WO1999014538A1

WO1999014538A1 - Air conditioning system

Info

Publication number: WO1999014538A1
Application number: PCT/JP1998/004179
Authority: WO
Inventors: Kensaku Maeda
Original assignee: Ebara Corporation
Priority date: 1997-09-17
Filing date: 1998-09-17
Publication date: 1999-03-25

Abstract

An air conditioning system capable of operating a heat source absorbing heat pump smoothly and achieving high energy efficiency, comprising a desiccant air conditioner, a first absorption-refrigeration cycle, a second absorption-refrigeration cycle operating at a lower temperature than the first absorption-refrigeration cycle, and an absorption heat pump provided with a heat exchanger to cool a refrigerant in the refrigerant path from a condenser to an evaporator in the first cycle, forming heat exchange relationships between the evaporator in the first cycle and an absorber in the second cycle and between a condenser in the first cycle and a regenerator in the second cycle. The treated air in the air conditioner is cooled using evaporation heat generated in the second cycle of the absorption heat pump as the heat source for cooling while regenerating desiccant by heating the regenerated air in the air conditioner using the absorption heat in the first cycle and the condensation heat in the second cycle in the absorption heat pump as the heat source. The system is configured so as to direct the regenerated air or a heating medium for heating the regenerated air to the heat exchanger for cooling the refrigerant provided in the refrigerant path in the first cycle of the absorption heat pump to exchange heat with the refrigerant.

Description

Description Air-conditioning system Technical field

The present invention relates to an air conditioning system using a desiccant, and more particularly to an air conditioning system using an absorption heat pump as a heat source for heating regeneration air and cooling processing air. Background art

FIG. 8 shows a conventionally known example of an air conditioning system in which an absorption heat pump is used as a heat source device and an air conditioner using a desiccant is combined with a so-called desiccant air conditioner. This air-conditioning system is composed of a process air path される in which moisture is adsorbed by the desiccant rotor 103, and a desiccant port 110, which is heated by a heating source and passes through the desiccant port 103 after the moisture adsorption. It has a regeneration air path B for desorbing and regenerating moisture, and has a sensible heat between the treated air to which moisture is adsorbed and the regenerated air before regeneration and before being heated by the heating source. An air conditioner having an exchanger 104, a first cycle that forms an absorption refrigeration cycle with the evaporator 3, absorber 1, regenerator 2, and condenser 4 as main components, and an evaporator 13 A second absorption refrigeration cycle that operates at a lower temperature than the first cycle, with the absorber 11, the regenerator 12, and the condenser 14 as main constituent devices. The heat exchange relationship 21 between the evaporator 3 and the second cycle absorber 11 An absorption heat pump that forms a heat exchange relationship 20 between the condenser 4 of the first cycle and the regenerator 12 of the second cycle. Cycle The regenerated air of the air conditioner is heated by the heater 120 to regenerate the desiccant by using the heat of absorption of the heat of the second cycle and the heat of condensation of the second cycle as the heat source. This is an air conditioning system that cools the processing air of the air conditioner with a cooler (cold water heat exchanger) 115 using the heat source as a cooling heat source. In this air conditioning system, a high energy-saving effect can be obtained because the absorption heat pump simultaneously cools the processing air of the desiccant air conditioner and heats the regeneration air.

However, the absorption heat pump, which is the heat source of the system, requires the refrigeration effect of the first cycle to be smaller than the absorption heat of the second cycle. It turned out that it was necessary to prevent overconcentration. The reason will be described below.

Fig. 9 shows a During diagram showing the operating state of the absorption heat pump of the conventional decent air conditioning system. Fig. 9 shows a typical example of a lithium bromide-water system generally used in an absorption refrigerator, and shows the first cycle and the second cycle separately. The alphabetic symbols shown in the figure indicate the state of the absorbing solution or refrigerant, and the same symbols are circled in FIG.

In Fig. 9, the absorption solution in the first cycle is heated from an external heat source in the regenerator 2, generates refrigerant vapor and is concentrated (order c: 175 ° C in the figure), and then heat exchanger After 5 (state d), it reaches absorber 1. In the absorber 1, the absorbing solution absorbs the refrigerant evaporated in the evaporator 3, is diluted (state a), is heated again through the heat exchanger 5 (state b), and returns to the regenerator 2. The refrigerant vapor generated in the regenerator 2 flows into the condenser 4 and condenses (state). In the condenser 4, the heat of condensation generated during the condensation is transmitted to the regenerator 12 of the second cycle by the heat transfer tube 20 which has a heat exchange relationship. The condensed refrigerant is sent to the evaporator 3 and evaporated. Emits (state e). In the evaporator 3, the evaporating heat absorbed during the evaporation is transmitted from the absorber 11 (state A) in the second cycle by the heat transfer tube 21 which has a heat exchange relationship. The absorption solution of the second cycle is heated in the regenerator 12 by the heat of condensation (state) of the first cycle through the heat transfer tube 20, generates refrigerant vapor, is concentrated (state C), and is then heat-exchanged. After 15 (State D), it reaches absorber 11. In the absorber 11, the absorbing solution absorbs the refrigerant (state E) evaporated in the evaporator 13, is diluted (state A), and is heated again through the heat exchanger 15 (state B). Return to In the absorber 11, the absorbed heat generated at the time of absorption is transferred to the evaporator 3 (state e) in the first cycle by the heat transfer tube 21 having a heat exchange relationship. The refrigerant vapor generated in the regenerator 12 flows into the condenser 14 and condenses (state F). The heat transfer medium flows in the order from the condenser heat transfer tubes 31 of the second cycle 31 to the absorber heat transfer tubes 30 of the first cycle, whereby the absorption solution temperature of the first cycle (state a: 75 ° C in the figure) ) Is higher than the refrigerant condensation temperature of the second cycle (State F: 65 ° C in the figure). The condensed refrigerant (state F) is sent to the evaporator 13 and evaporates (state E).

