GB2293441A - Refrigeration/heat-pump apparatus for cooling/heating air - Google Patents
Refrigeration/heat-pump apparatus for cooling/heating air Download PDFInfo
- Publication number
- GB2293441A GB2293441A GB9418432A GB9418432A GB2293441A GB 2293441 A GB2293441 A GB 2293441A GB 9418432 A GB9418432 A GB 9418432A GB 9418432 A GB9418432 A GB 9418432A GB 2293441 A GB2293441 A GB 2293441A
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- United Kingdom
- Prior art keywords
- heat
- air energy
- air
- bilateral
- evaporator
- Prior art date
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Links
- 238000001816 cooling Methods 0.000 title claims abstract description 32
- 238000010438 heat treatment Methods 0.000 title claims abstract description 22
- 238000005057 refrigeration Methods 0.000 title description 8
- 239000000126 substance Substances 0.000 claims abstract description 37
- 238000001704 evaporation Methods 0.000 claims abstract description 18
- 239000007788 liquid Substances 0.000 claims abstract description 15
- 230000008020 evaporation Effects 0.000 claims abstract description 12
- 239000012530 fluid Substances 0.000 claims abstract description 3
- 238000000034 method Methods 0.000 claims description 59
- 230000002146 bilateral effect Effects 0.000 claims description 33
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims description 24
- 230000002441 reversible effect Effects 0.000 claims description 15
- 230000009466 transformation Effects 0.000 claims description 6
- 239000000463 material Substances 0.000 claims description 4
- 239000002184 metal Substances 0.000 claims description 3
- 229910052755 nonmetal Inorganic materials 0.000 claims description 3
- 239000000203 mixture Substances 0.000 claims description 2
- FNYLWPVRPXGIIP-UHFFFAOYSA-N Triamterene Chemical compound NC1=NC2=NC(N)=NC(N)=C2N=C1C1=CC=CC=C1 FNYLWPVRPXGIIP-UHFFFAOYSA-N 0.000 claims 2
- 241000009298 Trigla lyra Species 0.000 claims 1
- 238000010586 diagram Methods 0.000 abstract description 22
- 239000003507 refrigerant Substances 0.000 abstract description 13
- 230000002745 absorbent Effects 0.000 abstract description 5
- 239000002250 absorbent Substances 0.000 abstract description 5
- 239000007791 liquid phase Substances 0.000 abstract 2
- 238000009833 condensation Methods 0.000 description 16
- 230000005494 condensation Effects 0.000 description 16
- 230000005540 biological transmission Effects 0.000 description 14
- 239000007789 gas Substances 0.000 description 5
- 230000000052 comparative effect Effects 0.000 description 4
- 230000000694 effects Effects 0.000 description 4
- 238000010521 absorption reaction Methods 0.000 description 3
- 230000007423 decrease Effects 0.000 description 3
- 239000007921 spray Substances 0.000 description 3
- PEDCQBHIVMGVHV-UHFFFAOYSA-N Glycerine Chemical compound OCC(O)CO PEDCQBHIVMGVHV-UHFFFAOYSA-N 0.000 description 2
- 238000004378 air conditioning Methods 0.000 description 2
- QVGXLLKOCUKJST-UHFFFAOYSA-N atomic oxygen Chemical compound [O] QVGXLLKOCUKJST-UHFFFAOYSA-N 0.000 description 2
- 230000002427 irreversible effect Effects 0.000 description 2
- AMXOYNBUYSYVKV-UHFFFAOYSA-M lithium bromide Chemical compound [Li+].[Br-] AMXOYNBUYSYVKV-UHFFFAOYSA-M 0.000 description 2
- KWGKDLIKAYFUFQ-UHFFFAOYSA-M lithium chloride Chemical compound [Li+].[Cl-] KWGKDLIKAYFUFQ-UHFFFAOYSA-M 0.000 description 2
- 229910052760 oxygen Inorganic materials 0.000 description 2
- 239000001301 oxygen Substances 0.000 description 2
- 230000009897 systematic effect Effects 0.000 description 2
- 101100010712 Caenorhabditis elegans dyn-1 gene Proteins 0.000 description 1
- 239000006096 absorbing agent Substances 0.000 description 1
- 238000003915 air pollution Methods 0.000 description 1
- 230000003750 conditioning effect Effects 0.000 description 1
- 230000003247 decreasing effect Effects 0.000 description 1
- 230000007547 defect Effects 0.000 description 1
- 238000005265 energy consumption Methods 0.000 description 1
- 230000007613 environmental effect Effects 0.000 description 1
- 235000011187 glycerol Nutrition 0.000 description 1
- 239000005457 ice water Substances 0.000 description 1
- 238000009413 insulation Methods 0.000 description 1
- 230000004060 metabolic process Effects 0.000 description 1
- 239000007769 metal material Substances 0.000 description 1
- 230000001360 synchronised effect Effects 0.000 description 1
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
-
- 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
Landscapes
- 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)
- Other Air-Conditioning Systems (AREA)
- Sorption Type Refrigeration Machines (AREA)
Abstract
Apparatus for cooling heating air comprises an evaporator 1, a condenser 2, and a low pressure difference heat-pump 15. A working substance pair (i.e. working fluid of the apparatus) comprises a refrigerant and an absorbent. In the evaporator one substance of the pair is evaporated to provide a gas/concentrated liquid phase. This is accomplished by heat exchange with atmospheric air which is cooled for supply to a room. The pressure of gas/liquid phase is increased by pump 15 and is supplied to condenser for return to a dilute solution of the working substance pair by heat exchange with air exhausted from the room. The condenser has a film evaporation surface (6, Figure 5). Throttle 17 expands the dilute solution of the working substance pair before return to the evaporator. Pump 15 may comprise a liquid pump and a vapour pump. In the T-S diagram for the apparatus the heat-absorbing arc and heat-releasing arcs intersect at point J (see figure 1). <IMAGE>
Description
HEAT CIRCULATORY EXCHANGER USING AIR ENERGY
BACKGROUND OF THE INVENTION
Air conditioner is used to condition the energy state and the air quality in a room so as to satisfy PeoPle's requirment for comfort and physi logical hygiene. The source of air pollution in a room mainly comes from indoor things and metabolism of human body. The airflow cycle sealed hermetically in a room means that the indoor air polluted after absorption refrigeration is a repeated vicious cycle of the dirty degree aggravated sucessfully. It is very harmful for peoPle's health. Using 100% fresh air, corresponding power consumed will increase over 1.2 times.
