CN1114040A - Air energy heat circulation exchanger - Google Patents

Abstract

The air energy heat circulation exchanger is a fresh air energy heat circulation exchanger with synchronous temperature change and near-zero heat transfer temperature difference, and the used working medium is a working medium pair consisting of a refrigerant and an absorbent.

Description

The invention relates to an air energy heat circulation exchanger.

Air conditioning is to adjust the energy state and air properties of indoor air to meet the comfort and physiological hygiene requirements of the human body. The sources of indoor air pollution mainly come from the metabolic activities of indoor objects and human body. Closed air circulation is to suck indoor dirty air into the room after being refrigerated. The result of this air circulation is that the degree of pollution will continue to deepen and repeat a vicious cycle, which is extremely harmful to human health. If 100% fresh outdoor air is introduced, the corresponding power consumption needs to increase by more than 1.2 times, so high energy consumption and low energy conversion efficiency are the defects of current air conditioners.

In other words, to meet the oxygen demand in a certain space and the cooling (heating) requirements, the current air conditioners need to consume a lot of electric energy.

The second law of thermodynamics states that heat can spontaneously transfer from a high-temperature object to a low-temperature object, but cannot spontaneously transfer from a low-temperature object to a high-temperature object. Carnot cycle and Lorenz cycle are ideal cycles with the highest thermodynamic efficiency, and are also the guiding theory for various air conditioners. According to the current various air conditioners developed according to the above theory, the refrigeration process all needs to consume a lot of energy to pump heat energy from low-temperature objects to high-temperature objects. Therefore, the refrigeration process must be a process of high energy consumption and excessive energy consumption, and the thermodynamic cycle efficiency of various types of air conditioners is far lower than the Carnot cycle efficiency.

Can the energy of the refrigerated air (outdoor hot air energy) be used to compensate the energy required for the refrigeration cycle, so that the energy-consuming refrigeration process can be transformed into a process of energy storage and power generation, as long as the energy obtained is greater than the energy required for refrigeration The energy can make the refrigeration system operate automatically. This requires a higher evaporating temperature and a lower condensing temperature, and obtains the cold (hot) peak temperature necessary for air conditioning during the heat exchange process.

The invention is a low-pressure difference heat pump air conditioner with air energy as the main refrigeration (heat) cycle power. The low-pressure differential heat pump can be used for both liquid-gas mixed transportation and liquid-gas separation transportation. Air energy refers to the part of energy contained in natural air that can be used for cooling (heating). The differential cooling tube is a high-efficiency heat exchanger with a large heat flow per unit area and can make the temperature difference of the end heat transfer infinitely close to zero. The working medium pair refers to the combination of refrigerant and absorbent, such as water and lithium bromide (LiBr) or ammonia (NH ₃ ) and water, or water and lithium chloride (LiCl), etc. The thermal cross-cycle machine of the present invention is an outdoor fresh air air conditioner composed of an air-energy two-way evaporator, an air-energy two-way condenser, and a low-pressure differential energy conversion heat pump. Its temperature-entropy diagram is a cross-shaped thermodynamic cycle, which can be fully utilized The energy of the air is used to compensate the power cycle required for the cold (heat) process, so it has a very high thermodynamic cycle efficiency. Another feature of the thermal cross cycle machine of the present invention is that 100% of outdoor fresh air is required for the output of cold (heat) in the air conditioning to obtain the best thermal cycle efficiency.

The present invention uses outdoor high-temperature air as the energy source to directly achieve heating and cooling effects. Generally, the condenser and outdoor air temperature △T=13-15°C, the evaporator and evaporation temperature △T=8-12°C, and the present invention's △T= 0.1 ~ 0.5 ℃, can make full use of air to achieve the purpose of heat exchange.

