CN103994505A - Exhaust air source heat pump fresh air driving system - Google Patents

Exhaust air source heat pump fresh air driving system Download PDF

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Publication number
CN103994505A
CN103994505A CN201410137954.7A CN201410137954A CN103994505A CN 103994505 A CN103994505 A CN 103994505A CN 201410137954 A CN201410137954 A CN 201410137954A CN 103994505 A CN103994505 A CN 103994505A
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heat
source
air
heat exchanger
new wind
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CN201410137954.7A
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侴乔力
侴雨宏
魏蔚
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侴乔力
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Abstract

Disclosed is an exhaust air source heat pump fresh air driving system. An evaporator and a condenser of a heat pump unit are used for driving a heat source side exhaust air source heat recovery duct tank to deeply recover total heat of exhaust air and process the exhaust air to approximate the environmental working condition so as to reduce environmental heat pollution, and meanwhile driving a use side fresh air processing duct tank to deeply process the fresh air to approximate the indoor working condition in a cooling and heating combined mode. The inherent contradiction that energy consumption of an air conditioner is certainly increased when fresh air volume is increased is overcome; the energy conservation and emission reduction effects of the air conditioner are improved efficiently and largely; a fresh air port and an exhaust air port are separated, so that the fresh air is prevented from making contact with the exhaust air and causing cross pollution; the standardized design and manufacturing of exhaust air heat recovery equipment are achieved.

