CN101949585A - Dual-heat source jet enthalpy addition heat pump water heater - Google Patents
Dual-heat source jet enthalpy addition heat pump water heater Download PDFInfo
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- CN101949585A CN101949585A CN 201010255652 CN201010255652A CN101949585A CN 101949585 A CN101949585 A CN 101949585A CN 201010255652 CN201010255652 CN 201010255652 CN 201010255652 A CN201010255652 A CN 201010255652A CN 101949585 A CN101949585 A CN 101949585A
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Abstract
The invention relates to a dual-heat source jet enthalpy addition heat pump water heater, which comprises a main machine with a condenser, a four-way valve and a controller, a heat storage and insulation water tank, a finned evaporator and a main expansion valve, and is characterized by comprising a plate type evaporator, a first electromagnetic valve and a second electromagnetic valve, wherein the liquid inlet of the finned evaporator is connected with the first electromagnetic valve; the liquid inlet of the plate type evaporator is connected with the second electromagnetic valve; and the first electromagnetic valve is connected in parallel with the second electromagnetic valve and then is connected with the main expansion valve. Only one plate type evaporator and two electromagnetic valves are arranged on the basis of one air source heat pump water heater, so the same using effect of two pieces of equipment, namely one air source heat pump water heater and one water source heat pump water heater can be achieved, cost and floor area are saved, and the dual-heat source jet enthalpy addition heat pump water heater has the advantages of wide application range, high reliability, energy conservation and the like.
Description
Technical field
The present invention relates to hot water apparatus, be specifically a kind of be the air injection enthalpy-increasing Teat pump boiler of thermal source with air heat source or water source.Belong to energy class heat supply process field.
Background technology
What generally sell on China Teat pump boiler market at present mainly is two kinds of air source hot pump water heater and water source heat pump water heaters.
Under the conventional weather, environment temperature is far above water temperature, and air source hot pump water heater produces same temperature hot water, and the power that is consumed is than low many of water source heat pump water heater.
And in the northern area of China, cold season in winter, environment temperature was all about-15 ℃, and water temperature generally remains on more than 10 ℃, and north of china in winter one continued 4 months, air source hot pump water heater produces same temperature hot water, and the power that is consumed is than high many of water source heat pump water heater.Though in spring, summer, three seasons of autumn, air source hot pump water heater still can satisfy instructions for use in the north, but in the winter of cold, air source hot pump water heater is but because consumed power is too high, make the people forbidding, that is to say that air source hot pump water heater can not satisfy annual instructions for use in the north, use and energy-conservation aspect be subjected to great restriction, the northerly popularization of air source hot pump water heater is faced a severe test.
Summary of the invention
Content of the present invention can not satisfy annual instructions for use problem at the defective that exists in the prior art at air source hot pump water heater in the north, having provided a kind of air source and water source is two thermal source air injection enthalpy-increasing Teat pump boilers of thermal source.
For reaching above purpose, the technical scheme that the present invention takes is: a kind of pair of thermal source air injection enthalpy-increasing Teat pump boiler, comprise the main frame, the heat storing and heat preserving water tank that contain condenser, cross valve and controller, finned evaporator, main expansion valve, comprise plate-type evaporator, first magnetic valve, second magnetic valve, the inlet of finned evaporator is connected with first magnetic valve, the inlet of plate-type evaporator is connected with second magnetic valve, and first magnetic valve is in parallel with second magnetic valve, and back in parallel is connected with main expansion valve.
Wherein, the controller of main frame adopts Single-chip Controlling.
Cross valve D to, connect compressor exhaust pipe by high-voltage switch gear.
Cross valve C is to connecing the condenser air inlet.
Cross valve S to by vapour liquid separator, low tension switch, connect the compressor air suction mouth.
Cross valve E is to connecing finned evaporator and plate-type evaporator gas outlet respectively.
Wherein, the refrigerant outlet of condenser is successively through being divided into main line and two pipelines of auxilliary pipeline behind reservoir, the device for drying and filtering.
