CN1114040A - Air energy heat circulation exchanger - Google Patents
Air energy heat circulation exchanger Download PDFInfo
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- CN1114040A CN1114040A CN94106955A CN94106955A CN1114040A CN 1114040 A CN1114040 A CN 1114040A CN 94106955 A CN94106955 A CN 94106955A CN 94106955 A CN94106955 A CN 94106955A CN 1114040 A CN1114040 A CN 1114040A
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- Prior art keywords
- air
- air energy
- heat
- energy
- evaporation device
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Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B39/00—Evaporators; Condensers
- F25B39/04—Condensers
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F12/00—Use of energy recovery systems in air conditioning, ventilation or screening
- F24F12/001—Use of energy recovery systems in air conditioning, ventilation or screening with heat-exchange between supplied and exhausted air
- F24F12/002—Use of energy recovery systems in air conditioning, ventilation or screening with heat-exchange between supplied and exhausted air using an intermediate heat-transfer fluid
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F3/00—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems
- F24F3/12—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling
- F24F3/14—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling by humidification; by dehumidification
- F24F3/147—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling by humidification; by dehumidification with both heat and humidity transfer between supplied and exhausted air
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B41/00—Fluid-circulation arrangements
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D5/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, using the cooling effect of natural or forced evaporation
- F28D5/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, using the cooling effect of natural or forced evaporation in which the evaporating medium flows in a continuous film or trickles freely over the conduits
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2339/00—Details of evaporators; Details of condensers
- F25B2339/04—Details of condensers
- F25B2339/041—Details of condensers of evaporative condensers
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
- Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
- Y02B30/52—Heat recovery pumps, i.e. heat pump based systems or units able to transfer the thermal energy from one area of the premises or part of the facilities to a different one, improving the overall efficiency
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
- Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
- Y02B30/56—Heat recovery units
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Sorption Type Refrigeration Machines (AREA)
- Other Air-Conditioning Systems (AREA)
Abstract
The invented exchanger is composed of air energy bilateral evaporator, air energy bilateral condenser and low pressure difference energy conversion heat pump and uses the energy of outdoor air as main refrigerating circulation power. The flowing direction of the working medium is opposite to that of air to be refrigerated and condensing air, the variation of temp. is synchronous and the heat conducting temp. difference approaches to zero. The used working media is the working media pair composed of refrigerating agent and absorbent.
Description
The present invention relates to air energy heat circulation exchanger.
Air conditioning is the energy state and the air property of regulating room air, in order to satisfy the comfortable of human body and physiological hygiene requirement.And the pollution sources of room air are mainly derived from the metabolism campaign of indoor article and human body.Closed air-flow circulation is that the continuation input was indoor after indoor foul atmosphere was sucked refrigeration, and the result of this air-flow circulation is the constantly also vicious circle repeatedly of intensification of dirty degree, and is totally unfavorable to health.If introduce 100% fresh keeping chamber outer air, corresponding power consumption need increase more than 1.2 times, so high energy consumption and low-yield conversion efficiency are the defectives of existing air-conditioning.
In other words, as if the oxygen demand that will satisfy in the certain space, and due refrigeration (heat) requirement, with present air conditioner, need expend a large amount of electric energy.
The second law of thermodynamics is pointed out: heat can spontaneously pass to cryogenic object from high temp objects, and can not spontaneously pass to high temp objects from cryogenic object.Carnot cycle (Carnot cycle), Lao Lunci circulation (Lorenz cycle) are the highest Ideal Cycle of thermodynamic efficiency, also are the guiding theories of all kinds of air-conditionings.According to the existing all kinds of air conditioners of above-mentioned theory development, its process of refrigerastion need expend all very that macro-energy could be pumped to high temp objects from cryogenic object with heat energy.Therefore process of refrigerastion must be high-octane expending and excessive power consumption process, and existing its efficiency of thermal cycle of all kinds of air conditioners is far below Carnot's cycle efficiency.
Can compensate the required energy of kind of refrigeration cycle by means of the energy (hot outdoor air energy) of cooled air, make the process of refrigerastion of power consumption transfer the storage of energy and the process of generation power to, as long as the required energy of energy 〉=refrigeration of its acquisition can make refrigeration system move automatically.This needs higher evaporating temperature and lower condensation temperature, and obtains air-conditioning necessary cold (heat) peak temperature in heat transfer process.
The present invention be a kind of be the low pressure differential thermal pump air conditioner of main refrigeration (heat) circulation power with the air energy.But low pressure differential thermal pump both liquid gas mixes conveying, but also liquid gas separates conveying.This part energy of the be used to refrigeration (heat) that air can be meant in the natural air to be contained.The differential cooling tube is that a kind of unit are heat flow is big, and can make the terminal point heat transfer temperature difference be substantially equal to zero high-performance heat exchanger, and working media is to being meant the combination of cold-producing medium and absorbent, as water and lithium bromide (LiBr) or ammonia (NH
3) and water, or water and lithium chloride (LiCl) etc.Heating power intersection circulator of the present invention is the outdoor fresh air air conditioner that is made of air energy bi-directional evaporation device, the two-way condenser of air energy, low pressure reduction power conversion heat pump, its temperature-entropy curve is cross-shaped thermodynamic cycle, can make full use of air energy and compensate the required power cycle of cold (heat) process, thereby have high efficiency of thermal cycle.It is that the output of cold in the air conditioning (heat) amount all need adopt 100% outdoor fresh air could obtain best efficiency of thermal cycle that heating power of the present invention intersects another feature of circulator.
