of various valves is different: wherein, remove first magnetic valve 13, second magnetic valve 14, the 8th magnetic valve 20, the 9th magnetic valve 21 the tenth magnetic valve 22, indoor air-cooled condenser (steam air heater) or indoor air-cooled evaporimeter (cold wind device) 4 are in outside the closed condition, and remaining part and magnetic valve all are in opening;
In Fig. 3, winter operation water heater endless form of the present invention is: discharged by the high pressure gas end of refrigeration compressor 1 through the HTHP mixed working fluid gas after refrigeration compressor 1 compression, after gs-oil separator 2 oil, gas separate, flow to the b interface by a interface in the first commutation three-way magnetic valve 3, in the 6th magnetic valve 18 flows into indoor water-cooled condensers (water heater) 12, be condensed into HTHP, the higher boiling worker quality liquid more than 70 ℃, and cooling water is heated into more than 55 ℃ can be for the have a bath hot water of usefulness of people.After cooled HTHP mixed working fluid fluid (fluid-mixing of higher boiling worker quality liquid and low boiling working fluid gas composition) flows out from indoor water-cooled condenser (water heater) 12, through the 7th magnetic valve 19, flow through m interface and the n interface passage that form of commutation in the four way solenoid valve 5 then, flow into from the top and carry out rectifying in the rectifying gas-liquid separator 6 and separate with gas, liquid;
The higher boiling worker quality liquid flow direction afterwards that is flowed out by rectifying gas-liquid separator 6 bottoms is identical with the flow direction of higher boiling worker quality liquid among the embodiment 2; The low boiling working fluid gas flow direction afterwards that flows out from the top of rectifying gas-liquid separator 6 is identical with low boiling working fluid gas flow direction the embodiment 2.
Condensation temperature can reach more than 70 ℃ in the above-mentioned circulatory system, and evaporating temperature reaches (20～-40) ℃, and the difference of evaporating temperature and condensation temperature will be above (80～90) ℃.Therefore, under so abominable service condition, have the mode that adopts higher boiling working medium of the present invention and the fractional condensaion of low boiling working fluid only, could guarantee above-mentioned heat pump cycle can be normally, move efficiently.
Referring to Fig. 4, be third embodiment of the present invention summer operation cold wind device and water heater kind of refrigeration cycle mode structural representation.
Embodiments of the invention are all identical on structure is formed with first embodiment, its difference is that the opening of each magnetic valve is different: wherein, remove the b interface in the first commutation three-way magnetic valve 3, g interface in the second commutation three-way magnetic valve 8, the 3rd magnetic valve 15, the 4th magnetic valve 16, the 5th magnetic valve 17, the 6th magnetic valve 18, the 7th magnetic valve 19, passage that o interface in passage that m interface in the commutation four way solenoid valve 5 and n interface form and the commutation four way solenoid valve 5 and p interface form and outdoor air-cooled evaporimeter or outdoor air-cooled condenser 11 are in outside the closed condition, and remaining part and magnetic valve etc. all is in opening;
In Fig. 4, the method of operation of the embodiment of the invention is: discharged by the high pressure gas end of refrigeration compressor 1 through the HTHP mixed working fluid gas after refrigeration compressor 1 compression, through gs-oil separator 2 oil, after gas separates, flow to the c interface by a interface in the first commutation three-way magnetic valve 3, flow in the indoor water-cooled condenser (instant heating hydrophone) 12 through the 8th magnetic valve 20, through the 9th magnetic valve 21, flow through p interface and the n interface passage that form of commutation in the four way solenoid valve 5 then, in top inflow rectifying gas-liquid separator 6, carry out rectifying and gas, liquid separates, higher boiling worker quality liquid after the separation flows out from the bottom of rectifying gas-liquid separator 6, through first throttle valve 7, then through e interface and f interface in the second commutation three-way magnetic valve 8, node x place with converge through the low boiling working fluid gas after 10 throttlings of second choke valve, flow through o interface and the m interface passage that form of commutation in the four way solenoid valve 5 then together, by second magnetic valve 14, in interior air-cooled condenser (steam air heater) of inlet chamber or the indoor air-cooled evaporimeter (cold wind device) 4, then by first magnetic valve 13 and the tenth magnetic valve 22, carry out heat exchange in the higher boiling worker quality liquid passage in the inflow heat exchanger 9, turn back to the low pressure air suction end of refrigeration compressor 1 at last;
Referring to Fig. 5, be fourth embodiment of the present invention summer operation cold wind device kind of refrigeration cycle mode structural representation.