In the absorption heat pump configured as described above, the driving heat is applied to the regenerator 2 of the first cycle, and the used heat can be taken out by the absorber 1 of the first cycle and the condenser 14 of the second cycle, and The used cold energy can be taken out by the evaporator 13 in the second cycle. In this absorption heat pump, the cycles are independent of each other, so the mass balance is balanced and the refrigerant / solution does not move from one cycle to the other. However, the heat balance is not balanced, as explained below.

Now, let the ratio of the refrigerating effect of the evaporator to the heat input of the regenerator in the first cycle be. Is the so-called operating coefficient (COP), which is a variable that can be set in design by the circulation ratio of the solution, etc., but is approximately 0.8. Similarly Let the ratio of the refrigerating effect of the evaporator to the heat input of the regenerator in cycle ₂ be C2. The values obtained by dividing the heat output of the condenser by the heat input of the evaporator are defined as R i and R _{2 in} each cycle. : R t, R _2, since each of the refrigerant flow rate are equal, becomes a value obtained by dividing E down evening ruby variation of refrigerant definitive in evaporator E down evening Lupi change of the refrigerant in the condenser of the each cycle.

Here, assuming that the heat input to the first cycle is 1, the cooling effect Q e t of this cycle is

Q e! = C 1 (1)

It is.

On the other hand, in the second cycle, because the condensation heat of the first cycle is added to the regenerator, the regenerator heat input Q g ₂ is

Q g ₂ = C 1R 1 (2)

The cooling effect Q Θ ₂ of the second cycle is

Q e 2 = C 2-Q 2 = C ₂ -C i-R i (3)

The heat of condensation Q c ₂ of the second cycle is

Q c ₂ = R ₂ -Q e 2 = C i-C 2 'R i-R 2 (4)

The heat of absorption Q a ₂ in the second cycle is the total heat input in the second cycle minus the heat of condensation,

Q a 2 = C i - R i + C 2 - C i -. In _{_{R i- C 1 C 2 · R}} · R 2 (5) the absorption heat pump, absorption of the evaporator of the first cycle the second cycle Since the vessel exchanges heat, the heat of evaporation of the first cycle, Q e! And the magnitude of the absorbed heat Q a ₂ in the second cycle. So taking the difference _{_{between, Q a 2 - Q e 1}} = C iR il- C 2-C iR i- C i- C 2-R i- 2- C I

= C 1 [(R, - 1) - C 2 · R i (R 2 - 1)] (6) from the operating state of the cycle in FIG. 5, when calculating a RR _2, 0

R, = (6 75-95) / (609-95) = 1.128

R ₂ = (6 39-65) / (603-65) = 1.06 7

Ci and C ₂ are approximately 0.8 (standard value of single-effect absorption cycle), and the value of equation (6) is obtained.

Q a ₂ -Q ei = 0.8 (0.1 28-0.8 x 1.1 28 x 0.067)

= 0.054> 0

It can be seen that the heat absorbed in the second cycle is larger. If, evaporation heat Q e of the first cycle, but the order Do greater than absorption heat Q a ₂ second cycle, there is a need for a (6) 0, therefore,

_{C 2 ≥ (R 1 - 1} ) / (2 - 1) / R, (7)

Becomes Calculating this C 2 gives

C ₂ ≥ 0.128 / 0.067 / 1.128 = 1.694

This is an unattainable value for C 0 P of a single-effect absorption refrigeration cycle. That is, in this cycle, the heat of absorption Q a ₂ of the second cycle is always higher than the heat of evaporation of the first cycle Q e! It turns out that it is bigger than that.

Therefore, in the conventional heat source absorption heat pump shown in Fig. 8, since the refrigeration effect in the first cycle is small, the heat absorbed in the second cycle cannot be completely cooled. As the solution cannot be absorbed completely, the solution gradually concentrates, so that there is a problem that continuous luck cannot be achieved. In view of the above problems, an object of the present invention is to provide an air conditioning system capable of smoothly operating a heat source absorption heat pump and obtaining high energy efficiency. Disclosure of the invention

According to the first aspect of the present invention, there is provided a processing space in which water is adsorbed by a desiccant. An air conditioner having a path for air, a path for regenerated air for desorbing and regenerating moisture in the desiccant by passing through the desiccant after being adsorbed after being heated by the heating source, and at least an evaporator and absorption The first cycle, which constitutes an absorption refrigeration cycle, using a heater, a regenerator, and a condenser as constituent devices, and the first cycle, which includes at least an evaporator, an absorber, a regenerator, and a condenser as constituent devices A second absorption refrigeration cycle operating at a lower temperature, forming a heat exchange relationship between the evaporator of the first cycle and the heat absorber of the second cycle, and A heat exchange relationship is formed between the condenser and the regenerator in the second cycle, and a heat exchanger for cooling the refrigerant during cooling of the refrigerant from the condenser in the first cycle to the evaporator is provided. An absorption heat pump; In the air conditioning system that cools the air conditioner using the heat of absorption of the first cycle of the heat pump and the heat of condensation of the second cycle as the heating source, the heat pump is provided in the refrigerant path of the first cycle of the heat pump. An air conditioning system characterized in that the system is configured so that regeneration air or a heating medium for heating the regeneration air is guided to a heat exchanger that cools the refrigerant, and exchanges heat with the refrigerant.