The present invention be with the outdoor high temperature air be the energy directly reach the heating and cooling-down effect, general condenser and outside air temperature △ T=13～15 ℃, evaporimeter and evaporating temperature △ T=8～12 ℃, and △ T=0.1 of the present invention～0.5 ℃, can make full use of the purpose that air can reach heat exchange.
In other words, the present invention introduces 100% outdoor air, after the apparatus of the present invention of flowing through, derive cold (heat) air, not only can obtain oxygen demand fully, and because of fully height (low) the temperature formation circulation of utilization outdoor air, theoretic EER value is high, that is, go to produce maximum refrigeration (heat) effect with minimum energy loss.
In cyclic process of the present invention, working media (Working substance) circulation is different with existing mode, mainly be: general absorption mode is made up of four parts, be evaporimeter, generator, condenser, absorber, and evaporimeter of the present invention comprises the generator function, and condenser comprises the absorber function, and the GENERAL TYPE generator must be with used heat or steam, evaporimeter must be done the secondary heat exchange with frozen water, and the present invention does not then need.
The object of the present invention is to provide a kind of air energy heat circulation exchanger.
The object of the present invention is achieved like this, promptly by a kind of air energy heat circulation exchanger is provided, by air energy bi-directional evaporation device, the two-way condenser of air energy, low pressure reduction power conversion heat pump is formed, be distributed on air energy bi-directional evaporation device and the two-way condenser of air energy with the working media convection current that can be recycled utilization, utilize the air energy of drainage to change power to cause the working media that flows to storing energy on air energy bi-directional evaporation device as heat, and on air can two-way condenser release heat, and be recycled, and air can be released energy by the bi-directional evaporation device at air simultaneously, can absorb energy on the two-way condenser in air.
The invention has the advantages that it can realize best refrigeration with lowest energy consumption.
Below in conjunction with accompanying drawing, embodiments of the invention are described, wherein:
Fig. 1 is switch thermodynamic cycle temperature entropy TS figure of the present invention;
Fig. 2 is desirable Carnot cycle, Lao Lunci circulation and the TS comparison diagram of thermodynamic cycle of the present invention;
Fig. 3 is an air energy heat circulation exchanger process of refrigerastion schematic diagram of the present invention;
Fig. 4 is an A-A line cutaway view among Fig. 3;
Fig. 5 is a B-B line cutaway view among Fig. 3;
Fig. 6 is the circulate comparison diagram of used working media of thermodynamic cycle of the present invention, Carnot cycle, Lao Lunci;
Fig. 7 is the pressure enthalpy Ph comparison diagram corresponding to Fig. 6;
Fig. 8 is the TS figure that thermodynamic cycle of the present invention changes over the circulation of heating power triangle;
Fig. 9 is the window type embodiment of thermodynamic cycle machine of the present invention.
Referring to Fig. 1, it is air energy heat circulation exchanger temperature entropy TS figure (TEMPERATUREENTROPY), in kind of refrigeration cycle:
T
2Being the thermal peak temperature, also is outdoor air dry bulb (DRY BULB) temperature.
T
2=T
K(thermal peak is the maximum temperature point).
T
1Being cold front value temperature, also is the cold wind output temperature.
T
1=T
0(the cold front value is the minimum temperature point).
T
4It is air wet bulb (WET BULB) temperature of air-conditioned room.
T
3Be the exhaust wet-bulb temperature of condensation air.
The I district: the 1-J-2 process is the refrigeration work medium to from T
o～T
KContinuous temperature change heat absorption (stored air energy) process; Pairing cooled air lateral areas is the II district: the 2-J-1 process is that cooled air is from T
K～T
oContinuous temperature change exothermic process.The III district: the 3-J-4 process is the refrigeration work medium to from T
3～T
4Continuous temperature change exothermic process; Pairing IV district: the 4-J-3 process is that condensation air is from T
4～T
3Continuous temperature change wet fully endothermic process.
2-3 is to low temperature (T from high temperature
K～T
3) adiabatic pumping process.
4-1 is the adiabatic expansion process.
The area of △ 1J4 is the required merit W of kind of refrigeration cycle
1; The area of △ 23J is that the air that kind of refrigeration cycle obtains can W
2, W
2Can be converted into useful work fully.The J point is right endotherm of refrigeration work medium and exotherm intersection point.