Such high energy consumption and energy exchange efficiency are the most defect of the current air conditioners.
In other words, to meet the need for oxygen amount in a certain room and the need for necessary refrigeration (heating), it is necessary for the popular civil air conditioners to consume such high power.
The second law of thermodynamics points out that heat can transfer from a high temperature object to a low temperature object spontaneously, but can't transfer from a low temperature object to a high temperature object spontaneously. Carnot cycle and Lornty cycle are ideal cycle of the highest thermodynamic efficiency and also are the guide theory of the various air conditioners. The refrigerating process of the current air conditioners developed by above theory all needs to consume high grade energy that thermal energy can be pumped from a low temperature object to a high temperature object. Hence the refrigerating process must be that "the high grade energy is consumed and devalued". Moreover, thermodynamic cycle efficiency of the current air conditioners is far lower than
Carnot cYcle efficiency.
With the help of the air energy refrigerated (the outdoor hot air energy is higher than the indoor), can the energy in the refrigerating cycle be compensated? This makes the refrigerating process of energy consumed reverse one of the energy stored and power produced. As long as the energy obtained is more than or equal to the energy needed in refrigerating process, the refrigerating system can be worked automatically. Of course9 this needs slight high evaporating temperature and slight low condensing temperature. And in the exchange heat process, the necessary cooling (heating) valley temperature for the air conditioning can be obtained.
SUMMARY OF THE INVENTION
The present invention relates to a low pressure difference heat-pump air conditioner using air energy as its main refrigerating (heating) circulatory power. The low pressure difference heat-PumP can be conveyed by mixing up liquid and air or by separating liquid and air. Air energy referring to the energy existing in the natural air that can be used for cooling or heating. The slight separate cooling pipe is a high efficient heat exchanger which has large density of heat flow rate and can make the end heat transmission temperature difference to tend towards zero infinitely. Working substance pair means the combination of refrigerant and absorbent, such as water and LiBr, or NH3 and water, or water and LiCl.The present invention, the heat circulatory exchanger which is an air conditioner providing Purely fresh air, is comprised of an air energy bilateral evaporator (hereafter as AEB evaporator), an air energy bilateral condensor (hereafter as AEB condensor), low pressure difference enrgy transmission heat-pumP (hereafter as LPDET heat-pump). Its temperature-entropy diagram tends to be a cross-like thermodynamic cycle and can make the most of the air energy to compensate the power circulation needed in the process of cooling (heating) so as to have high thermodynamic cycle efficiency. Another character of the heat circulatory exchanger is that cool or heat output in an air conditioning system both needs 100% outdoor fresh air to obtain the best thermodynamic cycle efficient.
The present invention has an effect on cooling and heating by using outdoor hot air as its power directly. The current condensor has outdoor temperature #T 13-15"C, and the evaporator has evaporating temperature A T 8-120, and this invention has A T 0.1-0.5 C, so the heat transmission can be obtained by means of air energy.
In other words, the present invention uses 100% outdoor air to flow through the device of the invention and lead out the cool (hot) air, so it can not only gain the necessary oxygen but also use the high (low) temperature of outdoor fresh air to form the cycle. In theory, it EER is very high. That is, use the lowest energy loss to produce the highest cooling (heating) effect.
In the circulatory process of the Present invention, working substance cycle is different from the conventional type; the difference is that the conventional type of absorption has four parts, that is, evaporator, generator.
condenser, and absorber; as for the present invention, its evaporater includes the function of a generator. and its condenser includes the the function of a generator, and its condenser includes the function of an absorbor; the generater of the convention type has to use wasted heat or vapor, and evaporater has to use ice water to make secondary heat exchange, but the present invention doesn't need to use them.