In other words, the present invention introduces 100% outdoor air, flows through the device of the present invention, and exports cold (hot) air, which not only can fully obtain the oxygen demand, but also makes full use of the high (low) temperature of the outdoor air to form a cycle, theoretically The EER value above is extremely high, that is, to produce the greatest cooling (heating) effect with the lowest energy loss.

In the circulation process of the present invention, the working medium (Working substance) circulation is different from the existing method, mainly because: the general absorption mode is composed of four parts, namely evaporator, generator, condenser, absorber, and the evaporation of the present invention The generator contains the function of the generator, and the condenser contains the function of the absorber. The general type generator must use waste heat or steam, and the evaporator must use ice water for secondary heat exchange, but the present invention does not need it.

The object of the present invention is to provide an air energy heat circulation exchanger.

The object of the present invention is achieved by providing an air energy heat circulation exchanger, which is composed of an air energy bidirectional evaporator, an air energy bidirectional condenser, and a low-pressure differential energy conversion heat pump, and can be circulated by a working medium convection distribution On the air energy two-way evaporator and air energy two-way condenser, the air energy of the diversion is used as the heat conversion power to cause the flowing working medium to store energy on the air energy two-way evaporator, and release heat on the air energy two-way condenser. And it is circulated, and the air releases energy in the air-energy two-way evaporator at the same time, and absorbs energy in the air-energy two-way condenser.

The advantage of the present invention is that it achieves the best cooling effect with the lowest energy consumption.

Embodiments of the present invention are described below in conjunction with the accompanying drawings, wherein:

Fig. 1 is the temperature entropy TS figure of heat exchanger thermodynamic cycle of the present invention;

Fig. 2 is ideal Carnot cycle, Lorentz cycle and the TS contrast figure of thermodynamic cycle of the present invention;

Fig. 3 is a schematic diagram of the refrigeration process of the air energy heat circulation exchanger of the present invention;

Fig. 4 is A-A line sectional view among Fig. 3;

Fig. 5 is B-B line sectional view among Fig. 3;

Fig. 6 is the comparative diagram of working medium used in thermodynamic cycle, Carnot cycle and Laurenz cycle of the present invention;

Fig. 7 is a comparison diagram corresponding to the pressure-enthalpy Ph of Fig. 6;

Fig. 8 is the TS figure that thermodynamic cycle of the present invention changes into thermodynamic triangle cycle;

Fig. 9 is a window-type embodiment of the thermal cycler of the present invention.

See Figure 1, which is the temperature entropy TS diagram (TEMPERATUREENTROPY) of the air energy heat cycle exchanger. In the refrigeration cycle:

_T2 is the thermal peak temperature, which is also the dry bulb (DRY BULB) temperature of the outside air.

T ₂ =T _K (thermal peak is the point of highest temperature).

T ₁ is the cold peak temperature and also the output temperature of the cold air.

T ₁ =T ₀ (cold peak is the lowest temperature point).

_T4 is the air wet bulb (WET BULB) temperature of the air-conditioned room.

_T3 is the exhaust wet bulb temperature of the condensing air.

Zone Ⅰ: 1-J-2 process is the process of the cooling working medium absorbing heat (storing air energy) from the continuous temperature change from T _o to T _K ; the corresponding refrigerated air side zone is Zone Ⅱ: 2-J-1 The process is the exothermic process of the continuous temperature change of the refrigerated air from T _K to T _o . Zone Ⅲ: 3-J-4 process is the heat release process of the refrigeration working medium to the continuous temperature change from T ₃ to T ₄ ; the corresponding zone Ⅳ: 4-J-3 process is the process of condensing air from T ₄ to T ₃ Continuous temperature change is a completely wet endothermic process.

2-3 is adiabatic pumping process from high temperature to low temperature (T _K ~ T ₃ ).

4-1 is adiabatic expansion process.

The area of △1J4 is the work W ₁ required by the refrigeration cycle; the area of △23J is the air energy W ₂ obtained by the refrigeration cycle, and W ₂ can be completely converted into useful work. Point J is the intersection of the heat absorption line and the heat release line of the refrigeration working medium pair.