As described above, the heat exchanger for cooling the refrigerant provided in the first cycle of the absorption heat pump is configured to guide the heating medium in a low temperature state to the heat exchanger to exchange heat with the refrigerant. The cooling effect of the refrigerant increases, the rate of loss of the refrigeration effect due to self-evaporation when the refrigerant flows into the evaporator decreases, the refrigeration effect of the first cycle increases, and the concentration of the solution of the second cycle increases. High cooling efficiency and high energy efficiency, as well as recovering the retained heat of the refrigerant, which can be used to heat desiccant regenerated air, increasing the cooling effect of the system and achieving high energy efficiency be able to. The second aspect of the present invention provides a heat exchanger for cooling the refrigerant which is provided in the refrigerant path of the first cycle of the absorption heat pump for cooling the refrigerant by introducing regeneration air or a heating medium for heating the regeneration air. 2. The air conditioning system according to claim 1, wherein the air conditioning system is configured to be guided to a condenser in the second cycle and an absorber in the first cycle for heating after the replacement.

As described above, after the heating medium having the lowest temperature is guided to the heat exchanger that cools the refrigerant provided in the first cycle of the absorption heat pump, the heat is exchanged with the cooling medium, and then the absorber is cooled. In addition, the configuration in which the refrigerant is guided to the condenser for heating enhances the effect of cooling the refrigerant, and reduces the rate at which the refrigerant self-evaporates when flowing into the evaporator to impair the refrigeration effect. Since the refrigerating effect of the second cycle is improved, the concentration of the solution in the second cycle can be prevented and high energy efficiency can be obtained, and the heat retained in the refrigerant can be recovered and used for heating the regenerated desiccant air. However, the cooling effect of the system is increased, and high energy efficiency can be obtained.

The third aspect of the present invention provides a first cycle that forms an absorption refrigeration cycle with at least an evaporator, an absorber, a regenerator, and a condenser as constituent devices, and at least an evaporator, an absorber, a regenerator, and a condenser. A second absorption refrigeration cycle that operates at a lower temperature than the first cycle, and has a heat exchange relationship between the evaporator of the first cycle and the absorber of the second cycle. And a heat exchange relationship between the condenser of the first cycle and the regenerator of the second cycle is formed by a part of the heat of condensation of the first cycle. An absorption heat pump characterized in that a heat exchange relationship is formed so as to heat a heat medium from which heat is taken out by the absorber of the cycle and the condenser of the second cycle.

Thus, by extracting a part of the heat of condensation of the first cycle, Without reducing the refrigeration effect of the first cycle, the amount of heat applied to the regenerator in the second cycle is reduced to suppress the concentration of the solution, and the heat of evaporation in the first cycle and the heat of absorption in the second cycle Therefore, the concentration of the solution in the second cycle can be prevented. As a result, the smooth operation of the absorption heat pump is enabled, and the smooth operation of the entire system is enabled, so that an air conditioning system with high energy efficiency can be provided.

The invention according to claim 4 is directed to heating the heat medium after extracting the heat with the condenser of the second cycle and the absorber of the first cycle by a part of the heat of condensation of the first cycle. An absorption heat pump according to claim 3, characterized in that: In this way, by heating the heat medium with the heat of condensation of the first cycle having a high operating temperature, in addition to the effect of preventing the solution from being concentrated in the second cycle, a heat medium having a high temperature can be taken out. Therefore, particularly when used as a heat source for desiccant regeneration of a desiccant air conditioner, the regeneration capability is enhanced, and the dehumidification capability can be enhanced.

The invention according to claim 5 comprises detecting the concentration of the absorbing solution in the second cycle, and detecting the concentration of the absorbing solution in the second cycle by using the heat of condensation in the first cycle when the concentration exceeds the set value. 5. The absorption heat pump according to claim 3, wherein an amount of heat for heating a heat medium for extracting heat from the condenser in the second cycle is increased.

According to the invention of claim 6, the refrigerant level of the evaporator in the second cycle is detected, and when the liquid level rises above a set value, the absorber in the first cycle and the second refrigerant are detected. The absorption heat pump according to claim 5, wherein the amount of heat for heating a heat medium that takes out heat in the condenser of the cycle is increased, and thus, the absorption solution concentration in the second cycle is detected. The concentration is set By increasing the amount of heat that heats the heat medium that extracts heat with the absorber in the first cycle and the condenser in the second cycle by the heat of condensation in the first cycle when the heat exceeds the fixed value, By balancing the heat of evaporation of the second cycle with the heat of absorption of the second cycle, the concentration of the solution in the second cycle can be maintained at an appropriate level, and smooth operation can be continued.

The invention according to claim 7 provides a process air path in which moisture is adsorbed by the desiccant, and a moisture in the desiccant which passes through the desiccant after the moisture adsorption after being heated by the heating source. An air conditioner having a regeneration air path for desorption and regeneration, and having a sensible heat exchanger between the treated air to which moisture is adsorbed and the regeneration air before desiccant regeneration and before being heated by the heating source; A first cycle that forms an absorption refrigeration cycle with at least an evaporator, an absorber, a regenerator, and a condenser as components, and at least an evaporator, an absorber, a regenerator, and a condenser as components. A second absorption refrigeration cycle operating at a lower temperature than the first cycle, forming a heat exchange relationship between the evaporator of the first cycle and the absorber of the second cycle, and One cycle condenser and second An absorption heat pump that forms a heat exchange relationship with a regenerator of the cycle, and the air conditioning uses the absorption heat of the first cycle and the condensation heat of the second cycle of the absorption heat pump as a heat source. An air conditioning system that heats the regeneration air of the air conditioner to regenerate the desiccant and cools the processing air of the air conditioner using the heat of evaporation of the second cycle of the absorption heat pump as a cooling heat source. An air conditioning system characterized by forming a heat exchange relationship so as to heat regeneration air or a heat medium serving as a heating source for the regeneration air by a part of the condensation heat of the first cycle.