BRIEF DESCRIPTION OF THE DRAWINGS:
FIG 1 is a T-S diagram (temperature-entroPY diagram) of
thermodynamic cycle of the present invention.
FIG 2 is a T-S contrast diagram of the ideal Carnot cycle
and Lorenty cycle and the thermodynamic cycle of the
present invention.
FIG 3 is a schematic diagram of the refrigerating process of
the heat circulatory exchanger.
FIG 4 is a sectional view of A-A in FIG 3.
FIG 5 is a sectional view of B-B in FIG 3.
FIG 6 is a comparative view of applied working substance of
the present invention Carnot cycle, and Lorenty cycle.
FIG 7 is a P-h (Pressure enthalPY) comparative diagram
corresponding to FIG 6.
FIG 8 is a T-S diagram of a thermodynamic triangle cYcle of
changed from a thermodynamic cycle of the present
invention.
FIG 9 is a window type embodiment of the thermodynamic cycle
of the present invention.
DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT
Now referring to FIG. 1, a T-S diagram (temperature entropy diagram) of thermodynamic cycle of the present invention,
T2 is a heating valley temperature, namely the outside dry bulb temperature.
T2=Tk, (the heating valley means the highest temperature point); T1 is a cooling valley temperature, namely the output temperature of cold wind.
T1=TO. (the cooling valley temperature, means the lowest temperature);
T4 is the wet bulb temperature of an conditioning room;
T3 is the exhaust temperature of the condensation air.
I area: 1-J-2 is that the refrigerating working substance is from TO-Tk continuously change temperature endothermic (store air energy) process.
Corresponding Ir area : 2-J-1 is that the refrigerated air is from Tk-TO continuously change temperature exothermic process;
m area: 3-J-4 is that the refrigerating working substance is from T3-T4 continuously change temperature exothermic process;
Corresponding 1", area: 4-J-3 is that the condensation is continuously change temperature endothermic process in full humidity;
2-3: the adiabatic pump process from the high temperature to the low temperature (Then3); 4-1: the adiabatic expansion process.
The area of t1J4 is the necessary work Wi in the refrigerating cycle; the area of /\2J3 is the obtainable air energy W2 in the refrigerating cycle. W2 can be fully converted into the useful work. J point is the intersection of the endothermic line and the exothermic line of the refrigerating working substance.
#1J4 of the anti-clockwise trend is the refrigerating machine in air energy engine in heat circulatory exchanger.
J point is the series point of the refrigerating machine and air energy engine.
In the refrigerating cycle the work of necessary compensation is W1-W2=/W.
The rate of the thermodynamic energy efficiency EER= Gen/ W. Qen is the refrigerating quantity. When W2 > =W1, it can work automatically with the helP of the air energy W2.
now KER > oo.
While the cooling valley temperature TO decreases, T4 will follow downworks, J point will do so, meanwhile W1 and
W2 will be increased, whereas /W = W1-W2 will not be increased. It is thus evident that heat circulatory exchanger obtains the air energy W2 in the refrigerating process of consumption work.
As shown in FIG.2, a T-S contrast diagram of the ideal
Carnot cycle and Lorenty cycle and the thermodynamic cycle of the present invention:
the T-S diagram of Carnot cycle
the T-S diagram of Lorenty cycle
the T-S diagram of thermodynamic cycle of the present invention
Under the condition of the same Tk and To, the consumption work of the Carnot cycle is the maximum and its refrigeration quantity is the minimum, but the refrigeration quantity of the thermodynamic cycle of the present invention is maximum and its consumption work is the minimum; and the
Lorenty cycle is between the Carnot and the thermodynamic cycle of the present invention. The large the temperature difference of Tk and To, the more evident the contreast above.
The heat transmission process of the present invention is the full and infinite differential nonisotherm process, which temperature difference of the end heat transmission infinitelu tends to zero. So it may be thought that 1-J-4 are a process of the reversible continuous change temperature, the thermodynamic cycle of the present invention is formed by the processes of two reversible continuous change temperature and two isentropy.
As shown in FIG.3, a schematic diagram of the refrigerating process of the heat circulatory exchanger.
the AEB evaporator 1 is exchanged heat by heat conduction piece 5. According to FIG.4, parallel arrangement heat conduction piece 5, which is plane form metal, divides the AEB evaporator 1 into I area and E area.
I area is the infinite differential non isotherm endothermal area (storing energy) of To-Tk refrigerating working substance comPosed of heat conduction piece 5 and dxn differential heat insulated piece 20; Ir area is the infinite differential non isotherm area of Tk-To refrigerated air comPosed of heat conduction piece 5 and corrugated heat conduction piece 7 (dyn flow duct). As corrugated conduction piece 7 is made of the thin metal material, the heat conduct Ion quantity of dyn direction may be thought zero.In dun direction heat conduction piece 5 can be adiabatically separated into many stripe temperature area, next the exchange heat area of heat conduct on piece 20 and air can be increased. dxn differential heat insulated piece is made of the nonmetal material that the thermal resistance is large. In dxn direction heat conduction piece can be adiabatically separated into many striPe temperature area.Therefore the heat conduction piece is separated adiabatically into innumerable (dxn, dyn) differential isotherm heat conduction area, whereas the temperature of each differential isotherm area and adjacent differential isotherm area (dxn1,dyn) or (dxy,dYn-1) is not equal, and the temperature diference of that trends to zero. As heat conduction area of AEB evaporator 1 is an infinite differential isotherm one, AEB evaporator 1 may be thought from To-Tk (or Tk-To) continuous change temperature heat conduction area and the change temperature process of two side is synchronous.