Main line is directly connected to the main road inlet of economizer, the outlet of the main road of economizer through behind the main expansion valve respectively with first magnetic valve, second magnetic valve connects, first magnetic valve is connected with the inlet of finned evaporator, second magnetic valve is connected with the inlet of plate-type evaporator, first magnetic valve is in parallel with second magnetic valve, and back in parallel is connected with main expansion valve.
Auxilliary pipeline enters the mouth through the bypass that electromagnetic expanding valve is connected to economizer, and the bypass outlet of economizer is connected to the auxilairy air intake of compressor.
Wherein, heat storing and heat preserving water tank upper and lower part is provided with the hot-water circulation pipe respectively, and the hot-water circulation pipe on top is connected with the hot water outlet of condenser, and the hot-water circulation pipe of bottom is connected with the water inlet of hot water of condenser by water circulating pump.
The heat storing and heat preserving water tank adopts nonbearing structure, and its inlet pipeline can be connected with the running water pipe network by entering water electromagnetic valve.
Wherein, the importation of controller comprises: environment temperature sensor, coil temperature sensor, water tank temperature sensor, high-voltage switch gear, low tension switch.
The output of controller is used for controlling with lower member: water circulating pump, compressor, blower fan, cross valve, electromagnetic expanding valve, first magnetic valve, second magnetic valve.
Wherein, the coil pipe of finned evaporator is provided with the coil temperature sensor that is connected with controller, and controller also is connected with environment temperature sensor, water tank temperature sensor.
By above technical scheme, the user is on an air source hot pump water heater basis, only increase a plate-type evaporator, 2 magnetic valves, just can reach the same result of use of an air source hot pump water heater and a water source heat pump water heater, two equipment, save cost and take up an area of usable floor area.Have full season, round-the-clock, applied widely, reliability is high, advantage such as energy-conservation.
Description of drawings
The present invention has the structural representation of the two thermal source air injection enthalpy-increasing Teat pump boilers of following accompanying drawing: Fig. 1; The refrigerant flow direction figure of air injection enthalpy-increasing Teat pump boiler during Fig. 2 air source; The refrigerant flow direction figure of air injection enthalpy-increasing Teat pump boiler during Fig. 3 water source.
Reference numeral: 1, compressor, 2, high-voltage switch gear, 3, cross valve, 4, condenser, 5, reservoir, 6, device for drying and filtering, 7, electromagnetic expanding valve, 8, economizer, 9, main expansion valve, 10, finned evaporator, 11, vapour liquid separator, 12, low tension switch, 13, the heat storing and heat preserving water tank, 14, water circulating pump, 15, hot-water circulation pipe, 16, blower fan, 17, second magnetic valve, 18, first magnetic valve, 19, plate-type evaporator, 20, controller, 21, environment temperature sensor, 22, coil temperature sensor, 23, the water tank temperature sensor.
The specific embodiment
Below in conjunction with accompanying drawing the present invention is described in further detail.
The present invention relates to a kind of pair of thermal source air injection enthalpy-increasing Teat pump boiler, belong to energy class heat supply process field.
Fig. 1 is the structural representation of of the present invention pair of thermal source air injection enthalpy-increasing Teat pump boiler, and among Fig. 1, on behalf of heat source water, dotted arrow flow to, solid arrow represent flow of hot water to.
A kind of pair of thermal source air injection enthalpy-increasing Teat pump boiler of the present invention, comprise the main frame, the heat storing and heat preserving water tank 13 that contain condenser 4, cross valve 3 and controller 20, finned evaporator 10, main expansion valve 9 comprises plate-type evaporator 19, first magnetic valve, 18, the second magnetic valves 17, the inlet of finned evaporator 10 is connected with first magnetic valve 18, the inlet of plate-type evaporator 19 is connected with second magnetic valve 17, and first magnetic valve 18 is in parallel with second magnetic valve 17, and back in parallel is connected with main expansion valve 9.
Finned evaporator 10 is supporting blower fan 16.
Described controller 20 adopts Single-chip Controlling.
Cross valve 3D is to connect compressor 1 blast pipe by high-voltage switch gear 2.