The anticlockwise △1J4 is the refrigerator in the air energy heat circulation exchanger, the clockwise △23J is the air energy engine in the air energy heat circulation exchanger, and the J point is the series connection point of the machine and the air energy engine.

The work to be compensated by the refrigeration cycle is W ₁ -W ₂ =△W

Thermal energy efficiency ratio EER = (Q absorption)/(△W); where Q absorption is the cooling capacity

When W ₂ ≥ _{W 1} , it can run automatically with the help of air energy W ₂ , then EER→∞.

When the cold peak temperature T _o decreases: T ₄ also moves down, J point also moves down, W ₁ and W ₂ increase at the same time, △W=W ₁ -W ₂ does not increase, it can be seen that the air energy heat cycle The switch also obtains air energy W ₂ during the power-consuming cooling process

Figure 2 is a TS comparison chart of the ideal Carnot cycle, Lorenz cycle and air energy heat cycle exchanger.

是卡诺循环。

is the Carnot cycle.

is the Lorenz cycle.

是空气能热量循环交换机。

It is an air energy heat circulation exchanger.

Under the same T _K and T _o conditions, the Carnot cycle consumes the most power and the cooling capacity is the smallest; the air energy heat circulation exchanger has the maximum cooling capacity and the minimum power consumption; the Lorentz cycle is between the Carnot cycle and the air energy heat circulation exchanger , the greater the temperature difference between T _K and T _o , the more obvious the above contrast.

The heat transfer process of the differential heat transfer tube is a sufficient, infinitely differential, non-isothermal process, and the temperature difference at the end of the heat transfer infinitely approaches zero. Therefore, 1-J-2 and 3-J-4 can be considered as reversible continuous temperature change process. The air energy heat circulation exchanger is composed of two reversible continuous temperature changes and two isentropic processes.

Fig. 3 is a schematic diagram of the refrigeration process of the air energy heat circulation exchanger.

The air energy two-way evaporator 1 exchanges heat through the heat conducting sheet 5 . Referring to Fig. 4, the air energy two-way evaporator 1 is divided into zone I and zone II by planar metal heat conducting sheets arranged in parallel. Zone I is the infinitely differential non-isothermal heat-absorbing (energy storage) zone of T _o ~ T _K refrigerating working medium composed of heat conduction sheet 5 and dxn differential heat insulating sheet 20, and the TS diagram corresponds to 1-J-2 and zone I The refrigerated air side is II, the dyn flow channel of the infinitely differential non-isothermal heat release zone of the refrigerated air composed of the heat conduction sheet 5 and the corrugated heat conduction sheet 7 from T _K to T _o , and the TS diagram corresponds to 2-J-1. The corrugated heat conduction sheet 7 is made of thin metal material, and the heat conduction in the dyn direction can be regarded as zero. The heat conduction sheet can be adiabatically cut into many strip-shaped temperature zones in the dyn direction, and the second is to increase the heat exchange area between the heat conduction sheet and the air The dxn differential thermal insulation sheet 20 is made of non-metallic material with large thermal resistance, and the thermal insulation sheet is cut into many strip-shaped temperature zones in the dxn direction. Therefore, the heat conduction sheet is adiabatically cut by dxn and dyn into countless (dxn, dyn) micro-isothermal heat-conducting surfaces, and each micro-isothermal surface and the adjacent micro-isothermal surfaces (dxy+1, dyn) or (dxn, dyn-1 ) are not equal in temperature, and the temperature difference tends to zero. Since the heat transfer surface of the air energy two-way evaporator 1 is an infinitely differential non-isothermal heat transfer surface, it can be considered that the air energy two-way evaporator is a heat transfer surface with continuous temperature changes from T _o ~ T _k (or T _k ~ T _o ), and The temperature change process on both sides is synchronized.