By supply air fan 12 outdoor air al at heating valley temperature Tk fully makes heat conduction piece 5 heat with continuous change temperature along a2 direction in the dy flow duct of Ir area. Cold wind a3, which gives out heat to cooling valley temperature To, is input into the indoor via outlet wind adiustment shutter 14, and its refrigerated process in the T-S diagram corresponds to the continuous change temperature exothermic process of 2-J-1 (Tk-To).
Dilute solution gl made up of absorbent i and refrigerant x evenly distributes to each gl distributing tube via transporting liquid tube 16 and sprays each dxn flow duct of the parallel arrangement in Iarea by jet hole.
according to g1#g12#g2 direction flows. Return tube 11 is the turning of dxn flow duct. The endothermal process of gl- > gl2-+g2 in dxn flow duct in T-S diagram corresponds to the continuous change temperature endothermal process of 1-j-2 (To-Tk). Under the isobaric state P1, through full and continuous change temperature gl is heated from cooling valley temperature To to heating valley temperature Tk.
Gradually absorbing heat, the liquid refrigerant x contained in gl is evaporated the gas refrigerant x2 of superheat temperature Tk-To=t T. Corresponding g1 is also changed to concentrated solution g2 of super heat temperature ffT The exchange heat process of AEB evaporator 1 is completed on the differential isotherm area, whereas each differential isotherm area always makes the temperature of a working substance pair i, x of two side of the heat conduction piece 5 and refrigerated air infinitely tend to isotherm. and the temperature difference of the end heat transmission must tend to zero. Hence the endothermal process from To-Tk of refrigerating working substance pair is a reversible process without heat loss.But the heat exchange is G,1-0,5 degree C, and it is not necessary that makes the heat transmission temperature difference tend to zero.
The performance of heat pump of AEB evaporator 1 shows: g2 and x2 is superheat intensely. In To-Tk reversible endothermal proces T the part of air energy W2 is stored.
And the refrigerating process is also store energy process.
AEB condenser 2 is also exchanged heat by heat conduction piece 5. According to FIG 5, parallel arrangement heat conduction piece 5, which is plane form metal, divides the AEB condenser 2 into m area and IV area.
m area is the exothemal area, where refrigerating working substance pair g2 and x2 made up of heat conduction piece 5 and dxn differential heat-insulated piece 20 is condensed liquefaction from T3-T4 continuous non-isotherm. In T-S diagram it corresponds to 3-j-4. The condensation air side corresponding to m area is IV area. IV area is the infinite differential non-isothermal enditherm area in full humidity of the condensation air from T4-T3. which is made up of heat conduction pieces and dyn differential heat-insulated piece 21. In T-S diagram it corresponds to 4-j-3.The outside of heat conduction piece 5 is pasted the film evaporation surface 6 made of the porous absorbant material, which is of the performance of good carrier water, absorption water and larger porous surface area. The performance of carrier water can greatly increase the coefficient of heat transmission of film evaporation surface 6 and heat conduction piece 5 ; and the porous performance can form a large humidity evaporation surface area that makes the condensation process become the endothermal process of the relatively low temperature in full humidity.
As the specific heat of moist air in given pressure Cp1 is greatly large than the dry air Cp2, the temperature difference of T4-T3 is relatively small. dxn differential heat insulated piece 20 and dyn differential heat-insulated piece 21 are both made of nonmetal material that has greater thermal resistance. The two side of heat conduction piece 5 are divided into innumerable (dxn.dYn) differential isotherm heat conduction area by differential insulation that makes heat conduction piece 5 if AEB condenser 2 becomes heat conduction area of continuous change temperature from T4-T3.
After taking heat and humidity in the house, cold wind a3 from AEB evaporator 1 becomes a4 that the comfort degree of humidity. Then a4 is drawn to the dyn flow duct of IV area by exhuast fan 19, and along the direction of a5 fully absorbs the moisture on the film evaporation surface 6, and finally exhausts to atmosphere after turning to saturation state a6 increased the wet bulb temperature from T4-T3.
g2 and x2 from AEB evaporator 1 that the pressure is P1 are Pressurized to P2 by LPDET heat-pump 15, than are divided to each liquid-gas distributing tube 3 of AEB condenser 2 through liquid-gas transporting tube 13, and jetted to dxn flow duct of m area from the jet hole, along the direction of g2- > gl full given out heat continued non-isotherm from T3-+T4, and gradually made liquefaction to become subcoolling weak solution gl, subcooling weak solution gl is flown to AEB evaporator 1 by transporting liquid tube 16 and nerottle valve 17. And like cycle above is again and again.