Referring to Fig. 5, embodiments of the invention are all identical on structure is formed with first embodiment, its difference only is that the opening of various valves is different: wherein, remove the b interface in the first commutation three-way magnetic valve 3, g interface in the second commutation three-way magnetic valve 8, the 5th magnetic valve 17, the 6th magnetic valve 18, the 7th magnetic valve 19, the 8th magnetic valve 20, the 9th magnetic valve 21, passage and indoor water-cooled condenser 12 (instant heating hydrophone) that o interface in passage that m interface in the commutation four way solenoid valve 5 and n interface form and the commutation four way solenoid valve 5 and p interface form are in outside the closed condition, and remaining part and magnetic valve etc. all is in opening;
In Fig. 5, embodiments of the invention and the difference of the 3rd embodiment on the method for operation are: the HTHP mixed working fluid gas that flows to the c interface by a interface in the first commutation three-way magnetic valve 3, through the 4th magnetic valve 16, flow in the outdoor air-cooled evaporimeter (perhaps outdoor air-cooled condenser) 11, then by the 3rd magnetic valve 15, flow through p interface and the n interface passage that form of commutation in the four way solenoid valve 5, flow into from the top and carry out rectifying in the rectifying gas-liquid separator 6 and separate with gas, liquid.
The higher boiling worker quality liquid flow direction afterwards that is flowed out by rectifying gas-liquid separator 6 bottoms is identical with the flow direction of higher boiling worker quality liquid among the embodiment 4; The low boiling working fluid gas flow direction afterwards that flows out from the top of rectifying gas-liquid separator 6 is identical with low boiling working fluid gas flow direction the 3rd embodiment.
Referring to Fig. 6, be fifth embodiment of the present invention spring and autumn operation water heater endless form structural representation.
Referring to Fig. 6, embodiments of the invention are all identical on structure is formed with first embodiment, its difference is the difference of the opening of various valves: wherein, remove the c interface in the first commutation three-way magnetic valve 3, g interface in the second commutation three-way magnetic valve 8, the passage that m interface in the four-way reversing solenoid valve 5 and o interface form, the passage that n interface in the four-way reversing solenoid valve 5 and p interface form, first magnetic valve 13, second magnetic valve 14, the 8th magnetic valve 20, the 9th magnetic valve 21, the tenth magnetic valve 22 is in outside the closed condition, and remaining part and magnetic valve are in opening.
In Fig. 6, the method of operation of embodiments of the invention is: discharged by the high pressure gas end of refrigeration compressor 1 through the HTHP mixed working fluid gas after refrigeration compressor 1 compression, after gs-oil separator 2 oil, gas separate, by a interface and the b interface in the first commutation three-way magnetic valve 3, in the 6th magnetic valve 18 flows into indoor water-cooled condensers (water heater) 12, be condensed into HTHP, the higher boiling worker quality liquid more than 70 ℃, and cooling water is heated into more than 55 ℃ can be for the have a bath hot water of usefulness of people.After cooled HTHP mixed working fluid fluid (fluid-mixing of higher boiling worker quality liquid and low boiling working fluid gas composition) flows out from indoor water-cooled condenser (water heater) 12, through the 7th magnetic valve 19, flow through m interface and the n interface passage that form of commutation in the four way solenoid valve 5 then, flow into from the top and to carry out rectifying in the rectifying gas-liquid separator 6 and separate with gas, liquid, after higher boiling worker quality liquid after the separation flows out from the bottom of the gas-liquid separator 6 of rectifying, through first throttle valve 7, then by e interface and f interface in the second commutation three-way magnetic valve 8; The low boiling working fluid gas inflow heat exchanger 9 that flows out from the top of rectifying gas-liquid separator 6, after 10 throttlings of second magnetic valve, node x place with flow out from rectifying gas-liquid separator 6 bottoms and converge mutually through the higher boiling working medium fluid of first throttle valve 7 throttlings, flow through o interface and the p interface passage that form of commutation in the four way solenoid valve 5 together, and together through the 3rd magnetic valve 15, flow in the outdoor air-cooled evaporimeter (perhaps outdoor air-cooled condenser) 11, then through the 4th magnetic valve 16 and the 5th magnetic valve 17, carry out heat exchange in the higher boiling worker quality liquid passage in the inflow heat exchanger 9, at last, turn back to the low pressure air suction end of refrigeration compressor 1.