The △ 1J4 of counterclockwise trend is the refrigeration machine in the air energy heat circulation exchanger, and the △ 23J of trend is the air energy engine in the air energy heat circulation exchanger clockwise, and the J point is the series connection point of system machine and air energy engine.
The merit of the required compensation of kind of refrigeration cycle is W
1-W
2=△ W
Heating power Energy Efficiency Ratio EER=(Q suction)/(△ W); Wherein the Q suction is a refrigerating capacity
Work as W
2〉=W
1The time can be by means of air energy W
2And operation automatically, at this moment EER → ∞.
When cold front value temperature T
oDuring reduction: T
4Also move down thereupon, the J point also moves down thereupon, W
1And W
2Increase simultaneously, △ W=W
1-W
2Do not increase, visible air energy heat circulation exchanger obtains air energy W simultaneously again in the process of refrigerastion of wasted work
2
Fig. 2 is the TS comparison diagram of desirable Carnot cycle, Lao Lunci circulation and air energy heat circulation exchanger.
It is the Lao Lunci circulation.
At identical T
KAnd T
oCarnot cycle wasted work maximum under the condition, the refrigerating capacity minimum; The maximum wasted work minimum of air energy heat circulation exchanger refrigerating capacity; Labor Lenze is circulated between Carnot cycle and air energy heat circulation exchanger, T
KAnd T
oThe big more above-mentioned contrast of the temperature difference also obvious more.
The diabatic process of differential heat-transfer pipe is the not constant temperature process of sufficient, unlimited differential, and its terminal point heat transfer temperature difference is substantially equal to zero.Thereby 1-J-2 and 3-J-4 can think reversible continuous temperature change procedure.Air energy heat circulation exchanger is made of two reversible continuous temperatures variation and two isentropic procedures.
Fig. 3 is an air energy heat circulation exchanger process of refrigerastion schematic diagram.
Air can pass through conducting strip 5 heat exchange by bi-directional evaporation device 1.Referring to Fig. 4, air can be separated into I district and II district by bi-directional evaporation device 1 with the plane metal conducting strip that is arranged in parallel.The I district is the T that conducting strip 5 and dxn differential heat Insulation film 20 are formed
o～T
KThe unlimited differential of refrigeration work medium decalescence (energy storage) district not, TS figure is an II corresponding to the 1-J-2 cooled air side corresponding with the I district, conducting strip 5 and ripple conducting strip 7 compositions from T
K～T
oThe unlimited differential isothermal heat release zone dyn runner not of cooled air, T-S figure is corresponding to 2-J-1.Ripple conducting strip 7 thin metal materials are made, the heat conduction amount of dyn direction can be considered zero, can the conducting strip thermal insulation be cut into a lot of bar shaped warm areas in the dyn direction, next is that the bigger nonmetallic materials of heat exchange area dxn differential heat Insulation film 20 usefulness thermal resistances that increase conducting strip and air are made, and in the dxn direction conducting strip thermal insulation is cut into a lot of bar shaped warm areas.Therefore conducting strip is cut into numerous (dxn, dyn) little isothermal thermal conductive surface by dxn, dyn thermal insulation, and the temperature of each little isothermal level and little isothermal level (dxy+1, dyn) adjacent one another are or (dxn, dyn-1) was both unequal, and its temperature difference trends towards zero again.Because the thermal conductive surface of air energy bi-directional evaporation device 1 is the not isothermal thermal conductive surface of unlimited differential, can think that therefore air can the bi-directional evaporation device be from T
o～T
k(or T
k～T
o) continuous temperature change thermal conductive surface, and the temperature changing process of both sides is synchronous.
Be in the thermal peak temperature T
KOutdoor air a
1, at blowing fan 12 impetus lower edge a
2Direction in the dyn in II district runner fully continuous temperature change heating conducting strip 5, heat release is to cold front value temperature T
oCold wind a
3It is indoor to regulate window 14 inputs through air-out, its cooled process on T-S figure corresponding to 2-J-1(T
k-T
o) and continuous temperature variation exothermic process.
The weak solution g that absorbent I and cold-producing medium X form
1Through each g of woven hose 16 uniform distributions
1Distributing pipe sprays in each dxn runner that the I district is arranged in parallel from choke valve 17, presses g
1→ g
12→ g
2Direction flows, and loop pipe 11 is dxn runner corners.g
1→ g
12→ g
2Endothermic process in the dxn runner on T-S figure corresponding to 1-J-2(T
o-T
k) continuous temperature change endothermic process, at isopiestic state P
1Down, g
1From cold front value temperature T
oThe continuous temperature variation is heated to the thermal peak temperature T fully
K, g
1The liquid refrigerant X that includes progressively absorbs heat and is evaporated to overtemperature T
k-T
oThe vaporized refrigerant X of=△ T
2, g
1Also correspondingly be heated to form overtemperature △ Tg
2Concentrated solution.