The exchange heat Process of AEB condenser 2 is also completed on the heating non-isothermal heat conduction area of infinite differential, and the heat transmission temperature difference of the end heat must tend to zero, so it is both a reversible continuous change temperature process that the condensed process from T3-+T4, and corresponding from T4- > T3 the condensation air endothermal process in full humiditY.
Under the condensation state of T3-3T4 relatively low temperature, the superheat rich solution g2, which surface pressure is far lower than P2, has the ability of absorbing the gas refrigerant x2 intensely and causing to liquefaction extherm. So the performance of super condensation of AEB condensor 2 is shown in two respects of condensation of low temperature and low pressure, which is the result of double effects: W2 of g2 store and condensation of low temperature T3-+T4 super condensation may also make gl weak solution subcool ing, increase refrigeration quanting and decrease To further.And these all make the system completely a good-cycle In the practical cycle, non-isotherm transmission heat temperature difference of AEB evaporator 1 and AEB condenser 2 are controlled between 0.1-0.5 degree C. It is not essential that the transmission heat temperature difference must be tended to zero. For the reason there are still a few irreversible exergy loss in the process of 1-J-2 and 3-J-4. On the other hand, with fluid of refrigerating working substance pair flowing and dividing repeatedly.
there must be friction resistance. The process of 4-1 is not a isentropic process but an isenthalpic throttling pressure- decreasing process. Therefore, there must be also the irreversible exergy loss.
Exergy loss formed by the irrversible process above shows the loss of the systematic net work ZXW1. Hence the work Wm that the ehermodynamic cycle of the heat circulatory exchanger has to complete is equal to Wm=nW1 A W. Wm is more than dEW which is the compensate work needed for the ideal heat circulatory exchange cycle. Wm is supplied by the LPDET heat-pump 15.The effect of LPDET heat-pump 15 is to make the liquid g2 and gas x2 at the same time increase pressure from P1 to P2 and transport to the inlet of condenser 2, and make absorbent and refrigerant carry out thermodynamic operation according to FIG.3 which finishes the process of energy transportation and transformation process;
Because the transmission heat temperature difference of
AEB evaporator 1 and AEB condenser 2 is relatively small, so is P2-PI= EXP, and the isentralpic throttling exergy loss of 4-1 process and the exergy loss if the refrigerating working substance produced by frictional resistance of liquid are still small. For these reasons the systematic net work loss must be also small.Obviously, heat circulatory exchanger has not only great theoretical EER value but also great thermodynamic perfect degree Under the standard test working conditions, the practical EER m = Qen/Wm can reach 20-35.
FIG 6 is a comparative view of TS diagram;
the heat circulatory exchanger whose working substance is comprised of absorbent and refrigerant;
Carnot refrigerator whose working substance is azeotropy or single refrigerant;
Lorenz refrigerator whose working substance is non-azeotropic mixture refrigerant; FIG 7 is a
P-h (Pressure enthalpy) comParative diagram corresponding to
FIG 6. The current Carnot and Lorenty cooler (except large air conditioner) use wind cooling condenser and wind cooling evaporator. Because the condensing temperature of the wind cooling condenser is 13-15 degree C higher than the outdoor temperature. The evaporating temperature of wind cooling condenser is 8-12 degree C lower than the outlet of the cool wind.Under the same cool wind output temperature and the same Tk environmental temperature, the transmission heat temperature difference of differential heat transmissioner of the heat circulatory exchanger is 0.1-0.5 degree C. The condensing temperature of Carnot and Lorenty cooler is higher than Tk and its cooling pressure is bigger than P2.
but its evaporating temperature is lower than To and its evaporating pressure is lower than P1. From the comParison between FIG 6 and FIG 7, in the practical cooling system, the higher the cooling pressure, the lower the evaporating temperature, the bigger the loss of work, and the smaller the cooling quantity; if: work loss of Carnot cooler is Wc, cooling quantity Qc, EEKc work loss of Lorenty cooler is WL, cooling quantity QL, EERL work loss of the exchanger is Wm, cooling quantity Qm, EERm : Wc > WL > Wm and Qm > QL > Qc :EERm > EERL > EERc
the air energy heat circulatory exchanger has higher air intake superheat temperature, this Part of heat is carried by the temperature increase from the absorbant, so the exchanger must use absorbant which has large capacity and higher heat conduction coefficient; and it has larger subcool ing temperature, (the result of super refrigerating) so the cooling quantity Am is larger than Qc and QL, because the EER value of Carnot, Lorenty cooler is lower, they can not use 100% fresh air, whereas the present invention uses 100% fresh air so it has the best thermodynamic cycle efficiency.