Claims (7)
1. a high-low temperature changeable graded evaporation air-conditioner heat pump water heater comprises refrigeration compressor (1), it is characterized in that, the refrigeration working medium of refrigeration compressor (1) is a hybrid refrigeration working medium;
The high pressure gas end of refrigeration compressor (1) is connected with gs-oil separator (2), the first commutation three-way magnetic valve (3), first magnetic valve (13), indoor air-cooled condenser or indoor air-cooled evaporimeter (4), second magnetic valve (14) in turn; Indoor air-cooled condenser or indoor air-cooled evaporimeter (4) are connected with commutation four way solenoid valve (5) on the one hand by second magnetic valve (14), and are connected with rectifying gas-liquid separator (6) by this commutation four way solenoid valve (5); The top of rectifying gas-liquid separator (6) directly is connected with the gas pipeline arrival end of heat exchanger (9); The bottom of rectifying gas-liquid separator (6) is connected with the arrival end of the fluid pipeline of first throttle valve (7), second commutation three-way magnetic valve (8) and heat exchanger (9) successively by tube connector; The port of export of the fluid pipeline of heat exchanger (9) directly is connected with the low pressure air suction end of refrigeration compressor (1); The port of export of the gas pipeline of heat exchanger (9) is connected with the second commutation three-way magnetic valve (8) on the one hand by second choke valve (10) on the pipeline, is connected with commutation four way solenoid valve (5) on the other hand;
Second magnetic valve (14) also is connected by the port of export of the 7th magnetic valve (19) with indoor water-cooled condenser (12), and the arrival end of indoor water-cooled condenser (12) is connected with the first commutation three-way magnetic valve (3) by the 6th magnetic valve (18);
An interface of commutation four way solenoid valve (5) is connected by the port of the 3rd magnetic valve (15) on the pipeline with outdoor air-cooled evaporimeter or outdoor air-cooled condenser (11), perhaps is connected by the port of export of the 9th magnetic valve (21) with indoor water-cooled condenser (12);
Another port of outdoor air-cooled evaporimeter or outdoor air-cooled condenser (11) is connected with the arrival end of the 8th magnetic valve (20) with indoor water-cooled condenser (12) by the 4th magnetic valve (16), perhaps is connected with the fluid pipeline arrival end of the 5th magnetic valve (17) with heat exchanger (9) by the 4th magnetic valve (16);
The fluid pipeline arrival end of heat exchanger (9) also is connected with the first commutation three-way magnetic valve (3) by the tenth magnetic valve (22).
2. high-low temperature changeable graded evaporation air-conditioner heat pump water heater as claimed in claim 1, it is characterized in that, described hybrid refrigeration working medium is made up of higher boiling, mid-boiling point, three kinds of working medium of low boiling, they are chosen in higher boiling group, mid-boiling point group, low boiling group respectively, perhaps only therein the higher boiling group and the low boiling group in choose, form bi-component, three components or mostly be the environment-friendly type hybrid refrigeration working medium of four components most.
3. high-low temperature changeable graded evaporation air-conditioner heat pump water heater as claimed in claim 1 is characterized in that, the high pressure of described refrigeration compressor is in 4～12 with the ratio of low pressure.
4. high-low temperature changeable graded evaporation air-conditioner heat pump water heater as claimed in claim 1 is characterized in that, described indoor air-cooled condenser or indoor air-cooled evaporimeter, and indoor air-cooled condenser wherein is a steam air heater, indoor air-cooled evaporimeter is the cold wind device.
5. high-low temperature changeable graded evaporation air-conditioner heat pump water heater as claimed in claim 1 is characterized in that, described indoor water-cooled condenser is a water heater.