The outdoor air a ₁ at the heat peak temperature T _K is driven by the blower fan 12 to heat the heat conduction sheet 5 with sufficient continuous temperature changes in the dyn flow channel of zone II along the direction a ₂ , and release heat to the cold air at the cold peak temperature T _o a ₃ enters the room through the air outlet adjustment window 14, and its refrigerated process corresponds to 2-J-1 (T _k -T _o ) and the heat release process of continuous temperature change on the TS diagram.

The dilute solution g1 composed of absorbent _I and refrigerant X is evenly distributed through the infusion pipe 16, and each _g1 distribution pipe is sprayed from the throttle valve 17 into each dxn flow channel arranged in parallel in zone I, according to _g1 → _g12 → _g2 direction flow, the return pipe 11 is the turning point of the dxn flow channel. The endothermic process of g ₁ →g ₁₂ →g ₂ in the dxn flow channel corresponds to the continuous temperature change endothermic process of 1-J-2(T _o -T _k ) on the TS diagram. In the isobaric state P ₁ , g ₁ is heated from the cold peak temperature T _o to the hot peak temperature T _K with sufficient continuous temperature changes, and the liquid refrigerant X contained in g ₁ gradually absorbs heat and evaporates into vapor refrigeration at superheated temperature T _k -T _o = △T Agent X ₂ , g ₁ is correspondingly heated to a concentrated solution at superheating temperature ΔTg ₂ .

Since the heat exchange process of the air energy two-way evaporator 1 is carried out on the micro-isothermal surface, and each micro-isothermal surface always makes the cooling working medium on both sides of the heat conduction sheet do its best to the temperature of I, X and the refrigerated air. It may tend to be isothermal, and the heat transfer temperature difference at the end must tend to zero, so the cooling working medium is a reversible process without heat loss for the heat absorption process from T _o to T _K ; and the air used in actual heat exchange can evaporate in both directions Device 1, the heat transfer temperature difference is 0.1 ~ 0.5 ℃ and there is no need to demand that the heat transfer temperature difference → 0.

The heat pump performance of the air energy two-way evaporator 1 is manifested in that g ₂ and X ₂ are strongly overheated, and the part of air energy W ₂ △T is stored in the reversible heat absorption process from T _o to T _k , and the cooling process is simultaneously energy storage process.

The air energy two-way condenser 2 also exchanges heat through the heat conducting fins 5 . Referring to FIG. 5 , the air energy two-way condenser 2 is divided into zone III and zone IV by planar metal heat conducting fins arranged in parallel. Zone III is the cooling working medium pair g ₂ and X ₂ composed of heat conduction fins 5 and dxn differential heat insulating fins 20 are condensed and liquefied from T ₃ to T ₄ at different temperatures. The TS diagram corresponds to 3-J-4 . The condensing air side corresponding to zone Ⅲ is the condensing air infinite differential non-isothermal complete wet heat absorption zone from T ₄ to T ₃ composed of heat conduction sheet 5 and dyn differential heat insulating sheet 21 in area Ⅳ, and the TS diagram corresponds to 4-J-3 . The outer side of the heat conducting sheet is laminated with a film-type evaporation surface 6 made of porous water-absorbing material, and its film surface has good water storage, water absorption and large porous surface area. The water storage property can greatly improve the heat transfer coefficient of the film evaporation surface 6 and the heat conduction sheet 5; the porosity can form a larger evaporation surface area; making the condensation process a complete wet heat absorption process with a lower temperature. Since the constant pressure specific heat Cp1 of the humid air is much larger than the constant pressure specific heat Cp2 of the air, the temperature difference between T ₄ and T ₃ is small. The dxn differential thermal insulation sheet 20 and the dyn differential thermal insulation sheet 21 are both made of non-metallic materials with high thermal resistance. The heat conduction sheet 5 of the two-way condenser 2 becomes a heat conduction surface for continuous temperature change from T ₄ to T ₃ .