Because the heat transfer process of air energy bi-directional evaporation device 1 carries out on little isothermal level, it is tending towards isothermal possibly to the greatest extent and the refrigeration work medium that each little isothermal level always makes its conducting strip two sides is to the temperature of I, X and cooled air, its terminal point heat transfer temperature difference must trend towards zero, so the refrigeration work medium is to from T
o～T
KEndothermic process be the reversible process of no heat waste; And the air that is applied to actual heat exchange can bi-directional evaporation device 1, its heat transfer temperature difference is 0.1～0.5 ℃ and there is no need overcritical heat transfer temperature difference → 0.
The heat pump sex expression of air energy bi-directional evaporation device 1 exists g
2And X
2Overheated strongly, at T
o～T
kReversible endothermic process in stored this part air energy W of △ T
2, the process of its refrigeration is again thermal energy storage process simultaneously.
Air can two-way condenser 2 also be by conducting strip 5 heat exchange.Referring to Fig. 5, air can be divided into III district and IV district by two-way condenser 2 with the plane metal conducting strip that is arranged in parallel.The III district is that the refrigeration work medium formed of conducting strip 5 and dxn differential heat Insulation film 20 is to g
2And X
2From T
3～T
4Continuously not isothermal be condensed and the heat release zone that liquefies, T-S figure is corresponding to 3-J-4.The condensation air side corresponding with the III district be IV district conducting strip 5 and dyn differential heat Insulation film 21 form from T
4～T
3The unlimited differential of the condensation air wet fully heat absorption of isothermal district not, T-S figure is corresponding to 4-J-3.The film-type evaporation face 6 that the outside applying porous water-absorbing material of conducting strip is made, its face have good water storage, water imbibition and bigger porous surface and amass.Water storage can improve the heat transfer coefficient of film-type evaporation face 6 and conducting strip 5 greatly; Porous can form bigger evaporation surface; Make its condensation process become the lower wet fully endothermic process of temperature.Because the specific heat at constant pressure Cp1 of humid air is more much bigger than pressurization by compressed air specific heat Cp2, thus T
4～T
3The temperature difference is less.Dxn differential heat Insulation film 20 and dyn differential heat Insulation film 21 are all made with the bigger nonmetallic materials of thermal resistance, the two sides of conducting strip 5 is cut into infinitely a plurality of (dxn, dyn) differential isothermal thermal conductive surface by the differential thermal insulation, thereby the conducting strip 5 of the two-way condenser 2 of air energy is become from T
4～T
3Continuous temperature change thermal conductive surface.
Cold wind a from 1 output of air energy bi-directional evaporation device
3After indoor extract heat, wet amount, become the required temperature of human comfort, temperature a
4, forced to suck by ventilating fan 19 in the dyn runner in IV districts along a
5Direction fully absorbs steam on film-type evaporation face 6, from wet-bulb temperature T
4Rise to wet-bulb temperature T
3Saturated mode a
6And row is to atmosphere.
The pressure that flows out from air energy bi-directional evaporation device 1 is P
1G
2And X
2Be pumped to P by low pressure differential thermal pump 15
2, each liquid vapour distributing pipe 3 of distributing to the two-way condenser 2 of air energy through liquid vapour carrier pipe 13 sprays into from spray orifice in the dxn runner in III district, along g
2→ g
1Direction is from T
3To T
4Fully, continuously not the isothermal heat release and progressively liquefaction be cold weak solution g
1g
1Flow into air energy bi-directional evaporation device 1 through woven hose 16 and choke valve 17 ... circulation and so forth.
Air can two-way condenser 2 heat transfer process also be that differential at unlimited differential does not carry out on the isothermal thermal conductive surface, its terminal point heat transfer temperature difference → 0 is therefore from T
3～T
4Condensation process and its correspondence from T
3～T
4The process that is condensed and its correspondence from T
4～T
3The wet endothermic process of condensation air all are reversible continuous temperature change procedures.
Overheated concentrated solution g
2At T
3→ T
4Under the condensing state of lower temperature, its surperficial dividing potential drop is far below P
2, have strong absorption gaseous refrigerant X
2And make its liquefaction and the ability of heat release.Therefore the supercool that air can two-way condenser 2 coagulates sex expression aspect two of low temperature and low pressure condensations, and this is because g
2The W that stores
2And T
3～T
4The result of cryogenic condensation double action.Supercool can make g again with fixed attention
1Weak solution is cold excessively, and refrigerating capacity is increased and T
oFurther reduce, this has just more promoted the benign cycle of system.
In actual cycle air can bi-directional evaporation device 1 and air can two-way condenser 2 the not isothermal heat transfer temperature difference be controlled between 0.1～0.5 ℃ and and unnecessary overcritical heat transfer temperature difference → 0 of going, so 1-J-2 and 3-J-4 process still have a small amount of irreversible work (EXERGY) to decrease to exist.Refrigeration work medium convection cell back and forth flows on the other hand, divides timing must have frictional resistance to exist; 41 processes are not isentropic procedure but the throttling step-down process of constant enthalpy, have irreversible work to decrease yet and exist.