As shown in FIG 3, outdoor air al with moisture X1 releases heat in the AEB evaporator 1 to the cool wind a3 of the cold valley temperature To, the moisture of a3 decreases to X2 and the water condensation of the input cold wind per
Kg is X1-X2= OX1. AX1 drops into water pan 10 and then flows from Pipe into chaddis 9 for water collection, and the time is set by a water pump 23 and water is sprayed from a flow nozzle 18 to the film evaporation surface 6 of AEB condenser 2.The condensation of AEB condenser 2 is a process of wet heat-absorbing. indoor air a4 of moisture X3 absorbs steam from the film evaporation surface 6 to become wet air a6 of moisture X4 per Kg and will be exhausted outdoors, the consumed water quantity of its exhausted air is X4-X3= E9X2. the input air of the heat circulatory exchanger in every period of time is equal to the output air, so when AX1= nX2, it is at the water balance point.
Because the moisture of natural air and the indoors wet load
X3-X2 can not be Predetermined (they are in active state) the stored water quantity in the chaddis 9 is A X2 > X1, it should be automatically supplied by water supplier, when it is AXl > A X2. it should be guided out automatically.
Now referring to FIG.3 and FIG.8, when AEB evaporator 1 is used as an indoor machine and when AEB condenser 2 is used as an outdoor machine: the condensed air of the AEB condenser 2 is absorbed from outdoor and then exhausted to outdoor (similar to the current separate type air conditioner). The T-S diagram of air energy heat circulatory exchanger becomes
the T-S shaped circulatory Figure in FIG 6 (hereafter called thermodynamic triangle cycle machine).
T2 is dry bulb temperature of indoor air.
T4 is wet bulb temperature of indoor air.
T3 is exhaust wet bulb temperature of air energy bilateral condenser 2.
To=T1 is the cooling valley temperature and the cool wind temperature of the AEB evaporator 2.
When thermodynamic triangle cycle machine is practically operated, T2 is changeable. When T2=T3. J point is overlapped with T1 and T3 at one point, W2=0 . when T3 > T2, J point will disappear. The thermodynamic triangle cycle machine and the heat circulatory exchanger are of the same system and are all comprised of two reverse continuous heat transformation processes, one isulated pump convey process, and one isenthalpic throttling process.
If the thermodynamic triangle cycle machine and the heat circulatory exchanger are of the same cooling valleY temperature To.
because: T2 < Tk, Tk is outdoor envirnmental temperature; T4 < Ts. Ts is outdoor air wet bulb temPerature;
that is, hot valley temperature of the thermodynamic triangle cycle machine is lower than the heat circulatory exchanger, and its condensing temperature is higher than air energy heat circulatory exchanger; because Tk-Ts > T2-T4, so the air energy stored by the thermodynamic triangle cycle machine in cooling process is smaller than air energy heat circulatory exchanger. Then the work WM' input to the system by the thermodynamic triangle cycle machine must be bigger than the work WM the heat circulatory exchanger needs. But the thermodynamic triangle cycle machine also can store air energy in the energy-consuming condensation process.And the heat-pump efficiency of the AEB evaporator 1 and the super condensation of the AEB condenser 2 are still existed. And the irreverible loss in the heat-transmission is smaller, so it has higher thermodynamic circulatory efficiency; that is the function efficiency EER.
If the refrigerating work substance pair in the thermodynamic triangle cycle machine is changed into nonazeotropic mixed refrigerant, the thermodynamic triangle cycle will become
Lorenz cycle as shown in FIG. 8.
The work WL > 2WM' the Lorenz cycle needs can be seen in
FIG.8; and because the area under the heat- absorbing line 1-2' is smaller than the area under the heat-absorbing line
Q1-J-2 of the thermodynamic triangle cycle machine; so the function coefficient EER of the thermodynamic triangle cycle machine is twice as much as Lorenty refrigerator. If the refrigerating work substance pair in the thermodynamic triangle cycle machine is changed into azeotropic refrigerant or single refrigerant, its function coefficient
EER must be lower down further. Because Lorenz and Carnot refrigerator may not use the air energy in the regrigerating
Process, the heat-pump efficiency of the AEB evaporator 1 and the super condensation of the AEB condenser 2 will not exist any more.So the thermodynamic triangle cycle machine and the heat circulatory exchanger can obtain the most function coefficient only when they use refrigerating work substance pair.
Air enrngy heat circulatory exchanger can be made as a window-type machine. FIG.g shows a window type heat circulatory exchanger. Above its central line is the AEB evaporator 1, below its central line is the AEB consenser 2.
Outdoor natural air al is driven by supply air fan 12 to pass through dyn channel of the AEB evaporator 1 and release heat to the input room a3 of cooling valley temperature TO.
Because of the exhaust/intake function of the exhaust fan 19, indoor air a4 passes through exhaust adjusting blade 28 and then turns its direction to carry moisture and heat on the film evaporation surface 6 of the dyn channel of the AEB condenser 2 and finally is, in a6 state, exhausted into the atmosphere. A return flow panel 27 of AEB evaporator 1 and
AEB condenser 2 is used to separate dxn channel so as to make the refrigerating working subatance pair flow in a "U" shaped direction in the differential heat transmissioner.
The flow nozzle 18 sprays vapor of set quantity onto the film evaporation surface 6 of the AEB consenser 2 at predetermined time in the process of refrigeration to make the surface 6 wet in time. Water pump 23 intermittently supplies water of set quantity for electro-magnetic control valve 24 at predetermined time; control valve 24 provides water for nozzle 18 in the process of refrigeration and provides water for heating nozzle 26 in the process of heating. Water filter 22 can prevent pollution from entering the water supply system.