The cold air _a3 output from the air energy two-way evaporator 1 absorbs heat and humidity in the room, and becomes the temperature and temperature _a4 required for human comfort, and is forced into the dyn flow channel of area IV by the exhaust fan 19 along the direction of _a5 in the membrane The water vapor is fully absorbed on the evaporating surface 6 of the formula, and is discharged to the atmosphere from the wet bulb temperature _T4 to the saturated state _a6 of the wet bulb temperature _T3 .

The pressure of _g2 and _X2 flowing out from the air energy two-way evaporator ₁ is P1, which is pumped to _P2 by the low-pressure differential heat pump 15, and distributed to each liquid-vapor distribution pipe of the air energy two-way condenser 2 through the liquid-vapor delivery pipe 13 3 is sprayed into the dxn flow channel of zone III from the nozzle hole, and is gradually liquefied into a supercooled dilute solution g ₁ through sufficient and continuous non-isothermal heat release along the g ₂ →g ₁ direction from T ₃ to T ₄ . g ₁ flows into the air energy two-way evaporator 1 through the infusion pipe 16 and the throttle valve 17...so the reciprocating cycle.

The heat exchange process of the air energy two-way condenser 2 is also carried out on the infinite differential differential anisothermal heat transfer surface, and the temperature difference of the end heat transfer → 0, so the condensation process from T ₃ to T ₄ corresponds to the condensation process from T ₃ to The condensed process of T ₄ and the corresponding heat absorption process of condensed air from T ₄ to T ₃ are both reversible continuous temperature change processes.

The superheated concentrated solution g ₂ has the ability to strongly absorb the gaseous refrigerant X ₂ and liquefy it to release heat in the condensed state at a lower temperature T ₃ → T ₄ , its surface partial pressure is much lower than that of P ₂ . Therefore, the super-condensability of the air energy two-way condenser 2 is manifested in two aspects of low-temperature and low-pressure condensation, which is the result of the dual effects of the W ₂ stored in g ₂ and the low-temperature condensation of T ₃ ~ T ₄ . Super-condensation can make the g ₁ dilute solution supercooled, increase the cooling capacity and further reduce T _o , which further promotes the virtuous cycle of the system.

In the actual cycle, the non-isothermal heat transfer temperature difference between the air-energy two-way evaporator 1 and the air-energy two-way condenser 2 is controlled between 0.1 and 0.5°C, and there is no need to demand that the heat transfer temperature difference → 0, so 1-J-2 and There is still a small amount of irreversible work (EXERGY) loss in the 3-J-4 process. On the other hand, the refrigeration working medium reciprocates the fluid, and there must be frictional resistance during distribution; the 41 process is not an isentropic process but an isenthalpic throttling and depressurization process, and irreversible power loss also exists.

The power loss formed by the above irreversible process is expressed as the loss of net work of the system △W ₁ . Therefore, the compensation work required for the thermodynamic cycle of the air energy heat cycle exchanger W _M = △W ₁ + △W, W _M > the compensation work required for the thermodynamic cycle of the ideal air energy heat cycle exchanger △W _o W _M is converted from low pressure differential energy heat pump Provided by M, the pumping action of the low-pressure differential heat pump M simultaneously pressurizes the liquid _g2 and vapor state _X2 from _P1 to _P2 and transports them to the inlet of the air energy two-way condenser 2, so that the absorbent and refrigerant are carried out as shown in Figure 3 Thermal operation completes the process of energy delivery and energy conversion.

Since the heat transfer temperature difference between the air-energy two-way evaporator 1 and the air-energy two-way condenser 2 is small, and P ₂ -P ₁ =△P is small, the isenthalpic throttling power loss and cooling working medium fluid of the 4-1 process The power loss caused by frictional resistance is also small, so the total net power loss △W ₁ of the system is also small. It can be seen that the air energy heat circulation exchanger not only has a very high theoretical EER value, but also has a high thermodynamic perfection degree (THERMODYNAMIC PERFECT DEGREE). Under standard test conditions, its actual EERm= (Q suction)/(Wm) The value can reach 20-35.