Thus, some of the heat of condensation from the first cycle of the absorption heat pump is removed. Without reducing the refrigeration effect of the first cycle-reducing the amount of heat applied to the regenerator in the second cycle to reduce the concentration of the solution, reducing the heat of evaporation in the first cycle and the second In order to balance the heat absorbed in the cycle, it is possible to prevent the concentration of the solution in the second cycle and to achieve smooth operation of the system. By using it as a heat source for the regeneration of the air conditioner's decent power, the regenerative capacity can be increased, and the dehumidifying capacity and power can be increased.

The invention according to claim 8 is configured such that the regeneration air or a heating medium for heating the regeneration air is guided to a heat exchanger that extracts a part of the condensation heat of the first cycle of the absorption heat pump to exchange heat with the refrigerant. Claims characterized by the following:

7. The air conditioning system according to 7.

As described above, by introducing the regeneration air or the heating medium that heats the regeneration air to the heat exchanger that extracts a part of the condensation heat of the absorption heat pump in the first cycle, heat exchange with the refrigerant increases the temperature. Since the desiccant of the desiccant air conditioner can be regenerated with this heat source, the dehumidifying capacity can be increased. BRIEF DESCRIPTION OF THE FIGURES

FIG. 1 is an explanatory view showing a basic configuration of an embodiment of an air conditioning system using a decant according to the present invention, and FIG. 2 is a drawing showing the absorption solution cycle of the absorption heat pump shown in FIG. FIG. 3 is an explanatory diagram showing a desiccant air-conditioning cycle of the air of the air conditioning system of FIG. 1 in a wet air diagram, and FIG. 4 is a second embodiment of the present invention. Fig. 5 is an explanatory diagram showing the basic configuration of the desiccant air conditioning system. Fig. 5 is a During diagram showing the cycle of the heat source absorption heat pump shown in Fig. 4. Fig. 6 is wet air showing the cycle of the desiccant air conditioning system shown in Fig. 4. FIG. 7 is a diagram of a third embodiment of the present invention. FIG. 8 is a view showing an embodiment of the conventional air conditioning system, and FIG. 9 is a diagram showing a During line showing an operation state of an absorption heat pump part of the conventional decent power air conditioning system. FIG. BEST MODE FOR CARRYING OUT THE INVENTION

Hereinafter, an embodiment of an air conditioning system according to the present invention will be described with reference to the drawings. <FIG. 1 is a diagram showing a basic configuration of a desiccant air conditioning system according to the present invention. , Evaporator 3, Absorber 1, Regenerator 2, Condenser 4, Heat exchanger 5 as the main components of the first cycle that forms an absorption refrigeration cycle, and Evaporator 13 and Absorber 11, Regeneration A second absorption refrigeration cycle that operates at a lower temperature than the first cycle, with the main components of the unit 12, the condenser 14, and the heat exchanger 15, and the evaporator of the first cycle 3 and a heat exchange relationship 21 between the absorber 11 of the second cycle and a heat exchange relationship between the condenser 4 of the first cycle and the regenerator 12 of the second cycle. The relationship 20 is formed, and the refrigerant path 8 from the condenser 4 of the first cycle to the evaporator 3 is formed. It is provided with a heat exchanger 4 0 to cool the refrigerant. Further, in this embodiment, a sensor 62 for detecting the refrigerant level of the evaporator in the second cycle, a valve 60, a path 64 for sending refrigerant to the absorber, and a controller 63 are provided. When the solution is over-concentrated by the signal, the valve 60 is opened to send a refrigerant to the absorber 11 to dilute the solution.

On the other hand, the air conditioner is configured as shown below, as in the conventional embodiment of FIG. The processing air path A is connected to the air conditioning space 101 and the suction port of the processing air blower 102 via the path 107, and the outlet of the blower 102 is connected to the desiccant trolley 103. Connect through 108 and desiccan The outlet of the processing air of the trolley 103 is connected to the sensible heat exchanger 104, which has a heat exchange relationship with the regeneration air, via the path 109, and the processing air of the sensible heat exchanger 104 The outlet is connected to the cooler 1 15 via the route 110, and the outlet of the processing air of the cooler 115 is connected to the humidifier 105 via the route 111, and the humidifier 105 The outlet of the processing air is connected to the air-conditioned space 101 via a path 112 to form a processing air cycle.

On the other hand, the regeneration air path 、 connects the outside air to the suction port of the regeneration air blower 130 through the path 124, and the discharge port of the blower 130 has a sensible heat heat exchange relationship with the processing air. The sensible heat exchanger 104 is connected to the low-temperature side inlet of another sensible heat exchanger 124 through the path 125, The low-temperature side outlet of the sensible heat exchanger 1 2 1 is connected to the heater 1 2 0 via the path 1 2 6, and the outlet of the regeneration air of the heater 1 2 It is connected to the air inlet via the route 127, and the outlet of the regenerated air at the desiccant outlet 103 is connected to the hot side inlet of the sensible heat exchanger 121 via the route 128, The outlet on the high-temperature side of the sensible heat exchanger 122 is connected to the external space via a path 129 to form a cycle in which regenerated air is taken in from the outside and exhausted outside.

After passing the heat transfer medium (hot water) between the absorption heat pump section and the air conditioner section through the heat transfer medium (hot water), the hot water exits the heater 120 in the regeneration air path between the air conditioner and the path. 1 2 3, pump 150, route 50, refrigerant cooling heat exchanger 40, route 51, condenser 14, route 52, 'absorber 1 It is configured to return.