Description

Row's wind source heat pump drives the system of new wind
(1) technical field
The present invention relates to a kind of system that wind source heat pump drives new wind of arranging, by circulating refrigerant in air exhaust heat exchange device, reclaim air draft sensible heat and latent heat, and promote its hot/cold amount grade by source pump, to realize the water capacities such as winter, heat new wind, the air conditioner fresh air power-saving technology of dehumidifying in summer, cooling new wind.
(2) background technology
(1) building consumes half electric energy of the whole world, and air-conditioning and heating consume half electric energy of building, and air-conditioning and the heating of the U.S., Japan consume 1/3 of its total electric energy, and Sweden even consumes 45% of its total electric energy;
(2) produce extremely toxic substance and germ, and distribute radioactive building, owing to there is severe contamination, cannot utilize return air, have to adopt single flow air-conditioning, therefore with huge exhaust air rate, lose huge heat;
(3) in the air return type air-conditioning of the public building such as machine room, arenas, hospital, supermarket, because resh air requirement is huge; The temperature of air draft simultaneously, humidity approach indoor design operating mode most, are that new wind is processed and mixed desired value, so in air draft, contain a large amount of available heats;
(4) in common air return type air-conditioning because exhaust air rate is less, cause new wind to reclaim air draft heat limited, therefore can between return air process chamber back segment and new wind air channel, arrange complete hot regenerator, utilize summer 37-40 ℃ of full heat of new wind to heat 12-14 ℃ of dew point return air, not only reduced again that thermoelectricity consumes but also the new wind of cooling processing;
(5) new wind suction chamber outer air, air draft exhalation room air, forms the breathing of building, by changing wind, maintains indoor air quality; Existing new wind unit in summer is by electric refrigerated dehumidification, cooling new wind, and heat new wind by water capacities such as electric heating pumps winter; Its new wind load accounts for air conditioner load can reach 20-30%, therefore utilizes new wind to reclaim air draft heat to meet new wind load, is the effective conservation measures of air-conditioning system.Saving the new wind of 70-80% and process the operation of air conditioner electricity charge that power consumption is amounted to saving 10-20%, is the important channel that reduces air-conditioning power consumption.
And existing new wind reclaims air draft heat technique, be mainly divided into following several form:
1, flat sensible heat exchanger: the metal of interlaced arrangement spacing 4-8mm or Plastic Flat andante, new wind reclaims the air draft sensible heat of another side by central dividing plate, because new air-dry bulb temperature can not be lower than air draft dew point, otherwise air draft meeting produces condensate water even freezes and increases exhaust resistance, affects its service life.For avoiding air draft dewfall, can only reclaim air draft sensible heat, therefore regulate air quantity only in 40-60% scope, to change its sensible heat organic efficiency η, make independently to realize operation of air conditioner as unit; In addition new wind and exhaust duct need centralized arrangement, easily between fresh inlet and wind exhausting outlet, go here and there wind; Because new wind does not contact air draft, avoid air cross pollution of opening and shaft; Equipment no-rotary part makes reliable; The air draft sensible heat of the recyclable >50kW of flat sensible heat exchanger, can be used for large resh air requirement air-conditioning because cost is low.
2, plate-fin total-heat exchanger: control new wind warm, that humidity is different and air draft alternating current through two groups of plate-fin air channels, imitate the two lungs of human body and suck new wind, exhalation air draft, form rhythmical building and breathe, to change room air; Wherein utilize the thermal capacitance accumulation of heat of plate wing and surperficial hygroscopic effect and become full heat exchange carrier, between new wind and air draft, transmit air sensible heat and latent heat, maintain heat, the wet condition of room air, can realize the total heat recovery efficiency η of 60-70%, but cannot independently realize operation of air conditioner.
Switching import/export air-valve according to plate wing temperature summer between new wind dew point and temperature of outgoing air, makes plate wing periodically to dry and cold air draft, discharge sensible heat as full heat carrier, and discharge evaporation latent heat to surperficial moisture film, makes after air draft intensification, humidification outside discharge chamber; Plate wing is cooled and cools to temperature of outgoing air; Switch according to this import/export air-valve, so that plate wing absorbs sensible heat and the dewfall latent heat of damp and hot new wind, make to be sent to after new wind cooling, dehumidifying indoor, maintain the dry and cold state of air, reduce new wind load; Plate and fin surface forms moisture film and heats to new wind dew point.
Switch import/export air-valve according to plate wing temperature winter between new air temperature and air draft dew point, make plate wing periodically to dry and cold new wind, discharge sensible heat as full heat carrier, and discharge evaporation latent heat to surperficial moisture film, make that new wind heats up, send into after humidification indoor, maintain the humid tropical condition of air, reduce new wind load; Plate wing is cooled and cools to new air temperature; Switch according to this import/export air-valve, so that plate wing absorbs sensible heat and the dewfall latent heat of damp hot discharge air, make outside air draft cooling, the rear discharge chamber of dehumidifying; Plate and fin surface forms moisture film and heats to air draft dew point.