Figure 6 is The working medium is an air energy heat cycle exchanger composed of absorbent and refrigerant and Carnot refrigerator with azeotropic or single refrigerant as working medium and The TS comparison diagram of the Laurenz refrigerator whose working medium is a non-azeotropic mixed refrigerant; Figure 7 is the corresponding pressure-enthalpy Ph comparison diagram (PRESSURE ENTHALPA DIAGRAM). The current commercially available Carnot and Lorenz refrigerators (except large air conditioners) all use air-cooled condensers and air-cooled evaporators. Since the condensation temperature of the air-cooled condenser is 13-15°C higher than the outdoor ambient temperature, the evaporation temperature of the air-cooled evaporator is 8-12°C lower than the cold air outlet temperature, and the differential heat exchanger of the air-energy heat circulation exchange The heat temperature difference is 0.1-0.5°C, under the same cold air output temperature and the same ambient temperature T _K ; the condensation temperature of Carnot and Lorenz refrigerators is higher than T _K and the condensation pressure is higher than P ₂ while the evaporation temperature is low In T _o and evaporation pressure is lower than P ₁ . From the comparison of Figure 6 and Figure 7, it can be seen that in the actual refrigeration system: the higher the condensing pressure, the lower the evaporation temperature, the greater the power consumption, and the smaller the cooling capacity.

Suppose: the power consumption of the Carnot refrigerator is W _c , the cooling capacity is Q _c , EER _c

The power consumption of the Lorenz refrigerator is W _L , the cooling capacity is Q _m , EER _L

The power consumption of the air energy heat circulation exchanger is W _m , the cooling capacity is Q _m , and the EER _m

∵W _c >W _L >W _m and Q _m >Q _L >Q _c

∴ EER _m > EER _L > EER _c

The air energy heat circulation exchanger has a large suction superheat temperature, and this part of the heat is carried by the temperature rise of the absorbent, so the air energy heat circulation exchanger should choose an absorbent with large heat capacity and high thermal conductivity; it also has a large Subcooling temperature (the result of super-condensation), so the cooling capacity Q _M is much larger than Q _c and Q _L , because the EER value of the Carnot and Laurents refrigerators is low, 100% outdoor fresh air cannot be used, while On the contrary, the present invention can adopt 100% outdoor fresh air to realize the best thermodynamic cycle efficiency.

See Figure 3, the outdoor air _a1 with moisture content _X1 releases heat to the cold air of _a3 cold peak temperature T _o in the air energy two-way evaporator 1, the moisture content of _a3 drops to _X2 , then every Kg input The condensed water amount of the cold air is X ₁ -X ₂ =△X ₁₀ △X ₁ drips into the water receiving tray 10 and flows into the water storage tray 9 from the water pipe, and is sprayed from the nozzle 18 to the membrane of the air energy two-way condenser 2 by the water pump at regular intervals and quantitatively Evaporation surface 6. The condensation of the air energy two-way condenser 2 is a wet heat absorption process, and the indoor air a ₄ with a moisture content of X ₃ absorbs water vapor from the film evaporation surface 6 of the air energy two-way condenser 2 and evolves into humid air with a moisture content of X ₄ a ₆ is discharged to the outside, the water consumption per Kg of exhausted air is X ₄ -X ₃ =△X ₂ , the air energy and heat circulation exchanger has the same amount of air input and exhaust air per unit time, so when △X ₁ = △X ₂ is the water balance point. Since the moisture content X ₁ of the natural air and the indoor humidity load X ₃ -X ₂ cannot be predetermined (it is dynamic), the water storage in the water storage tray should be replenished by the automatic water supply device when △X ₂ >△X ₁ , when △X ₁ >△X ₂ , it will be automatically derived.