The merit that above-mentioned irreversible procedure forms is decreased the loss △ W that shows as system's net work
1So merit W of the required compensation of air energy heat circulation exchanger thermodynamic cycle
M=△ W
1+ △ W, W
MThe compensation merit △ W that＞desirable air energy heat circulation exchanger thermodynamic cycle is required
oW
MProvided by low pressure reduction power conversion heat pump M, the pump action of low pressure differential thermal pump M is with liquid g
2With steam state X
2Simultaneously from P
1Be pressurized to P
2Can carry by two-way condenser 2 inlets to air, make absorbent and cold-producing medium carry out the heating power operation, finish energy and carry and conversion process of energy by Fig. 3.
Because the heat transfer temperature difference of air energy bi-directional evaporation device 1 and the two-way condenser 2 of air energy is less, and P
2-P
1=△ P is less, so the merit that the isenthalpic throttling merit of 4-1 process is decreased and refrigeration work medium fluid frictional resistance causes damage is also less, so total net work loss △ W of system
1Also less.As seen air energy heat circulation exchanger not only has high theoretical EER value, and higher thermodynamic perfect degree (THERMODYNAMIC PERFECT DEGREE) arranged, under the test working condition of standard, (Q suction)/(Wm) value can reach 20～35 to its actual EERm=.
Fig. 6 is
Working media be the air energy heat circulation exchanger formed of absorbent and cold-producing medium and
Working media is that the CARNOT REFRIGERATOR of azeotropic or unitary system cryogen reaches
Working media is the TS comparison diagram of the Lao Lunci refrigeration machine of mixed non-azeotropic refrigerant; Fig. 7 is its corresponding enthalpy Ph comparison diagram (PRESSURE ENTHALPA DIAGRAM) of pressing.Existing commercially available Kano and Lao Lunci refrigeration machine (removing large-size air conditioning) all adopt air cooled condenser and air-cooled evaporimeter.Because the condensation temperature of air cooled condenser is high 13～15 ℃ than outdoor environment temperature, the evaporating temperature of air-cooled evaporimeter is than low 8～12 ℃ of cold wind outlet temperature, and the heat transfer temperature difference of the differential heat transmitter of air energy heat circulation exchanger is 0.1～0.5 ℃, at identical cold wind output temperature and identical environment temperature T
KPreceding topic down; The condensation temperature of Kano, Lao Lunci refrigeration machine is higher than T
KWith condensing pressure greater than P
2And evaporating temperature is lower than T
oBut be lower than P with evaporating pressure
1From the contrast of Fig. 6 and Fig. 7 as can be known the refrigeration system of reality: condensing pressure is higher, and evaporating temperature is lower, and power consumption is also bigger, and refrigerating capacity is littler on the contrary.
If: the power consumption of CARNOT REFRIGERATOR is W
c, refrigerating capacity Q
c, EER
c
The wasted work of labor Lenze's refrigeration machine is W
L, refrigerating capacity Q
m, EER
L
The wasted work of air energy heat circulation exchanger is W
m, refrigerating capacity Q
m, EER
m
∵ W
c＞W
L＞W
mAnd Q
m＞Q
L＞Q
c
∴EER
m＞EER
L＞EER
c
Air energy heat circulation exchanger has bigger suction superheat temperature, and this part heat is delivered by the temperature rise of absorbent, so air energy heat circulation exchanger should be selected the absorbent that thermal capacity is big, thermal conductivity factor is higher; Also have bigger supercooling temperature (being the result that supercool coagulates effect), so refrigerating capacity Q
MThan Q
cAnd Q
LMuch bigger, Yin Kanuo, Lao Lunci refrigeration machine EER value are low can not to adopt 100% outdoor fresh air, and the present invention can adopt 100% the best efficiency of thermal cycle of outdoor fresh air realization on the contrary.
Referring to Fig. 3, water capacity X
1Outdoor air a
1Heat release is to cold front value temperature T in air energy bi-directional evaporation device 1
oA
3Cold wind, a
3Water capacity reduce to X
2, the condensate flow of then every Kg input cold wind is X
1-X
2=△ X
10△ X
1Splash into drip tray 10 and flow in the ponding dish 9, regularly, quantitatively spray to the film-type evaporation face 6 of the two-way condenser 2 of air energy by water pump from nozzle 18 from water pipe.The condensation of the two-way condenser 2 of air energy is wet endothermic processes, water capacity X
3Room air a
4Develop into water capacity X from the film-type evaporation face 6 absorption steam of the two-way condenser 2 of air energy
4Humid air a
6And arrange to outdoor, the water consumption that its every Kg discharges air is X
4-X
3=△ X
2, air energy heat circulation exchanger is an equivalent at unit interval input air and discharge air, therefore as △ X
1=△ X
2The time be the water balance point.Because the water capacity X of natural air
1With indoor humidity load X
3-X
2Can't be scheduled to (being dynamic), so the water amount in the ponding dish is at △ X
2＞△ X
1In time, should be replenished by automatic water supply device, at △ X
1＞△ X
2In time, then draw automatically.