Follow plate and fin surface periodically condensation water film and evaporation thereof, cause: the cross pollution such as bacterium, microorganism, impurity in (1) new wind and air draft; (2) unit total heat recovery efficiency is high and low, depends on enthalpy difference between new wind and air draft; (3) rotatable parts such as import/export air-valve reduce equipment operational reliability; (4) air-valve switching cycle in import/export arranges improperly, can cause plate and fin surface frosting; (5) new wind and exhaust duct centralized arrangement, easily form fresh inlet and wind exhausting outlet string wind; (6) plate wing and import/export air-valve all need nonstandard design, therefore improve and design and develop cost, and place capacity is less, only reclaim <50kW air draft heat entirely.
3, rotary type total heat exchanger: formed by four parts such as asbestos paper runner, body, transmission, speed governing.Runner is full heat exchange carrier, by after plane and the gluing sodium sulphate of waveform compressed asbestos sheet, lithium chloride more superimposed, roll into cellular; Body outsourcing iron plate, inside establishes dividing plate and is divided into new wind passage and air exhaust passage; Control the adjustable air draft of runner rotating speed and contact the runner time with new wind, obtain the total heat recovery efficiency η of 60-70%, cannot realize independent operating, to control Indoor Temperature, humidity; The air draft of recyclable >50kW is heat entirely, significantly reduces costs; For the larger building air conditioning of resh air requirement.
Utilize accumulation of heat, the hygroscopic effect of runner, under temperature, wet gradient effect, first realize runner and alternately carry out heat, wet exchange from air drafts warm, that humidity is different and new wind, thereby indirectly realize the heat between air draft and new wind, the exchange of wetting.For example after summer temperature, new wind direction top runner heat release that humidity is higher, moisture releasing, be cooled, dry; And absorb heat, the runner after moisture absorption goes to bottom, temperature, air draft that humidity is lower are given in heat release, moisture releasing, make that it heats up, after humidification outside discharge chamber.Runner continues rotation and impels heat, moisture content in new wind to pass to continuously and indirectly air draft.Winter is just in time contrary, and runner first absorbs heat, the moisture content in air draft, then removes heating, the new wind of humidification, impels the heat of air draft, moisture content to pass to continuously and indirectly new wind.Thus and thus, new wind reclaims air draft heat entirely, and to realize cooling, dry fresh air in summer, heating in winter, the new wind of humidification, to meet new wind load demand.Yet, because newly wind and air draft mediate contact causes cross pollution; Rotatable parts reduce equipment operational reliability; New wind and exhaust duct need centralized arrangement, easily at fresh inlet and wind exhausting outlet string wind.
Since the crisis of the seventies generation world energy sources, some industrially developed country are its extensive use in engineering as the measure of air conditioner industry maximum energy-saving, and product specification is numerous, and air quantity is 50-100000m 3/ h, runner diameter is 300-3500mm, for reclaiming building air draft heat entirely.In fan coil and inducible system, with it, substitute an air-conditioning and process new wind.And to reconstruction project, do not increase cold and heat source, available its significantly increases cooling, heat capacity.
4, heat pipe-type total-heat exchanger: the interior vapor flow pressure drop of heat pipe is very little, cause corresponding temperature drop very little, and the thermal conduction resistance of heat pipe length direction is minimum, thereby makes no longer heat pipe length restriction of heat conduction.Evaporator section and the condensation segment of heat pipe-type total-heat exchanger are arranged apart, have both been convenient to connection and the installation in air channel, also make new wind not contact with air draft, avoid cross pollution.
Heat heat pipe evaporator section by air draft winter, then heat new wind by heat pipe condenser section; Summer is by new wind heating heat pipe evaporator section, then by heat pipe condenser section heating air draft, that is new wind reclaim the full heat of air draft and be cooled, dry.When heat pipe adopts symmetrical structure, to conduct heat and just there is invertibity, bringing-up section and heat release section are interchangeable, to realize winter new wind, from air draft, reclaim full heat, and summer, new wind reclaimed full heat from air draft, new wind and exhaust duct needn't commutate with season, without rotatable parts so that install reliable.Air draft is transmitted full heat with new wind mutually by heat pipe fin, to obtain the total heat recovery efficiency η of 60-70%, cannot realize Independent air conditioning operation.Yet by heat pipe, reclaim air draft heat entirely, will significantly improve Thermal Conduction Equipment cost, need nonstandard design in addition, therefore development cost is higher, and place capacity is less, the air draft that can only reclaim <50kW is entirely hot, is difficult to be applied in high-capacity direct current air-conditioning.
(3) summary of the invention
The present invention seeks to the advantage that comprehensive existing various new wind reclaims air draft heat technique, improve its defect, design: (1) high efficiency, large capacity reclaim the complete hot equipment of air draft; (2) fresh wind port and exhaust outlet are arranged apart, avoid new wind to contact, go here and there wind, cross pollution with air draft; (3) realize standardized designs, manufacture the complete hot equipment of air draft that reclaims.