In addition, the path of the heat transfer medium (cold water) that transfers cold heat between the absorption heat pump section and the air conditioner section passes through the cooler 1 15 in the processing air path of the air conditioner after the cold water passes through the path 1. 1 8, pump 16 0, evaporator 1 3, route 1 1 It is configured to return to the cooler 1 15 via the order of 7. In the figure, the circled alphabets K to V are symbols indicating the state of air corresponding to that in Fig. 3, where SA is air supply, RA is return air, OA is outside air, and EX is exhaust air. Express.

Next, the operation of the absorption heat pump portion of the desiccant air conditioning system configured as described above will be described with reference to FIG.

The absorption solution of the first cycle is heated from an external heat source (not shown) in the regenerator 2 via the heat transfer tube 34, generates refrigerant vapor, is concentrated, and is then concentrated through the heat exchanger 5 to the absorber. Leads to one. In the absorber 1, the absorbing solution absorbs the refrigerant evaporated in the evaporator 3, and after being diluted, returns to the regenerator 2 via the heat exchanger 5 again by the action of the pump 6. In the absorber 1, heat is exchanged with a heat medium such as hot water by the heat transfer tube 30 in order to use the heat of absorption generated at the time of absorption. The refrigerant vapor generated in the regenerator 2 flows into the condenser 4 and is condensed. In the condenser 4, the heat of condensation generated during the condensation is transferred to the regenerator 12 in the second cycle by the heat transfer tube 20 which has a heat exchange relationship. The condensed refrigerant is cooled by the heat medium in the heat exchanger 40 and then sent to the evaporator 3 to evaporate. In the evaporator 3, the evaporative heat absorbed during the evaporation is transmitted from the absorber 11 in the second cycle by the heat transfer tube 21 having a heat exchange relationship.

The absorption solution of the second cycle is heated in the regenerator 12 by the heat of condensation of the first cycle through the heat transfer tube 20, generates refrigerant vapor, is concentrated, and is absorbed through the heat exchanger 15 Container 1 leads to 1. In the absorber 11, the absorbing solution absorbs the refrigerant evaporated in the evaporator 13, and after being diluted, returns to the regenerator 12 via the heat exchanger 15 by the action of the pump 16. In the absorber 11, the heat of absorption generated at the time of absorption is transferred to the evaporator 3 of the first cycle by the heat transfer tube 21 having a heat exchange relationship. The refrigerant vapor generated in the regenerator 12 is sent to the condenser 14 Inflows and condenses. In the condenser 14, heat is exchanged between the heat medium and the heat transfer tube 31 in order to use the heat of condensation generated during the condensation. In addition, the heat medium flows in the following order: a refrigerant cooling heat exchanger 40 in the first cycle, a condenser heat transfer tube 31 in the second cycle, and an absorber heat transfer tube 30 in the first cycle. The absorption solution temperature in the first cycle, the refrigerant condensation temperature in the second cycle, and the refrigerant temperature at the evaporator inlet in the first cycle increase in this order, and the refrigerant temperature at the evaporator inlet in the first cycle becomes the lowest. The refrigerant condensed in the second cycle is sent to the evaporator 13 and evaporates. In the evaporator 13, heat is exchanged with the heat medium such as chilled water and the heat transfer tube 33 to use the heat of evaporation absorbed during the evaporation.Next, the operation of the absorption heat pump configured as described above is performed. This will be described with reference to FIG. FIG. 2 is a Duling diagram showing a cycle of the heat source absorption heat pump of FIG. This figure shows a typical example of a lithium bromide-water system commonly used in absorption refrigerators. Alphabet symbols in the figure indicate the state of the absorbing solution and refrigerant, and the same symbols are circled in Fig. 1.

The absorption solution in the first cycle is heated from an external heat source in the regenerator 2, generates refrigerant vapor and is concentrated (state c: 175 ° C in the figure), and then passes through the heat exchanger 5 (state d) lead to absorber 1. In the absorber 1, the absorbing solution absorbs the refrigerant evaporated in the evaporator 3, is diluted (state a), is heated again through the heat exchanger 5 (state b), and returns to the regenerator 2. The refrigerant vapor generated in the regenerator 2 flows into the condenser 4 and condenses (in a state). In the condenser 4, the heat of condensation generated during the condensation is transferred to the regenerator 12 in the second cycle by the heat transfer tube 20 which has a heat exchange relationship. The condensed refrigerant is cooled by the refrigerant cooling heat exchanger 40 (state g), and then sent to the evaporator 3 to evaporate (state e). In the evaporator 3, the heat of evaporation that is absorbed during the evaporation is converted into Transmitted from the absorber 1 1 (state A) of the cycle.

The absorbing solution of the second cycle is heated by the regenerator 12 with the heat of condensation (state) of the first cycle through the heat transfer tube 20, generates refrigerant vapor, is concentrated (state C), and then heats It passes through the exchanger 15 (state D) to the absorber 11. In the absorber 11, the absorption solution absorbs the refrigerant (state E) evaporated in the evaporator 13, is diluted (state A), and is heated again through the heat exchanger 15 (state B). Return to In the absorber 11, the heat of absorption generated at the time of absorption is transferred to the evaporator 3 (state e) in the first cycle by the heat transfer tube 21 which has a heat exchange relationship. The refrigerant vapor generated in the regenerator 12 flows into the condenser 14 and is condensed (state F). The condensed refrigerant (state F) is sent to the evaporator 13 and evaporates (state E).