When the air energy circulatory exchanger is operated for heating (heating pump): the AEB evaporator 1 is the same, it only outputs cooling valley to the outdoors. The
AEB condenser 2 is the same, except that it inputs the heating valley into thr indoors. So the whole combination has to make a change as follows:
1. Exchange the inlet of the AEB evaporator 1 and AEB condenser 2 to outlet and at the same time exchange their outlet to inlet so as to make the refrigerating work substance pair to operate in reverse direction.
2. Make the supply air fan 12 operate in reverse direction and become an exhaust fan 19 so that air can be exhausted from the indoor to the outdoor. Indoor air passes through dyn channel of the AEB evaporator 1 and releases heat to cooling valley temperature and then will be exhausted into the atmosphere. Make the exhaust fan operate in reverse direction and become a supply air fan so that outdoor fresh air can pass through dyn channel of AEB condenser 2 to absorb heat and moisture to heating valley temperature and then will be input into the indoor.
3. Under the control of electro-magnetic control valve 24 and water pump 23, the heating nozzle 26 at the left side of the AEB evaporator 1 and at the right side of the AEB condenser 2 can spray vapor onto the AEB evaporator 1 and
AEB condenser 2 to wet the film evaporation surface of the
AEB condenser 2 and to solve the frost collected in the dyn channel of the AEB evaporator 1. Add some glycerine solution into the water collection chaddis 9 to reinforce the heat exchange performance of AEB evaporator 1 and AEB condenser 2, and prevent the dyn channel of the AEB evaporator 1 from being barriered by ice.
Because the heat transmission temperature difference of the differential heat transmissioner is very small and its condensing temperature is low, even if it is used for Lorenz and Carnot cycle, the performance coefficient EER of the air energy heat circulatory exchanger and the thermodynamic triangle cycle machine will become much higher than the conventional air conditioner.
Claims (18)
1. A heat circulatory exchanger using air energy comprising an air energy bilateral evaporator, an air energy bilateral condenser, and a low pressure difference energy transformation heat-pumP, wherein air energy bilateral evaporator and air energy condenser being flown by recycle working substance pair, by using the guided air energy as a heat transformation power to make the fluid working substance pair store energy in the air energy bilateral evaporator and release heat in the air energy bilateral condenser, and to be cYcled so that the air can release energy in the air energy bilateral evaporator and aborb energy in the air energy bilateral condenser at the same time.
2. As claimed in Claim 1. a heat circulatory exchanger using air energy, wherein low prssure difference energy transformation heat pump can carry low pressure vapor and liquid mixture.
3. As claimed in Claim 1, a heat circulatory exchanger using air energy, wherein low prssure difference energy transformation heat pump can be comprised of vapor-carry pump and liquid-carry pump.
4. As claimed in Claim 1, a heat circulatory exchanger using air energy, its characteristic is : it is comprised of a process of reversible isobar non isotherm heat-absorbing process from To (cold wind output temperature) to Tk (outdoor environment temperature) , a process of reversible isobar non isotherm heat-releasing process from T3 (condensing air highest exhaust wet bulb temperature) to T4 (indoor air wet bulb temperature) an isenthalpic insulated process, and a isenthalpic throttling ( insulated heat exPansion).
5. As claimed in Claim 1, a heat circulatory exchanger using air energy, wherein the air energy bilateral evaporator has the characteristic : the air energy bilateral evaporator is passed by conducting heat, its
Parallel arrangement heat conduction piece, which is plane form metal, divides the evaporator into I area and Ir area.
I area is the infinite differential non isotherm endothermal area (storing energy) refrigerating working substance pair composed of heat conduction piece and dxn differential heat insulated piece; Ir area is the infinite differential non isotherm area of dyn channel, and its refrigerated air comPosed of heat conduction piece and corrugated heat conduction Piece. I and Ir area temperatur change synchronously and their temperature gradient direction is reverse.
6. As claimed in Claim 5. dxn differential heat insulated piece is made of the nonmetal material that the thermal resistance is larger, so in dxn direction heat can be insulated, and separated into heat conduction area.
7. As claimed in Claim 5, the dxn channel of bilateral evaporator has a liquid and vapor delivery pipe at the outlet and inlet of its working substance pair, and has working substance liquid delivery holes on them, outlet of dxn channel connects to liquid and vapor carry pipers outward; and its inlet connects to a liquid carry pipe; the return flow panel of dxn channel is used to separate dxn channel, and there disposed a return PiPe at the turning corner, the two sides of the working substance return panel tends to be "U" shaPed channel and its flow direction is reverse: dxn channel can be several return flows in "U" shaped flow direction.
8. As claimed in Claim 1, a heat circulatory exchanger using air energy, wherein the air energy bilateral condensor has the characteristic : air energy bilateral condensor conducts heat through heat conducting piece, the working substance Pair in the dxn channel from T3-T4 non-isotherm release heat, in the dyn channel, condensing air is in an entirely wet absorbing process from T4- T3, the temperature of two sides of the heat-conducting piece is changed synchronously, temperature gradient direction is reverse, the working substance pair inlet of the dxn channel of the bilateral condenser can be connected to a liquid vapor carry
Pipe and its outlet is connected to liquid carry pipe.