For achieving the above object, the present invention by the following technical solutions, arranges system that wind source heat pump drives new wind as shown in Figure 1, wherein: 1-air draft source backheat airduct case; 2-source pump; The new wind of 3-is processed airduct case; 4-blower fan; 5-heat source side heat exchanger; 6-is used side heat exchanger; 7-refrigerant; 8-four-way change-over valve; 9-compressor; 10-device for drying and filtering; 11-check valve; 12-expansion valve.
According to the row's wind source heat pump shown in accompanying drawing 1, drive the system of new wind: its source pump 2 by the air draft source backheat airduct case 1 as heat source side, medium side switchover operation, as the new wind that uses side, process airduct case 3 and jointly form; Described source pump 2 is interior to be arranged heat source side heat exchanger 5 and uses side heat exchanger 6, in its heat exchanger tube, be filled with refrigerant 7, and tracheae and liquid pipe by refrigerant 7 refrigerant 7 closed circuits that connect into source pump 2, wherein the tracheae of refrigerant 7 connects compressors 9, heat source side heat exchanger 5 by four-way change-over valve 8 and uses refrigerant 7 air pipe interfaces of side heat exchanger 6; The symmetrical parallel component that connects device for drying and filtering 10 and check valve 11 in two ends of refrigerant 7 liquid pipes, and connect with middle expansion valve 12, and the flow direction of check valve 11 is pointed to respectively the refrigerant 7 liquid interface tubes of connected heat source side heat exchanger 5 and use side heat exchanger 6.
Described compressor 9 is semi-closed screw type compressor, open-type helical-lobe compressor, centrifugal compressor, piston compressor, scroll compressor, rotor-type compressor, or above-mentioned multiple compressors composes in parallel compressor 9.
Described heat source side heat exchanger 5 and use side heat exchanger 6 to overlap heat exchanger between the refrigerant 7 of pipe and air for fin.
System heating operation recovery air draft in winter heat of the present invention provides new wind heat treated for building, and air draft cold is reclaimed in cooling system operation in summer, and for building provides, new wind is lowered the temperature, dehumidification treatments, and its operation principle is described as follows:
1, system heating operation recovery air draft in winter heat provides new wind heat treated for building: as shown in Figure 1, winter, 20 ℃ of air conditioning air exhausts were by air draft source backheat airduct case 1 heat source side heat exchanger 5 of flowing through, by the low-temp low-pressure two-phase refrigerant 7 of another side circulation, absorbed evaporation latent heats and lower the temperature, dehumidify after discharge environment; Because flashing to the overheated gaseous coolant 7 of low-temp low-pressure, heat absorption by compressor 9, is compressed into the overheated gaseous coolant 7 of HTHP through four-way change-over valve 8, through four-way change-over valve 8, enter refrigerant 7 sides of using side heat exchanger 6 again, to the new wind of another side, discharge latent heat and be condensed into HTHP supercooled liquid refrigerant 7, again after drying filter 10, be inflated valve 12 throttlings and become low-temp low-pressure two-phase refrigerant 7, finally by check valve 11, flow into refrigerant 7 sides of heat source side heat exchanger 5, to complete heat pump cycle.New wind is processed airduct case 3 by new wind and is flowed through and use the air side of side heat exchanger 6 under blower fan 4 drives, and absorbs the condensation heat release of another side refrigerant 7 and after heating up, sends into room.
2, cooling system operation in summer is reclaimed air draft cold and is provided new wind cooling, dehumidification treatments for building: as shown in Figure 2, summer, 27 ℃ of air conditioning air exhausts were by air draft source backheat airduct case 1 heat source side heat exchanger 5 of flowing through, and by the overheated gaseous coolant 7 of the HTHP of another side circulation, were discharged condensation latent heat and after heating up, discharged environment, because heat release is condensed into after HTHP supercooled liquid refrigerant 7 drying filters 10, be inflated valve 12 throttlings and become low-temp low-pressure two-phase refrigerant 7, through check valve 11, flow into refrigerant 7 sides of using side heat exchanger 6 again, to absorb the new wind of another side, bring cooling, the full heat of dehumidifying, and flash to the overheated gaseous coolant 7 of low-temp low-pressure, through four-way change-over valve 8, by compressor 9, be compressed into the overheated gaseous coolant 7 of HTHP again, through four-way change-over valve 8, enter again refrigerant 7 sides of heat source side heat exchanger 5, to another side air draft, discharge latent heat and be condensed into HTHP supercooled liquid refrigerant 7, to complete kind of refrigeration cycle.New wind is flowed through and is used the air side of side heat exchanger 6 by new wind processing airduct case 3 under blower fan 4 drivings, to the another side refrigerant 7 required evaporation latent heats of release and after being lowered the temperature, dehumidifying, is sent into room.
The present invention is owing to adopting technique scheme, thereby the technology that directly reclaims air draft heat with various heat exchangers is compared, there is following obvious technical advantage: by source pump evaporimeter and condenser to freeze+to heat alliance mode, one side driving heat source side air draft source backheat airduct case, the degree of depth reclaims air draft heat entirely, and process air draft to approaching environmental working condition, reduce environmental thermal pollution; Drive on the other hand and use the new wind of side to process airduct case, the new wind of advanced treating is to approaching indoor operating mode.Thereby solve, improve the intrinsic contradictions that resh air requirement must increase air conditioning energy consumption, high efficiency, large capacity promote air conditioner energy saving, emission reduction effect; Fresh wind port and exhaust outlet be arranged apart to be avoided new wind to contact air draft causing cross pollution; Can realize standardized designs and the manufacture of air draft backheat equipment.