Referring to Fig. 3 and Fig. 8, when air can bi-directional evaporation device 1 during as indoor set, air can two-way condenser 2 during as off-premises station, the cooled air that air can bi-directional evaporation device 1 is the closed circulation air-flow of room air; The condensation air of the two-way condenser 2 of air energy is to arrange to outdoor (being equivalent to present divergence type air-conditioning) from outdoor absorption again.At this moment the T-S of air energy heat circulation exchanger figure just develops into Fig. 6's
Shape T-S circular chart (to call heating power triangle circulator in the following text).
T
2Be the dry-bulb temperature of room air.
T
4Be the wet-bulb temperature of room air.
T
3Be the exhaust wet-bulb temperature of the two-way condenser 2 of air energy.
T
o=T
1Be that cold front value temperature also is the output cold wind temperature of air energy bi-directional evaporation device.
Heating power triangle circulator T when actual motion
2Change.Work as T
2=T
3The time, J point and T
2, T
3Point overlaps a bit, W
2=0 works as T
3＞T
2The time J point disappear.Heating power triangle circulator and air energy heat circulation exchanger are that same system also is made of two approximate reversible continuous temperature change procedure, an adiabatic pumping process, isenthalpic throttling processes.
Suppose that air energy heat circulation exchanger and heating power triangle circulator are identical cold front value temperature T o.
Because: T
2＜T
K, T
KIt is outdoor environment temperature;
T
4＜T
8, T
8Be outdoor air wet-bulb temperature;
Just heating power triangle circulator thermal peak temperature is lower than air energy heat circulation exchanger, and condensation temperature is higher than heating power intersection circulator; Because T
K-T
8＞T
2-T
4, so the stored air energy of process of refrigerastion heating power triangle circulator intersects circulator less than heating power.Then heating power triangle circulator M is to the merit W of system's input
M' should be greater than the required merit W of air energy heat circulation exchanger
MBut heating power triangle circulator equally can the power consumption process of refrigerastion in the stored air energy, the heat pump of air energy bi-directional evaporation device 1 and the super condensability of the two-way condenser 2 of air energy still exist, and the irreversible loss of diabatic process is less, and therefore also having higher efficiency of thermal cycle is coefficient of performance EER.
If in heating power triangle circulator the refrigeration work medium is non-azeotropic (NONAZEOTROPIC) mix refrigerant to changing, the circulation of the heating power triangle of Fig. 8 promptly is changed to so
Lao Lunci circulation.The as can be seen from the figure required function W of Lao Lunci circulation
L＞2W
M'; And because the following area of endotherm 1-2 ' is less than with the area below the heating power triangle circulator endotherm Q1-J-2; As can be known the coefficient of performance EER Senior Two of the comparable labor Lenze's refrigeration machine of heating power triangle circulator doubly more than.Its coefficient of performance EER also will further reduce when changing to azeotropic (AZEOTROPIC) cold-producing medium or unitary system cryogen as if the working media with heating power triangle circulator.Because Lao Lunci refrigeration machine and CARNOT REFRIGERATOR can not be utilized air energy in process of refrigerastion; Make the heat pump of air energy bi-directional evaporation device 1 and the supercool of the two-way condenser 2 of air energy coagulate disappearance.So air energy heat circulation exchanger and heating power triangle circulator only use the refrigeration work medium to the time, could obtain its maximum coefficient of performance.
Air energy heat circulation exchanger can be made into window type machine.Fig. 9 is the air energy heat circulation exchanger of window type.Its center line is above to be air energy bi-directional evaporation device 1 part, and center line is following to be two-way condenser 2 parts of air energy.
Outdoor natural air a
1By blowing fan 12 drive can bi-directional evaporation device 1 by air the heat release of dyn runner to cold front value temperature T
oA
3Import indoor, room air a
4Under the swabbing action of ventilating fan 19 through air-out regulate window leaf 28 guiding rears air can two-way condenser 2 the film-type evaporation face 6 of dyn runner on draw wet, heat after, with a
6Form row is to atmosphere.The back flow plate 27 of air energy bi-directional evaporation device 1, the two-way condenser 2 of air energy is in order to separate the dxn runner, so that its refrigeration work medium flows to be the U font in the differential heat transmitter.
Air energy heat circulation exchanger is when heating (heat pump): air is can bi-directional evaporation device 1 still identical, just transfers to cold front value air outdoor; Air can two-way condenser 2 also phase still, but the thermal peak air input of its formation is indoor.Therefore, its whole formation must be done as down conversion:
1, with air can bi-directional evaporation device 1, air can two-way condenser 2 the inlet of refrigeration work medium switch to outlet simultaneously, outlet switching to inlet simultaneously makes its refrigeration work medium to inverted running.