形T-S循环图（以下称热力三角循环机）。Referring to Fig. 3 and Fig. 8, when the air-energy two-way evaporator 1 is used as an indoor unit and the air-energy two-way condenser 2 is used as an outdoor unit, the refrigerated air of the air-energy two-way evaporator 1 is the closed cycle airflow of indoor air; the air The condensed air of the two-way condenser 2 is drawn from the outside and then discharged to the outside (equivalent to the current separated air conditioner). At this time, the TS diagram of the air energy heat circulation exchanger evolves into the one shown in Figure 6

Shaped TS cycle diagram (hereinafter referred to as thermodynamic triangle cycle machine).

_T2 is the dry bulb temperature of the room air.

_T4 is the wet bulb temperature of the room air.

_T3 is the exhaust wet-bulb temperature of the air energy two-way condenser 2.

T _o =T ₁ is the cold peak temperature and also the output cold air temperature of the air energy two-way evaporator.

The T ₂ of the thermodynamic triangular cycle machine changes during actual operation. When T ₂ =T ₃ , point J coincides with points T ₂ and T ₃ , and when W ₂ =0, point J disappears when T ₃ >T ₂ . The thermodynamic triangular cycle machine and the air energy heat circulation exchanger are the same system and are also composed of two approximately reversible continuous temperature change processes, an adiabatic pumping process, and an isenthalpic throttling process.

Assume that the air energy heat cycle exchanger and the thermodynamic triangle cycle machine have the same cold peak temperature To.

Because: T ₂ <T _K , T _K is the outdoor ambient temperature;

T ₄ < T ₈ , T ₈ is the outdoor air wet bulb temperature;

That is, the thermal peak temperature of the thermodynamic triangle cycle machine is lower than that of the air energy heat cycle exchanger, and the condensation temperature is higher than that of the thermodynamic cross cycle machine; since T _K -T ₈ >T ₂ -T ₄ , the air stored in the thermodynamic triangle cycle machine during the refrigeration process Energy is less than a thermal cross cycle machine. Then the work W _M ′ input by the thermodynamic triangular cycle machine M to the system should be greater than the work W _M required by the air energy heat cycle exchanger. However, the thermodynamic triangular cycle machine can also store air energy in the energy-consuming refrigeration process, the heat pump of the air-energy two-way evaporator 1 and the supercondensability of the air-energy two-way condenser 2 still exist, and the irreversible loss in the heat transfer process is small , so it also has a high thermal cycle efficiency, that is, the coefficient of performance EER.

的劳伦茨循环。从图中可以看出劳伦茨循环所需的功能W_L＞2W_M′;且由于吸热线1-2′以下的面积小于以热力三角循环机吸热线Q1-J-2以下的面积;可知热力三角循环机可比劳伦茨制冷机的性能系数EER高二倍以上。若将热力三角循环机的工作介质改换为共沸（AZEOTROPIC）制冷剂或单一制冷剂时其性能系数EER还要进一步降低。因为劳伦茨制冷机和卡诺制冷机在制冷过程中不可能利用空气能量;使空气能双向蒸发器1的热泵性和空气能双向冷凝器2的超冷凝消失。所以空气能热量循环交换机和热力三角循环机只有在使用制冷工作介质对时，才能获得其最大的性能系数。If the refrigeration working medium pair is changed to a non-azeotropic (NONAZEOTROPIC) mixed refrigerant in the thermodynamic triangle cycle machine, then the thermodynamic triangle cycle in Figure 8 is changed to