Cross valve 3C is to connecing condenser 4 air inlets.
Cross valve 3S is to connecing compressor 1 air entry by vapour liquid separator 11, low tension switch 12.
Cross valve 3E is to connecing respectively to finned evaporator 10 and plate-type evaporator 19 gas outlets.
The refrigerant outlet of condenser 4 is successively through being divided into main line and two pipelines of auxilliary pipeline behind reservoir 5, the device for drying and filtering 6.
Main line is directly connected to the main road inlet of economizer 8, the main road outlet of economizer 8 through behind the main expansion valve 9 respectively with magnetic valve 17, magnetic valve 18 connects.The inlet of finned evaporator (10) is connected with first magnetic valve (18), and the inlet of plate-type evaporator (19) is connected with second magnetic valve (17), and first magnetic valve (18) is in parallel with second magnetic valve (17), and back in parallel is connected with main expansion valve 9.
Auxilliary pipeline enters the mouth through the bypass that electromagnetic expanding valve 7 is connected to economizer 8, and the bypass outlet of economizer 8 is connected to the auxilairy air intake of compressor 1.
Heat storing and heat preserving water tank 13 upper and lower parts are provided with hot-water circulation pipe 15 respectively, and the hot-water circulation pipe 15 on top is connected with the hot water outlet of condenser 4, and the hot-water circulation pipe 15 of bottom is connected with the water inlet of hot water of condenser 4 by water circulating pump 14.
Heat storing and heat preserving water tank 13 adopts nonbearing structure, and its inlet pipeline can be connected (not shown) with the running water pipe network by entering water electromagnetic valve.
The importation of controller 20 comprises: environment temperature sensor 21, coil temperature sensor 22, water tank temperature sensor 23, low tension switch 12, high-voltage switch gear 2.
The output of controller 20 is used for controlling with lower member: water circulating pump 14, compressor 1, blower fan 16, cross valve 3, auxiliary selenoid expansion valve 7, magnetic valve 17, magnetic valve 18.
The coil pipe of finned evaporator 10 is provided with the coil temperature sensor 22 that is connected with controller 20, and controller 20 also is connected with environment temperature sensor 21, water tank temperature sensor 23.
The present invention has two kinds of mode of operations, summer " air source " heating mode and winter " water source " heating mode, therefore one have two kinds of cold-producing medium endless form, below in conjunction with accompanying drawing each endless form is illustrated one by one.
Summer " air source " heating mode: referring to Fig. 2, when environment temperature is higher than water temperature, on controller 20, select in " air source ".
The concrete course of work is as follows: at this moment, finned evaporator 10 circuit electromagnetic valves 18 are opened, and plate-type evaporator 19 circuit electromagnetic valves 17 cut out.
In finned evaporator 10, the refrigerant liquid of low-temp low-pressure absorbs the heat in the surrounding air in finned evaporator 10, flash to the refrigerant gas of low-temp low-pressure, the refrigerant gas of low-temp low-pressure enters cross valve 3E backward,, after coming out, sucked from cross valve 3S by compressor 1 air entry.
Cold-producing medium by compressor 1 be compressed into high temperature and high pressure gas enter cross valve 3D to, after going out, enter condenser 4 from cross valve 3C, in condenser 4, be condensed into the cryogenic high pressure refrigerant liquid and discharge a large amount of heats, water absorbs the heat of its release and temperature constantly rises, to reach the purpose that produces hot water.
The high pressure refrigerant liquid of coming out from condenser 4 is through reservoir 5, by being divided into main road and bypass two-way behind the device for drying and filtering 6.
The cold-producing medium of main road directly enters in the economizer 8.
The cold-producing medium of bypass also enters in the economizer after through electromagnetic expanding valve 7 throttling step-downs becoming gas-liquid mixture, and the two produces heat exchange in economizer, is sucked by the auxilairy air intake of compressor 1 after becoming gas after the refrigerant liquid heat absorption of bypass.The cold-producing medium heat release of main road becomes subcooled liquid and enters finned evaporator 10 by magnetic valve 18 after by main expansion valve 9 throttling step-downs.