By flowing the heat medium in the order of the heat exchanger 40 for cooling the refrigerant in the first cycle, the condenser heat transfer tube 31 in the second cycle, and the absorber heat transfer tube 30 in the first cycle, Cycle absorption solution temperature (state a: 75 ° C in the figure), refrigerant condensation temperature in the second cycle (state F: 65 ° C in the figure), evaporator inlet in the first cycle (state g: The refrigerant temperature increases in the order of 55 ° C in the figure, and the refrigerant temperature at the evaporator inlet in the first cycle becomes the lowest. As described above, since the refrigeration effect of the first cycle is increased by minimizing the refrigerant temperature at the evaporator inlet of the first cycle of the absorption heat pump, the absorption heat of the second cycle is cooled. The capacity is increased, which can reduce the tendency of the second cycle solution to concentrate. The reasons are explained below.

In order to find the difference between the heat absorbed in the second cycle and the heat generated in the first cycle, as shown in the above equation (6), R i and R ₂ were calculated for the operation state of the cycle in FIG. For i, the heat exchanger at the entrance of the evaporator is the heat exchanger 4 0 As a result, the refrigeration effect increases, and thus decreases. That is,

R! = (6 7 5-9 5) / (609-55) = 1.047

R ₂ = (6 39-65) / (603-65) = 1.067

And C ₂ are approximately 0.8 (standard value of single-effect absorption cycle) as in the above-mentioned conventional example.

When the value of the above equation (6) is obtained,

Q a 2-Q et = C 1 [(:-1)-C ₂ -R i (R 2-1)]

= 0.8 (0.047— 0.8 x 1.047 x 0.067) =-0.007 <0

It can be seen that the heat of absorption in the second cycle is slightly smaller. Moreover, this difference is only a small difference of 0.9% with respect to the heat of evaporation (refrigeration effect) of the first cycle, and the difference between the heat absorbed in the second cycle and the heat of the first cycle. Are almost equal.

In this case, the heat of evaporation of the first cycle Q e! Is determined to be larger than the absorption heat Q a ₂ in the second cycle, that is, the condition that satisfies Equation (6) 0 is obtained as

C ₂ ≥ (R 1-1) / (R 2-1) / R

= 1 0. 047 / 0. 067 / 1. 047 = 0.67

This is a sufficiently achievable value for C 0 P in a single-effect absorption refrigeration cycle. That is, in this cycle is seen to be able to substantially equal the heat of vaporization Q ei with absorption heat Q a ₂ of the second cycle the first sub Ikuru.

Therefore, in the heat source absorption heat pump of the embodiment of FIG. 1, the absorption heat of the second cycle can be cooled by the refrigeration effect of the first cycle, so that the refrigerant can be absorbed by the absorber in the second cycle, Solution concentration , Continuous operation becomes possible. Further, with the increase in the amount of refrigerant absorbed in the second cycle, the refrigerating effect of the evaporator 13 also increases.

Next, the operation when the absorption heat pump configured as described above is combined with the desiccant air conditioning will be described. In FIG. 1, the air in the air conditioning space 101 is shown in FIG.

The (processed air) is sucked into the blower 102 via the passage 107, is pressurized, is sent through the passage 108 to the desiccant towel 103, and is sent to the desiccant towel by the desiccant towel. Absorb moisture and decrease absolute humidity. At the time of adsorption, the temperature of air rises due to heat of adsorption. The air whose humidity has dropped and the temperature has risen is sent to a sensible heat exchanger 104 via a path 109, where it is cooled by exchanging heat with outside air (regenerated air). The cooled air is sent to the cooler 115 via the path 110 and further cooled. The cooled treated air is sent to the humidifier 105 and cooled by water injection or vaporization humidification in the isenthalby process, and is returned to the air-conditioned space 101 via the route 112.

Since the desiccant rotor adsorbs moisture in this process, regeneration is necessary. In this embodiment, the desiccant rotor is operated as follows using outside air as regeneration air. Outside air (OA) is sucked into the blower 130 through the path 124 and is pressurized and sent to the sensible heat exchanger 104, where it cools the treated air and rises in temperature to the path 125 After that, it flows into the next sensible heat exchanger 1 2 1 and exchanges heat with the hot air after regeneration to increase the temperature. Further, the regenerated air exiting the sensible heat exchanger '12 1 flows into the heater 120 via the path 126, is heated by the hot water, and rises in temperature to 60 to 80 ° C, and the relative humidity is reduced. descend. This process is a sensible heat change of the regenerated air.The specific heat of air is significantly lower than that of hot water, and the temperature change is large.Therefore, even if the flow rate of hot water is reduced and the temperature change is increased, heat exchange is performed efficiently. The transfer power can be reduced. The regenerated air, whose relative humidity has decreased after exiting the heater 120, passes through the desiccant towels 103, and then passes through the desiccant heater. It removes evening water and has a regenerating effect. The regenerated air that has passed through the desiccant trolley 103 flows into the sensible heat exchanger 122 through the path 128, preheats the regenerated air before regeneration, and then passes through the path 129 as exhaust. Discarded outside o