6. high-low temperature changeable graded evaporation air-conditioner heat pump water heater as claimed in claim 1 is characterized in that, described outdoor air-cooled evaporimeter or outdoor air-cooled condenser, and outdoor air-cooled evaporimeter wherein is an evaporimeter, outdoor air-cooled condenser is a condenser.
7. high-low temperature changeable graded evaporation air-conditioner heat pump water heater as claimed in claim 1, it is characterized in that: by the first commutation three-way magnetic valve (3), the second commutation three-way magnetic valve (8), commutation four way solenoid valve (5), first magnetic valve (13), second magnetic valve (14), the 3rd magnetic valve (15), the 4th magnetic valve (16), the 5th magnetic valve (17), the 6th magnetic valve (18), the 7th magnetic valve (19), the 8th magnetic valve (20), the 9th magnetic valve (21), the tenth magnetic valve (22) is in different openings respectively, can realize the mutual switching between winter operation steam air heater heat pump cycle mode or winter operation water heater heat pump cycle mode or summer operation cold wind device and water heater kind of refrigeration cycle mode or summer operation cold wind device kind of refrigeration cycle mode or the spring and autumn operation water heater heat pump cycle mode.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNB2005100964243A CN100402949C (en) | 2005-11-25 | 2005-11-25 | High-low temperature changeable graded evaporation air-conditioner heat pump water heater |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNB2005100964243A CN100402949C (en) | 2005-11-25 | 2005-11-25 | High-low temperature changeable graded evaporation air-conditioner heat pump water heater |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1776325A true CN1776325A (en) | 2006-05-24 |
| CN100402949C CN100402949C (en) | 2008-07-16 |
Family
ID=36765973
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB2005100964243A Expired - Fee Related CN100402949C (en) | 2005-11-25 | 2005-11-25 | High-low temperature changeable graded evaporation air-conditioner heat pump water heater |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN100402949C (en) |
Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101512254B (en) * | 2006-09-12 | 2012-12-05 | 开利公司 | Anti-season startup for improving refrigeration system reliability |
| CN101660850B (en) * | 2008-08-27 | 2012-12-26 | Lg电子株式会社 | Air conditioning system |
| CN101660849B (en) * | 2008-08-27 | 2013-08-07 | Lg电子株式会社 | Air conditioner system |
| CN103983044A (en) * | 2014-05-28 | 2014-08-13 | 广东志高暖通设备股份有限公司 | Air cooled heat pump unit |
| CN105276864A (en) * | 2014-07-10 | 2016-01-27 | 南京理工大学 | Variable-component refrigerant heat pump hot water unit |
| CN108386936A (en) * | 2018-02-05 | 2018-08-10 | 冯卓林 | A kind of hidden air conditioner |
| CN108775729A (en) * | 2018-08-13 | 2018-11-09 | 瀚润联合高科技发展（北京）有限公司 | Evaporate cold and hot pump assembly |
| CN112228983A (en) * | 2020-10-15 | 2021-01-15 | 东南大学 | Heat-humidity ratio adjustable radiation cooling and fresh air integrated system and operation method |
Family Cites Families (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP3655681B2 (en) * | 1995-06-23 | 2005-06-02 | 三菱電機株式会社 | Refrigerant circulation system |
| JPH1047812A (en) * | 1996-08-06 | 1998-02-20 | Saginomiya Seisakusho Inc | Control for valve and control for refrigerating cycle |
| CN1091239C (en) * | 1996-12-25 | 2002-09-18 | 中国科学院低温技术实验中心 | High and low temperature switching valve type impulse pipe expander refrigeration liquefying flow path and device |
| JP2001317831A (en) * | 2000-05-08 | 2001-11-16 | Matsushita Electric Ind Co Ltd | Air conditioner |
| JP4911847B2 (en) * | 2001-09-26 | 2012-04-04 | ダイキン工業株式会社 | Solenoid valve control device and air conditioner equipped with solenoid valve control device |
-
2005