In finned evaporator 10, cold-producing medium absorbs behind the heat in the low temperature environment and becomes low-pressure gas and enter cross valve 3E backward, is sucked by compressor 1 air entry to the back of coming out from cross valve 3S.
The cold-producing medium of main road and bypass mixes in compressor 1 working chamber, and further discharge the compression back again, constitutes the working cycles loop of sealing.
Winter " water source " heating mode, referring to Fig. 3, the concrete course of work is as follows: when environment temperature is lower than water temperature in the winter time, select on controller at " water source ".
At this moment, fin formula evaporimeter 10 circuit electromagnetic valves 18 cut out, and plate-type evaporator 19 circuit electromagnetic valves 17 are opened.
The refrigerant liquid of low-temp low-pressure absorbs the heat in the heat source water in plate-type evaporator 19, flash to the refrigerant gas of low-temp low-pressure, and the refrigerant gas of low-temp low-pressure enters cross valve 3E backward,, is sucked by compressor 1 air entry after coming out from cross valve 3S.
The refrigerant gas of low-temp low-pressure is compressed into high temperature and high pressure gas by compressor 1 and enters cross valve 3D to entering condenser 4 from cross valve 3C after going out, in condenser 4, be condensed into the cryogenic high pressure refrigerant liquid and discharge a large amount of heats, water absorbs the heat of its release and temperature constantly rises, to reach the purpose that produces hot water.
The high pressure refrigerant liquid of coming out from condenser 4 is through reservoir 5, by being divided into two-way behind the device for drying and filtering 6.
The cold-producing medium that the cold-producing medium of main road directly enters bypasses in the economizer 8 also enters in the economizer 8 after becoming gas-liquid mixture after through electromagnetic expanding valve 7 throttling step-downs, the two produces heat exchange in economizer 8, sucked by the auxilairy air intake of compressor 1 after becoming gas after the refrigerant liquid heat absorption of bypass, the cold-producing medium heat release of main road becomes subcooled liquid and enters plate-type evaporator 19 by magnetic valve 17 after by main expansion valve 9 throttling step-downs.
In plate-type evaporator 19, the cold-producing medium of main road absorbs behind the heat in the heat source water and becomes low-pressure gas and enter cross valve 3E backward, is sucked by compressor 1 air entry to the back of coming out from cross valve 3S.
The cold-producing medium of main road and bypass mixes in compressor 1 working chamber, and further discharge the compression back again, constitutes the working cycles loop of sealing.
Claims (1)
1. two thermal source air injection enthalpy-increasing Teat pump boiler, comprise and contain condenser (4), the main frame of cross valve (3) and controller (20), heat storing and heat preserving water tank (13), finned evaporator (10), main expansion valve (9), it is characterized in that: comprise plate-type evaporator (19), first magnetic valve (18), second magnetic valve (17), the inlet of finned evaporator (10) is connected with described first magnetic valve (18), the inlet of plate-type evaporator (19) is connected with described second magnetic valve (17), described first magnetic valve (18) is in parallel with second magnetic valve (17), and back in parallel is connected with described main expansion valve (9).