2, make the blowing fan antiport and become ventilating fan from indoor to outdoor air draft, room air through air can bi-directional evaporation device 1 the heat release of dyn runner to cold front value temperature row to atmosphere; Make the ventilating fan antiport and become blowing fan, outdoor fresh air is indoor to the input of thermal peak temperature through the heat absorption of dyn runner, the moisture absorption of the two-way condenser 2 of air energy.
3, air can bi-directional evaporation device 1 left side, air can two-way condenser 2 right sides heat nozzle 26 under the effect of solenoid electric valve 24 and water pump 23 regularly to air can bi-directional evaporation device 1 and air can two-way condenser 2 sprayings can two-way condenser 2 in order to wetting air the film-type evaporation face and in time dissolve the long-pending frost of air in can bi-directional evaporation device 1 dyn runner.Can add in the ponding dish an amount of glycerine (GLYCERINE) glycerite with strengthen air can bi-directional evaporation device 1 and air can two-way condenser 2 heat exchange performance and prevent air can bi-directional evaporation device 1 dyn runner to form ice stifled.
Air energy heat circulation exchanger, heating power triangle circulator are because the heat transfer temperature difference of differential heat transmitter is little, and condensation temperature is lower.Even as Lao Lunci circulation during: compare with present commercially available air-conditioning its coefficient of performance EER is improved greatly with Carnot cycle.
Claims (18)
1, a kind of air energy heat circulation exchanger, it is characterized in that, by air energy bi-directional evaporation device, the two-way condenser of air energy, low pressure reduction power conversion heat pump is formed, be distributed on air energy bi-directional evaporation device and the two-way condenser of air energy with the working media convection current that can be recycled utilization, utilize the air energy of drainage to change power to cause the working media that flows for storing energy on the air energy bi-directional evaporation device as heat, and on air can two-way condenser release heat, and be recycled, and air can be released energy by the bi-directional evaporation device at air simultaneously, can absorb energy on the two-way condenser in air.
2, air energy heat circulation exchanger as claimed in claim 1 is characterized in that, low pressure reduction power conversion heat pump can be carried low pressure vapour, liquid mixture.
3, air energy heat circulation exchanger as claimed in claim 1 is characterized in that, low pressure reduction power conversion heat pump comprises gas transfer pump and liquid delivery pump.
4, air energy heat circulation exchanger as claimed in claim 1 is characterized in that, by one from T
o(cold wind output temperature) is to T
K(outdoor environment temperature) reversible equipressure not decalescence process and one from T
3(the highest exhaust wet-bulb temperature of condensation air) is to T
4Adiabatic pump pressure process, an isenthalpic throttling (the also available adiabatic expansion) process of isothermal exothermic process, a constant entropy do not constitute (room air wet-bulb temperature) reversible equipressure.
5, air energy heat circulation exchanger as claimed in claim 1, it is characterized in that, air energy bi-directional evaporation device is by heat conduction, the planar metal conducting strip that it is arranged in parallel can be divided into I district and II district by the bi-directional evaporation device with air: the I district is the dxn working media runner that conducting strip and dxn heat Insulation film are formed, be that decalescence (energy storage) is not distinguished, the II district is the dyn runner that conducting strip and ripple conducting strip are formed, it is the not isothermal heat release zone of cooled air, I district and II district variations in temperature are synchronous, and the thermograde direction is opposite.
6, air energy heat circulation exchanger as claimed in claim 5 is characterized in that, the dxn heat Insulation film is to make with the bigger nonmetallic materials of thermal resistance, can be in the thermal insulation of dyn direction, cut apart the heat conduction warm area.
7, air energy heat circulation exchanger as claimed in claim 5, it is characterized in that, the dxn runner of air energy bi-directional evaporation device, be provided with liquid, vapour distributing pipe at its working media entrance and exit place, working media fluid dispensing orifice is all arranged on it, the external transfusion of dxn runner exit, letter shoot, inlet connects woven hose; The back flow plate of dxn runner is in order to separate the dxn runner, and there is loop pipe at the turning, and it is opposite that working media circuit board both sides are U font runner direction; The dxn runner also can adopt repeatedly the U font to reflux.
8, air energy heat circulation exchanger as claimed in claim 1 is characterized in that, the two-way condenser of air energy is by conducting strip heat conduction, and working media is from T in the dxn runner
3～T
4Not isothermal heat release, in the dyn runner, condensation air is from T
4～T
3Wet fully endothermic process, conducting strip both sides variations in temperature is synchronous, the thermograde direction is opposite, the working media inlet of the dxn runner that air can two-way condenser connects the liquid letter shoot, outlet connects woven hose.
9, air energy heat circulation exchanger as claimed in claim 8 is characterized in that, the film-type evaporation face is established in the conducting strip outside.
10, air energy heat circulation exchanger as claimed in claim 9 is characterized in that, the film-type evaporation mask has water storage, the good cellular structure of water imbibition.
11, air energy heat circulation exchanger as claimed in claim 1 is characterized in that, working media is azeotropic operating medium to changing.
12, air energy heat circulation exchanger as claimed in claim 1 is characterized in that, working media is non-vapor of mixture working media to changing.