- 2005-11-25 CN CNB2005100964243A patent/CN100402949C/en not_active Expired - Fee Related
Cited By (13)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101512254B (en) * | 2006-09-12 | 2012-12-05 | 开利公司 | Anti-season startup for improving refrigeration system reliability |
| CN101660850B (en) * | 2008-08-27 | 2012-12-26 | Lg电子株式会社 | Air conditioning system |
| CN101660849B (en) * | 2008-08-27 | 2013-08-07 | Lg电子株式会社 | Air conditioner system |
| US9127865B2 (en) | 2008-08-27 | 2015-09-08 | Lg Electronics Inc. | Air conditioning system including a bypass pipe |
| CN103983044A (en) * | 2014-05-28 | 2014-08-13 | 广东志高暖通设备股份有限公司 | Air cooled heat pump unit |
| CN105276864B (en) * | 2014-07-10 | 2018-01-05 | 南京理工大学 | One kind becomes component refrigerants heat-pump hot-water unit |
| CN105276864A (en) * | 2014-07-10 | 2016-01-27 | 南京理工大学 | Variable-component refrigerant heat pump hot water unit |
| CN108386936A (en) * | 2018-02-05 | 2018-08-10 | 冯卓林 | A kind of hidden air conditioner |
| CN108386936B (en) * | 2018-02-05 | 2020-10-09 | 冯卓林 | Hidden air conditioner |
| CN108775729A (en) * | 2018-08-13 | 2018-11-09 | 瀚润联合高科技发展（北京）有限公司 | Evaporate cold and hot pump assembly |
| CN108775729B (en) * | 2018-08-13 | 2023-12-19 | 瀚润联合高科技发展（北京）有限公司 | Evaporation cold heat pump unit |
| CN112228983A (en) * | 2020-10-15 | 2021-01-15 | 东南大学 | Heat-humidity ratio adjustable radiation cooling and fresh air integrated system and operation method |
| CN112228983B (en) * | 2020-10-15 | 2021-12-10 | 东南大学 | Heat-humidity ratio adjustable radiation cooling and fresh air integrated system and operation method |
Also Published As
| Publication number | Publication date |
|---|---|
| CN100402949C (en) | 2008-07-16 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN1776325A (en) | High-low temperature changeable graded evaporation air-conditioner heat pump water heater | |
| CN1108502C (en) | Air conditioner apparatus | |
| CN101603749B (en) | Auto-cascade injection low-temperature refrigeration circulating device | |
| CN104048447B (en) | A kind of refrigeration system that is core with Michel Knuysen compressor | |
| CN1757991A (en) | Air-conditioner with a dual-refrigerant circuit | |
| CN101713599A (en) | Air-conditioning heat pump device | |
| CN101387454B (en) | Multifunctional CO2 air conditioner heat pump | |
| CN109916109A (en) | Heat pump system and air conditioner | |
| CN108318273B (en) | Multicycle heat pump experiment table | |
| CN1121168A (en) | Energy-saving double-temp. refrigerant method and system | |
| CN106225296A (en) | A kind of commutation defrosting net for air-source heat pump units and commutation Defrost method | |
| CN1205073A (en) | Air conditioner | |
| CN109163470A (en) | A kind of ultralow temperature carbon dioxide water chiller-heater unit | |
| CN107883600B (en) | One-driving-two air conditioning system | |
| CN210486159U (en) | Heat pump system | |
| CN2702223Y (en) | Dual purpose type air-conditioning and water heating apparatus | |
| CN2869685Y (en) | Over-cold throttling graded condensation type heat-pump water heater | |
| CN201964610U (en) | Air source and water source heat pump hot water unit | |
| CN102759219B (en) | Energy-saving heat pump hot water air conditioner and working method thereof | |
| CN1228588C (en) | Combined air-cooled heat pump unit | |
| CN208671233U (en) | Distributed air conditioner with air-source heat pump | |
| CN110173912B (en) | Mixed working medium compression circulation system with mechanical heat recovery function and working method | |
| CN1158494C (en) | Multistage absorption type refrigerating apparatus | |
| CN2542969Y (en) | Combined air-cooled heat pump unit | |
| CN102878620B (en) | A kind of two-phase flow refrigeration system |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20080716 Termination date: 20151125 |
|
| CF01 | Termination of patent right due to non-payment of annual fee |