(4) accompanying drawing explanation
Accompanying drawing 1 is that the system heating operation in winter of heat pump separate form of the present invention reclaims air draft heat for building the operation principle schematic diagram that new wind heat treated is provided.
Accompanying drawing 2 is that the cooling system operation in summer of heat pump separate form of the present invention is reclaimed air draft cold for building the operation principle schematic diagram that new wind cooling, dehumidification treatments are provided.
Accompanying drawing 3 is that the system heating operation in winter of heat pump integral form of the present invention reclaims air draft heat for building the operation principle schematic diagram that new wind heat treated is provided.
Accompanying drawing 4 is that the cooling system operation in summer of heat pump integral form of the present invention is reclaimed air draft cold for building the operation principle schematic diagram that new wind cooling, dehumidification treatments are provided.
(5) specific embodiment
The system embodiment that row's wind source heat pump that the present invention proposes drives new wind as shown in Figure 1, is now described as follows: its 2,1 new wind of source pump by 1,1 medium side switchover operation of 1 air draft source backheat airduct case is processed airduct case 3 and jointly formed.
Backheat amount 186.4kW, the exhaust air rate 51236m of described air draft source backheat airduct case 1 3/ h, blast 200Pa, long 20m * wide 1.0m * high 0.7m, blower fan input power 10.266kW.
Described new wind is processed heating load 222.7kW, the resh air requirement 51236m of airduct case 3 3/ h, blast 200Pa, long 20m * wide 1.0m * high 0.7m, blower fan input power 10.266kW.
The interior aluminium fin cover copper tube heat source side heat exchanger 5 of refrigerating capacity 186.4kW and the aluminium fin cover copper tube use side heat exchanger 6 of heating capacity 222.7kW of arranging of described source pump 2, in its heat exchanger tube, be filled with the R22 refrigerant 7 of 60kg, and diameter 68mm tracheae and diameter 38mm liquid pipe by refrigerant 7 refrigerant 7 closed circuits that connect into source pump 2, wherein the tracheae of refrigerant 7 connects theoretical capacity 180m by four-way change-over valve 8 3refrigerant 7 air pipe interfaces of the semi-closed screw type compressor 9 of/h, input power 36.3kW, heat source side heat exchanger 5 and use side heat exchanger 6; The symmetrical parallel component that connects device for drying and filtering 10 and check valve 11 in two ends of refrigerant 7 liquid pipes, and connect with middle expansion valve 12, and the flow direction of check valve 11 is pointed to respectively the refrigerant 7 liquid interface tubes of connected heat source side heat exchanger 5 and use side heat exchanger 6.
The embodiment of the present invention, winter discharge 47727m 3the indoor exhaust wind that/h, 20 ℃/wet-bulb temperature of dry-bulb temperature are 15 ℃, by blower fan 4, driven by air draft source backheat airduct case 1 heat source side heat exchanger 5 of flowing through, to discharge the full heat of 186.4kW, lower the temperature, dehumidify into after 10.4 ℃ of 13 ℃/wet-bulb temperature of dry-bulb temperature outside drain chamber; The full heat of air draft by source pump, heat source side heat exchanger 5 being reclaimed is again promoted to 222.7kW high-grade heat, and delivers to and use in side heat exchanger 6, with a flow 47341m who is flowed through by new wind processing airduct case 3 by blower fan 4 drivings 3the outdoor new wind that/h, 7 ℃/wet-bulb temperature of dry-bulb temperature are 6 ℃, is heated to 12.1 ℃ of 20.6 ℃/wet-bulb temperature of dry-bulb temperature etc. water capacity.The heating energy efficiency ratio COP of source pump 2 reaches 6.13, and row's wind source heat pump to drive the system backheat heating energy efficiency ratio COP of new wind be 3.92; Temperature organic efficiency η t of the present invention is 104.7%, than national standard, improves 61.1%; Enthalpy organic efficiency η h is 65.0%, than national standard, improves 18.2%.
The embodiment of the present invention, summer average discharge 51236m 3the indoor exhaust wind that/h, 27 ℃/wet-bulb temperature of dry-bulb temperature are 19 ℃, by blower fan 4, driven by air draft source backheat airduct case 1 heat source side heat exchanger 5 of flowing through, water capacity is heated into after 23.4 ℃ of 42.4 ℃/wet-bulb temperature of dry-bulb temperature outside drain chamber to absorb 254.9kW sensible heat heat etc.; The air draft cooling heat dissipation by source pump, heat source side heat exchanger 5 being reclaimed is again produced the cold into 208.5kW, and delivers to and use in side heat exchanger 6, with a flow 49924m who is flowed through by new wind processing airduct case 3 by blower fan 4 drivings 3the outdoor new wind that/h, 35 ℃/wet-bulb temperature of dry-bulb temperature are 24 ℃, lowers the temperature, dehumidifies to 20.4 ℃ of 27.0 ℃/wet-bulb temperature of dry-bulb temperature.Air draft cold absorption condensation heat by 1 source pump to reclaim, produces 175.0kW cold, and processes in the coil pipe of airduct casees 3, total flow 55800m with 12 ℃ of/17 ℃ of backwater that supply water, 3 the new wind of flowing through 3the new wind of/h from 24 ℃ of coolings of 35 ℃/wet-bulb temperature of dry-bulb temperature, dehumidify to 20.8 ℃ of 27 ℃/wet-bulb temperature of dry-bulb temperature.The refrigeration efficiency of source pump 2 reaches 4.49 than EER, and row's wind source heat pump to drive the system backheat refrigeration efficiency of new wind be 3.115 than EER; Temperature organic efficiency η t of the present invention is 100%, than national standard, improves 66.7%; Enthalpy organic efficiency η h is 72.72%, than national standard, improves 45.44%; Water capacity organic efficiency η d is 51.39%.