Lorenz cycle. It can be seen from the figure that the function W _L > 2W _M ' required by the Laurents cycle; and because the area below the endothermic line 1-2' is smaller than the area below the endothermic line Q1-J-2 of the thermodynamic triangle cycle machine; it can be seen The coefficient of performance (EER) of the thermodynamic triangle cycle machine can be more than two times higher than that of the Lorenz refrigerator. If the working medium of the thermodynamic triangle cycle machine is changed to azeotropic (AZEOTROPIC) refrigerant or a single refrigerant, its performance coefficient EER will be further reduced. Because it is impossible for the Lorenz refrigerator and the Carnot refrigerator to utilize air energy in the refrigeration process; the heat pump of the air energy two-way evaporator 1 and the supercondensation of the air energy two-way condenser 2 disappear. Therefore, the air energy heat circulation exchanger and the thermodynamic triangle cycle machine can only obtain their maximum performance coefficients when they use the refrigeration working medium pair.

The air energy heat circulation exchanger can be made into a window type machine. Fig. 9 is a window type air energy heat circulation exchanger. Above the center line is part 1 of air energy two-way evaporator, and below the center line is part 2 of air energy two-way condenser.

The outdoor natural air _a1 is driven by the blower fan 12 to pass through the dyn channel of the air energy two-way evaporator ₁ to release heat to the cold _peak temperature T _o . Adjust the window vanes 28 to guide the rear to absorb moisture and heat on the film evaporation surface 6 of the dyn flow channel of the air energy two-way condenser 2, and discharge it to the atmosphere in the form of a ₆ . The return plate 27 of the air energy two-way evaporator 1 and the air energy two-way condenser 2 is used to separate the dxn flow channel, so that the cooling working medium can flow in a U shape in the differential heat transfer device.

During cooling, the nozzle 18 sprays regularly and quantitatively to the film evaporation surface 6 of the air energy two-way condenser 2, that is, the film evaporation surface 6 is wetted. The water pump 23 regularly and intermittently sends water to the electromagnetic control valve 24; the electromagnetic control valve 24 supplies water to the nozzle 18 when cooling, and supplies water to the heating nozzle 26 when heating. Water filter 22 prevents contaminants from entering the water supply.

When the air energy heat circulation exchanger is used as heating (heat pump): the air energy two-way evaporator 1 is still the same, but the cold peak air is sent to the outside; the air energy two-way condenser 2 is still the same, but the heat formed by it is still the same. Peak air input into the chamber. Therefore, its overall composition must be transformed as follows:

1. Switch the inlet of the refrigeration working medium of the air energy two-way evaporator 1 and the air energy two-way condenser 2 to the outlet at the same time, and switch the outlet to the inlet at the same time to make the refrigeration working medium pair run in reverse.

2. Turn the supply fan in reverse to become an exhaust fan to exhaust air from indoor to outdoor. The indoor air is discharged to the atmosphere through the dyn flow channel of the air energy two-way evaporator 1 to the cold peak temperature; the exhaust fan is reversely operated to become a supply fan , the outdoor fresh air enters the room through the dyn channel of the air energy two-way condenser 2 to absorb heat and moisture until the heat peak temperature is reached.

3. The heating nozzle 26 on the left side of the air energy two-way evaporator 1 and on the right side of the air energy two-way condenser 2 is condensed to the air energy two-way evaporator 1 and the air energy two-way condenser at regular intervals under the action of the electromagnetic control valve 24 and the water pump 23 The device 2 spray is used to moisten the film evaporation surface of the air energy two-way condenser 2 and promptly resolve the frost accumulation in the air energy two-way evaporator 1 dyn flow channel. An appropriate amount of glycerine (GLYCERINE) glycerin solution can be added to the water pan to enhance the heat exchange performance of the air energy two-way evaporator 1 and the air energy two-way condenser 2 and prevent the air energy two-way evaporator 1 dyn channel from forming ice blockage.

Due to the small heat transfer temperature difference of the differential heat transfer device and the low condensation temperature of the air energy heat cycle exchanger and the thermodynamic triangle cycle machine. Even when used as a Lorentz cycle and a Carnot cycle: Compared with the current commercially available air conditioners, the coefficient of performance EER can be greatly improved.

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.

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