The process up to now will be described with reference to the psychrometric chart of FIG. 3. The air in the air-conditioned space 101 (processed air: state) is sucked into the blower 102 via the route 107 and is pressurized to increase the pressure in the route 1. After passing through 08, the desiccant rotor 103 is sent to the desiccant rotor 103, where the moisture in the air is adsorbed by the desiccant rotor, the absolute humidity decreases, and the temperature of the air rises due to the heat of adsorption (state L). The air whose humidity has dropped and the temperature has risen is sent to the sensible heat exchanger 104 via the path 109 and cooled by exchanging heat with the outside air (regenerated air) (state M). The cooled air is sent to the cooler 115 via the route 110 and further cooled (state N), and the cooled air is sent to the humidifier 105 via the route 111 to spray water or water. The temperature decreases during the iso-rubber process by vaporization humidification (state P), and is returned to the air-conditioned space 101 via route 112. In this way, an en-ubiquity difference ΔQ is generated between the return air in the room (state K) and the supply air (state P), thereby cooling the air-conditioned space 101. As described above, in the embodiment of FIG. 1, since the entropy ruby of the refrigerant at the inlet of the evaporator of the heat pump decreases and the refrigerating effect of the heat pump increases, the entropy ruby difference Δ q becomes large, and therefore, the enzymatic ruby difference △ Q showing the cooling effect also becomes large. On the other hand, desiccant regeneration is performed as follows. The outside air for regeneration (OA: state Q) is sucked into the blower 130 via the path 124, pressurized and sent to the sensible heat exchanger 104, where it cools the treated air and raises its temperature. (State: R) Flows into the next sensible heat exchanger 122 via route 125, and exchanges heat with the high-temperature air after regeneration to raise the temperature (state S). Further sensible heat exchanger 1 The regenerated air exiting 21 flows into the heater 120 via the path 126, is heated by the hot water, is heated to 60 to 80 ° C, and the relative humidity is reduced (state T). The regenerated air having a decreased relative humidity passes through the desiccant trowel 103 to remove the water from the desiccant trowel (state U). The regenerated air that passed through the desiccant outlet 103 passed through the passage 128 to the sensible heat exchanger 121, and preheated from the sensible heat exchanger 104 before regeneration before regeneration. After the temperature drops (State V), it is discarded as exhaust gas through Route 12 29.

In this way, the desiccant is air-conditioned by repeating the regeneration of the desiccant and the dehumidification and cooling of the treated air. Although desiccant air-conditioning has been widely used in the past for the method of using exhaust accompanying indoor ventilation as regeneration air, in the present invention, it is also possible to use exhaust from the room as regeneration air. Therefore, the same effect as in the present embodiment can be obtained. It is also possible to use a method in which the air cooled by the sensible heat exchanger 104 for cooling the treated air is not used for regeneration but is once exhausted, and the fresh outside air is led to the sensible heat exchanger 122 as regenerated air. I can't tell.

In this way, by providing the heat exchanger 40 for cooling the refrigerant in the refrigerant path from the condenser 4 to the evaporator 3 in the first cycle and performing cooling, the refrigerant flows into the evaporator 3 The rate at which the cooling effect is impaired due to self-evaporation is reduced, and a large refrigeration effect is obtained. However, the sensible heat of the condensed refrigerant in the first cycle, which has been lost by self-evaporation, can also be recovered and used as a heating source for heating the regenerated air. Therefore, as the cooling capacity increases, the energy efficiency of the entire air conditioning system also improves. In the present embodiment, during the second cycle of the heat source absorption heat pump, a sensor 62 for detecting the refrigerant level of the evaporator, a valve 60, a path 64 for sending the refrigerant to the absorber, and a controller A means for diluting the solution by opening the valve 60 and sending the refrigerant to the absorber 11 when the solution is excessively concentrated by the signal of the sensor 62 is provided. If the load on the heat transfer medium (hot water) rises due to no load, such as when the air conditioning system is partially loaded, the cooling effect of the heat exchanger 40 will not be obtained, and the first Since it is assumed that the refrigeration effect of the cycle is reduced and the heat absorbed in the second cycle cannot be cooled as described above, it is provided as a safety device in such a case. The solution concentration can be prevented from increasing.

This type of means is a well-known technique in a conventional absorption refrigerator, and as a similar means, the refrigerant temperature, pressure and solution temperature may be measured and calculated by a microcomputer or the like for dilution. Also, as shown in the above calculation example, when the heat exchanger 40 cools the refrigerant in the first cycle extremely effectively, on the contrary, the refrigeration effect in the first cycle is lower than that in the second cycle. The solution may be diluted in the first cycle as well, as it may exceed the heat absorption and thus reduce the evaporation pressure in the first cycle and the solution concentration in the second cycle may be too low. It is permissible to provide a means to reduce the refrigeration effect.

FIG. 4 is a diagram showing a basic configuration of a desiccant air-conditioning system according to a second embodiment of the present invention. The following configuration is added to the conventional absorption heat pump shown in FIG. That is, a heat exchanger 61 for extracting a part of the refrigerant vapor from the regenerator 2 of the first cycle to the outside and heating the heat medium with the heat of condensation is provided.The heat exchanger 61 and the regenerator 2 are further connected to each other. Route 6 during the 7 1, a control valve 65, a refrigerant passage condensed in the heat exchanger 61, a path 68 for guiding the refrigerant to the evaporator 3, and a throttle 69 are provided.In the path connecting the regenerator 2 and the condenser 4, The second control valve 66 is provided, and the refrigerant level detection sensor 62 of the evaporator 13 in the second cycle, the controller 63, the controller 63, the first control valve 65, the second A signal path 72 that connects the control valve 66 and a signal path 70 that connects the controller 63 and the refrigerant level sensor 62 are provided, and the refrigerant level sensor 62 is set. The controller 63 detects that the liquid level has risen above the value, and the controller 63 opens the first control valve 65 and throttles the second control valve 66. On the other hand, the air conditioner is configured in the same manner as the conventional embodiment of FIG.