9. As claimed in Claim 8, air energy bilateral condenser, wherein heat conducting piece having film evaporation surface disposed at outer side of the heat-conductive Piece.
10. As claimed in Claim 9, the film evaporation surface has a porous structure of good water-carry and water absorbing performance.
11. As claimed in Claim 1, a heat circulatory exchanger using air energy, wherein the working substance pair is changed to become azeotropic working substance.
12. As claimed in Claim 1, a heat circulatory exchanger using air energy, wherein the working substance Pair is changed to become non-azeotropic working substance.
13. As claimed in Claim 1, a heat circulatory exchanger using air energy, wherein the working substance pair is changed to become a single working substance.
14. As claimed in Claim 1, a heat circulatory exchanger using air energy, wherein the air energy bilateral evaporator and the air energy bilateral condenser are installed separatedly.
15. As claimed in Claim 1. a heat circulatory exchanger using air energy, wherein the air energy bilateral evaporator and the air energy bilateral condenser are installed combinedly.
16. As claimed in Claim 15, the air energy bilateral evaporator and the air energy bilateral condenser installed combinedly, wherein the air energy bilateral evaporator is used as an indoor machine and the air energy bilateral condenser is used as an outdoor machine.
17. As claimed in Claim 15, the air energy bilateral evaporator and the air energy bilateral condenser installed combinedly, wherein the air energy bilateral evaporator is used as an outdoor machine and the air energy bilateral condenser is used as an indoor machine.
18. As claimed in Claim 15, the air energy bilateral evaporator and the air energy bilateral condenser installed combinedly, wherein the air energy bilateral evaporator releases the heat of indoor air to the cooling temperature and then exhausts air out of door and the air energy bilateral condenser heats and moistens the outdoor air to the heating valley temperature and then exhaust the air into the indoor.
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 (2)
| Publication Number | Publication Date |
|---|---|
| GB9418432D0 GB9418432D0 (en) | 1994-11-02 |
| GB2293441A true GB2293441A (en) | 1996-03-27 |
Family
ID=5032731
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| GB9418432A Withdrawn GB2293441A (en) | 1994-06-14 | 1994-09-13 | Refrigeration/heat-pump apparatus for cooling/heating air |
Country Status (4)
| Country | Link |
|---|---|
| CN (1) | CN1114040A (en) |
| AU (1) | AU7149994A (en) |
| GB (1) | GB2293441A (en) |
| ZA (1) | ZA946528B (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO1998026223A1 (en) * | 1996-12-11 | 1998-06-18 | Springer Carrier S/A | Combination room air/split air conditioner |
| GR960100355A (en) * | 1996-10-15 | 1998-06-30 | Nutec Electrical Engineering Co. Ltd | High eer air conditioning apparatus with special heat exchanger. |
| GB2332048A (en) * | 1997-12-02 | 1999-06-09 | Louis J Bailey | Integrated heatihg,cooling,air conditioning & heat recovery system |
Families Citing this family (4)
| 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 |
| CN112174241B (en) * | 2020-10-26 | 2024-12-24 | 清华大学 | A porous material thermal distillation water purification system driven by working fluid circulation |
| 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 |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB2069117A (en) * | 1980-01-24 | 1981-08-19 | Inst Francais Du Petrole | Heat production utilising a heat pump |
| US4680939A (en) * | 1984-05-28 | 1987-07-21 | Institut Francais Du Petrole | Process for producing heat and/or cold by means of a compression engine 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
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB2069117A (en) * | 1980-01-24 | 1981-08-19 | Inst Francais Du Petrole | Heat production utilising a heat pump |
| US4680939A (en) * | 1984-05-28 | 1987-07-21 | Institut Francais Du Petrole | Process for producing heat and/or cold by means of a compression engine operating with a mixed working fluid |
Cited By (6)
| 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. |
| WO1998026223A1 (en) * | 1996-12-11 | 1998-06-18 | Springer Carrier S/A | Combination room air/split air conditioner |
| US6098415A (en) * | 1996-12-11 | 2000-08-08 | Carrier Corporation | Combination room air/split air conditioner |
| GB2332048A (en) * | 1997-12-02 | 1999-06-09 | Louis J Bailey | Integrated heatihg,cooling,air conditioning & heat recovery system |
| US6347527B1 (en) | 1997-12-02 | 2002-02-19 | Louis J. Bailey | Integrated system for heating, cooling and heat recovery ventilation |
| GB2332048B (en) * | 1997-12-02 | 2002-06-26 | Louis J Bailey | Intergrated system for heating cooling and heat recovery ventilation |
Also Published As
| Publication number | Publication date |
|---|---|
| GB9418432D0 (en) | 1994-11-02 |
| ZA946528B (en) | 1996-02-27 |
| AU7149994A (en) | 1995-12-21 |
| CN1114040A (en) | 1995-12-27 |
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