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| CN 201010255652 CN101949585A (en) | 2010-08-17 | 2010-08-17 | Dual-heat source jet enthalpy addition heat pump water heater |
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| CN 201010255652 CN101949585A (en) | 2010-08-17 | 2010-08-17 | Dual-heat source jet enthalpy addition heat pump water heater |
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Cited By (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102419025A (en) * | 2011-11-30 | 2012-04-18 | 合肥凌达压缩机有限公司 | Two-stage enthalpy-increasing air-conditioning system |
| CN102538273A (en) * | 2012-02-10 | 2012-07-04 | 海信（山东）空调有限公司 | Vapor-injected air-conditioning system, vapor-injected air-conditioning control method and air-conditioner |
| CN104457070A (en) * | 2014-05-21 | 2015-03-25 | 林志辉 | Method for controlling efficient operation of heat pump and heat pump system with multiple heat exchange and enthalpy increment |
| CN104964484A (en) * | 2015-08-01 | 2015-10-07 | 山东东德石油装备有限公司 | Multifunctional heating device of oil field double-source heat pump |
| CN106949666A (en) * | 2017-05-12 | 2017-07-14 | 中冶华天南京工程技术有限公司 | Heat pump and its control method |
| CN106996660A (en) * | 2017-05-17 | 2017-08-01 | 南京工程学院 | Big temperature difference Double-head heat pump based on heat source tower Yu underground pipe cooperation |
| CN107044730A (en) * | 2017-06-20 | 2017-08-15 | 合肥天鹅制冷科技有限公司 | Low-temperature air source heat pump preparing high-temp hot water facility |
| CN108518774A (en) * | 2018-04-19 | 2018-09-11 | 广东美的暖通设备有限公司 | Air-conditioning water heater system |
| CN109163367A (en) * | 2018-09-06 | 2019-01-08 | 大连民族大学 | A kind of air-source with second vapor injection-water source combined heat-pump heat supply method |
| CN110455004A (en) * | 2019-07-20 | 2019-11-15 | 深圳市辉宏技术有限公司 | The cold and hot balance unit of double source |
| CN110455005A (en) * | 2019-07-20 | 2019-11-15 | 深圳市辉宏技术有限公司 | A kind of cold and hot balance unit of double source |
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| CN101077269A (en) * | 2007-06-27 | 2007-11-28 | 王全龄 | Heat energy pump type boiled water and cold water drinking machine |
| CN201314700Y (en) * | 2008-10-28 | 2009-09-23 | 深圳市协诚机电设备工程有限公司 | Water heater for double-source heat pump |
| CN101476774A (en) * | 2008-11-18 | 2009-07-08 | 浙江正理电子电气有限公司 | Double-heat source heat pump water heater with air source and water source |
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Cited By (13)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102419025A (en) * | 2011-11-30 | 2012-04-18 | 合肥凌达压缩机有限公司 | Two-stage enthalpy-increasing air-conditioning system |
| CN102419025B (en) * | 2011-11-30 | 2013-10-23 | 合肥凌达压缩机有限公司 | Two-stage enthalpy-increasing air-conditioning system |
| CN102538273A (en) * | 2012-02-10 | 2012-07-04 | 海信（山东）空调有限公司 | Vapor-injected air-conditioning system, vapor-injected air-conditioning control method and air-conditioner |
| CN104457070A (en) * | 2014-05-21 | 2015-03-25 | 林志辉 | Method for controlling efficient operation of heat pump and heat pump system with multiple heat exchange and enthalpy increment |
| CN104457070B (en) * | 2014-05-21 | 2017-06-06 | 林志辉 | Heat pump with multiple heat interchange increasing enthalpy |
| CN104964484A (en) * | 2015-08-01 | 2015-10-07 | 山东东德石油装备有限公司 | Multifunctional heating device of oil field double-source heat pump |
| CN106949666A (en) * | 2017-05-12 | 2017-07-14 | 中冶华天南京工程技术有限公司 | Heat pump and its control method |
| CN106996660A (en) * | 2017-05-17 | 2017-08-01 | 南京工程学院 | Big temperature difference Double-head heat pump based on heat source tower Yu underground pipe cooperation |
| CN107044730A (en) * | 2017-06-20 | 2017-08-15 | 合肥天鹅制冷科技有限公司 | Low-temperature air source heat pump preparing high-temp hot water facility |
| CN108518774A (en) * | 2018-04-19 | 2018-09-11 | 广东美的暖通设备有限公司 | Air-conditioning water heater system |
| CN109163367A (en) * | 2018-09-06 | 2019-01-08 | 大连民族大学 | A kind of air-source with second vapor injection-water source combined heat-pump heat supply method |
| CN110455004A (en) * | 2019-07-20 | 2019-11-15 | 深圳市辉宏技术有限公司 | The cold and hot balance unit of double source |
| CN110455005A (en) * | 2019-07-20 | 2019-11-15 | 深圳市辉宏技术有限公司 | A kind of cold and hot balance unit of double source |
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Application publication date: 20110119 |