Claims (3)

1. arrange wind source heat pump and drive the system of new wind, it is by air draft source backheat airduct case (1); Source pump (2); New wind is processed airduct case (3); Blower fan (4); Heat source side heat exchanger (5); Use side heat exchanger (6); Refrigerant (7); Four-way change-over valve (8); Compressor (9); Device for drying and filtering (10); Check valve (11); The compositions such as expansion valve (12).It is characterized in that: the system that drives new wind according to the row's wind source heat pump shown in accompanying drawing 1: it is provided with the source pump (2) of air draft source backheat airduct case (1) as heat source side, medium side switchover operation, process airduct case (3) as the new wind that uses side and jointly form; Heat source side heat exchanger (5) is set in described source pump (2) and uses side heat exchanger (6), in its heat exchanger tube, be filled with refrigerant (7), and tracheae and liquid pipe by refrigerant (7) refrigerant (7) closed circuit that connects into source pump (2), wherein the tracheae of refrigerant (7) connects refrigerant (7) air pipe interface of compressor (9), heat source side heat exchanger (5) and use side heat exchanger (6) by four-way change-over valve (8); The symmetrical parallel component that connects device for drying and filtering (10) and check valve (11) in two ends of refrigerant (7) liquid pipe, and connect with middle expansion valve (12), and the flow direction of check valve (11) is pointed to respectively refrigerant (7) the liquid interface tube of connected heat source side heat exchanger (5) and use side heat exchanger (6).
2. a kind of system that wind source heat pump drives new wind of arranging as claimed in claim 1, it is characterized in that: described compressor (9) is semi-closed screw type compressor, open-type helical-lobe compressor, centrifugal compressor, piston compressor, scroll compressor, rotor-type compressor, or above-mentioned multiple compressors composes in parallel compressor (9).
3. a kind of system that wind source heat pump drives new wind of arranging as claimed in claim 1, is characterized in that: described heat source side heat exchanger (5) and use side heat exchanger (6) to overlap heat exchanger between the refrigerant (7) of pipe and air for fin.
CN201410137954.7A 2014-04-01 2014-04-01 Exhaust air source heat pump fresh air driving system Pending CN103994505A (en)