13, air energy heat circulation exchanger as claimed in claim 1 is characterized in that, working media is single working media to changing.
14, air energy heat circulation exchanger as claimed in claim 1 is characterized in that, air energy bi-directional evaporation device, air can separate installation by two-way condenser.
15, air energy heat circulation exchanger as claimed in claim 1 is characterized in that, air energy bi-directional evaporation device, air can merge installation by two-way condenser.
16, air energy heat circulation exchanger as claimed in claim 15 is characterized in that, air energy bi-directional evaporation device, air can merge installation by two-way condenser, and wherein air energy bi-directional evaporation device is as indoor set, and the two-way condenser of air energy is as off-premises station.
17, air energy heat circulation exchanger as claimed in claim 15 is characterized in that, air energy bi-directional evaporation device, air can merge installation by two-way condenser, and wherein air energy bi-directional evaporation device is as off-premises station, and the two-way condenser of air energy is as indoor set.
18, air energy heat circulation exchanger as claimed in claim 15, it is characterized in that, air energy bi-directional evaporation device, air can merge installation by two-way condenser, wherein air can the bi-directional evaporation device be arranged room air heat release to cold front value temperature to outdoor, and air can two-way condenser be arranged outdoor air heating, humidification to thermal peak temperature to indoor.
Priority Applications (4)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN94106955A CN1114040A (en) | 1994-06-14 | 1994-06-14 | Air energy heat circulation exchanger |
| ZA946528A ZA946528B (en) | 1994-06-14 | 1994-08-26 | Heat circulatory exchanger using air energy |
| AU71499/94A AU7149994A (en) | 1994-06-14 | 1994-08-26 | Heat circulatory exchanger using air energy |
| GB9418432A GB2293441A (en) | 1994-06-14 | 1994-09-13 | Refrigeration/heat-pump apparatus for cooling/heating air |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN94106955A CN1114040A (en) | 1994-06-14 | 1994-06-14 | Air energy heat circulation exchanger |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN1114040A true CN1114040A (en) | 1995-12-27 |
Family
ID=5032731
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN94106955A Pending CN1114040A (en) | 1994-06-14 | 1994-06-14 | Air energy heat circulation exchanger |
Country Status (4)
| Country | Link |
|---|---|
| CN (1) | CN1114040A (en) |
| AU (1) | AU7149994A (en) |
| GB (1) | GB2293441A (en) |
| ZA (1) | ZA946528B (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1743666B (en) * | 2004-09-02 | 2011-03-30 | 淄博绿能环保设备科技有限公司 | Temperature-different two-way heat tube transfer steam-current wind-wheel generating device |
| CN103521955A (en) * | 2013-09-27 | 2014-01-22 | 宣浩 | Cooling device for welding equipment |
Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GR960100355A (en) * | 1996-10-15 | 1998-06-30 | Nutec Electrical Engineering Co. Ltd | High eer air conditioning apparatus with special heat exchanger. |
| US6098415A (en) * | 1996-12-11 | 2000-08-08 | Carrier Corporation | Combination room air/split air conditioner |
| CA2255181A1 (en) | 1997-12-02 | 1999-06-02 | Louis J. Bailey | Integrated system for heating, cooling and heat recovery ventilation |
| CN114893715B (en) * | 2022-04-02 | 2023-11-21 | 安徽宇航派蒙健康科技股份有限公司 | Heating control method and device, system, computer equipment and storage medium thereof |
Family Cites Families (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR2474666A1 (en) * | 1980-01-24 | 1981-07-31 | Inst Francais Du Petrole | PROCESS FOR PRODUCING HEAT USING A HEAT PUMP USING A MIXTURE OF FLUIDS AS A WORKING AGENT AND AIR AS A SOURCE OF HEAT |
| FR2564955B1 (en) * | 1984-05-28 | 1987-03-20 | Inst Francais Du Petrole | PROCESS FOR PRODUCING HEAT AND / OR COLD USING A COMPRESSION MACHINE OPERATING WITH A MIXED WORKING FLUID |
-
1994
- 1994-06-14 CN CN94106955A patent/CN1114040A/en active Pending
- 1994-08-26 ZA ZA946528A patent/ZA946528B/en unknown
- 1994-08-26 AU AU71499/94A patent/AU7149994A/en not_active Abandoned
- 1994-09-13 GB GB9418432A patent/GB2293441A/en not_active Withdrawn
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1743666B (en) * | 2004-09-02 | 2011-03-30 | 淄博绿能环保设备科技有限公司 | Temperature-different two-way heat tube transfer steam-current wind-wheel generating device |
| CN103521955A (en) * | 2013-09-27 | 2014-01-22 | 宣浩 | Cooling device for welding equipment |
Also Published As
| Publication number | Publication date |
|---|---|
| GB9418432D0 (en) | 1994-11-02 |
| GB2293441A (en) | 1996-03-27 |
| ZA946528B (en) | 1996-02-27 |
| AU7149994A (en) | 1995-12-21 |
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