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN107729600A (en) * 2017-09-01 2018-02-23 珠海格力电器股份有限公司 Evaporator emulated computation method
CN108266877A (en) * 2017-12-20 2018-07-10 同济大学 The air-exhaust heat-recovery fresh air handling air-conditioner set of carbon dioxide trans-critical cycle

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN201259352Y (en) * 2008-09-16 2009-06-17 牟端 Multifunctional heat pump system
CA2630886A1 (en) * 2008-05-08 2009-11-08 Air Cube Inc. Method and system for recovering energy through air conditioning
CN201954714U (en) * 2011-02-17 2011-08-31 大连鸿源热能设备制造有限公司 Heat pump system for recovering air-conditioner discharged air
CN102705920A (en) * 2012-05-24 2012-10-03 吕智 Double-cold-source heat pump total heat recovery humidity regulating and temperature controlling fresh air unit and control method thereof
CN202660689U (en) * 2011-11-17 2013-01-09 北京建筑工程学院 Split heat pump type air exhaust energy recovery device for air-conditioner

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CA2630886A1 (en) * 2008-05-08 2009-11-08 Air Cube Inc. Method and system for recovering energy through air conditioning
CN201259352Y (en) * 2008-09-16 2009-06-17 牟端 Multifunctional heat pump system
CN201954714U (en) * 2011-02-17 2011-08-31 大连鸿源热能设备制造有限公司 Heat pump system for recovering air-conditioner discharged air
CN202660689U (en) * 2011-11-17 2013-01-09 北京建筑工程学院 Split heat pump type air exhaust energy recovery device for air-conditioner
CN102705920A (en) * 2012-05-24 2012-10-03 吕智 Double-cold-source heat pump total heat recovery humidity regulating and temperature controlling fresh air unit and control method thereof

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
孙戈: "《建筑能效评估》", 31 August 2013, 中国建材工业出版社 *

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN107729600A (en) * 2017-09-01 2018-02-23 珠海格力电器股份有限公司 Evaporator emulated computation method
CN107729600B (en) * 2017-09-01 2020-03-27 珠海格力电器股份有限公司 Evaporator simulation calculation method
CN108266877A (en) * 2017-12-20 2018-07-10 同济大学 The air-exhaust heat-recovery fresh air handling air-conditioner set of carbon dioxide trans-critical cycle

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Application publication date: 20140820