Then, the path of the heat transfer medium (hot water) for transferring heat between the absorption heat pump section and the air conditioner section is changed after the hot water exits the heater 120 in the regeneration air path of the air conditioner. , Route 1 2 3, Pump 1 50, Route 50, Condenser 14, Route 52, Absorber 1, Route 53, Heat Exchanger 61, Route 55, Route 1 2 2 To return to the heater 120. The path of the heat transfer medium (cold water) that transfers cold heat between the absorption heat pump section and the air conditioner section passes through the cooler 1 15 in the processing air path of the air conditioner after the cold water exits the path 1 18 , The pump 160, the evaporator 13 and the path 1 17 to return to the cooler 1 15 in this order.'In the figure, the circled K-V 6 is a symbol indicating the state of air corresponding to, SA is air supply, A is return air, OA is outside air, EX is exhaust. Next, the operation of the absorption heat pump portion of the desiccant air conditioning system configured as described above will be described with reference to FIG. As an operation state, when the controller 63 completely closes the first control valve 65 and opens the second control valve 66, the operation is the same as that of the conventional embodiment of FIG. Omit description Here, the operation when the controller 63 opens the first control valve 65 and throttles the second control valve 66 will be described.

The absorption solution of the first cycle is heated from an external heat source (not shown) in the regenerator 2 via the heat transfer tube 34, generates refrigerant vapor, is concentrated, and is then concentrated through the heat exchanger 5 to the absorber. Leads to one. In the absorber 1, the absorbing solution absorbs the refrigerant evaporated in the evaporator 3, and after being diluted, returns to the regenerator 2 via the heat exchanger 5 again by the action of the pump 6. In the absorber 1, heat is exchanged between the absorbing solution and a heat medium such as hot water via the heat transfer tube 30 in order to use the heat of absorption generated at the time of absorption. The refrigerant vapor generated in the regenerator 2 flows into the heat exchanger 61 via the first control valve 65, which is partially open, and condenses. In the heat exchanger 61, heat is exchanged with a heat medium such as hot water by the heat transfer tube 35 in order to utilize the heat of condensation generated during condensation. Most of the remaining refrigerant vapor generated in the regenerator 2 flows into the condenser 4 via the slightly throttled second control valve 66 and condenses. In the condenser 4, the heat of condensation generated at the time of condensation is transmitted to the regenerator 12 in the second cycle by the heat transfer tube 20 which has a heat exchange relationship. The refrigerant condensed in the heat exchanger 61 and the condenser 4 is sent to the evaporator 3 and evaporates. In the evaporator 3, the evaporative heat absorbed during the evaporation is transmitted from the absorber 11 in the second cycle by the heat transfer tube 21 having a heat exchange relationship.

The absorption solution of the second cycle was heated through the heat transfer tube 20 by the heat of condensation generated in the condenser 4 of the first cycle in the regenerator 12 to generate refrigerant vapor, and was concentrated. After that, it passes through the heat exchanger 15 and reaches the absorber 11. In the absorber 11, the absorption solution absorbs the refrigerant evaporated in the evaporator 13, and after being diluted, returns to the regenerator 12 via the heat exchanger 15 again by the action of the pump 16. In the absorber 11, the heat of absorption generated at the time of absorption is transferred to the evaporator 3 in the first cycle by the heat transfer tube 21 having a heat exchange relationship. Generated by regenerator 1 2 The refrigerant vapor flows into the condenser 14 and condenses. In the condenser 14, heat is exchanged by the heat medium and the heat transfer tube 31 in order to use the heat of condensation generated during the condensation. In the evaporator 13, heat is exchanged by the heat transfer tube 33 with a heat medium such as cold water in order to use the evaporation heat absorbed during the evaporation.

Next, the operation of the absorption heat pump configured as described above will be described with reference to FIG. FIG. 5 is a During diagram showing a cycle of the heat source absorption heat pump of FIG. This figure shows a typical example of a lithium bromide monohydrate system commonly used in absorption refrigerators. The alphabetic symbols shown in the figure indicate the state of the absorbing solution and the refrigerant, and the same symbols are also circled in FIG.

The absorption solution in the first cycle is heated from an external heat source in the regenerator 2, generates refrigerant vapor and is concentrated (state c: 175 ° C in the figure), and then passes through the heat exchanger 5 (state d) lead to absorber 1. In the absorber 1, the absorbing solution absorbs the refrigerant evaporated in the evaporator 3, is diluted (state a), is heated again through the heat exchanger 5 (state b), and returns to the regenerator 2. Part of the refrigerant vapor generated in the regenerator 2 flows into the heat exchanger 61 and the rest flows into the condenser 4 and condenses (in a state). In the condenser 4, the heat of condensation generated during condensation is transferred to the regenerator 12 in the second cycle by the heat transfer tube 20 that has a heat exchange relationship, but is generated when the heat is condensed in the heat exchanger 61. The condensed heat is not transferred to the recycler 12 of the second cycle. The condensed refrigerant is sent to the evaporator 3 and evaporates (state e). In the evaporator 3, the evaporative heat absorbed during the evaporation is transmitted from the absorber 11 (state A) in the second cycle by the heat transfer tube 21 having a heat exchange relationship.

The absorption solution of the second cycle is passed through the heat transfer tube 20 with the remaining heat of condensation (state) excluding the heat of condensation generated when condensing in the heat exchanger 61 of the first cycle in the regenerator 12. Heated to generate refrigerant vapor and concentrated (State C) After that, it passes through the heat exchanger 15 (state D) and reaches the absorber 11. In the absorber 11, the absorption solution absorbs the refrigerant (state E) evaporated in the evaporator 13, is diluted (state A), and is heated again through the heat exchanger 15 (state B). Return to In the absorber 11, the heat of absorption generated at the time of absorption is transferred to the evaporator 3 (state e) in the first cycle by the heat transfer tube 21 having a heat exchange relationship. The refrigerant vapor generated in the regenerator 12 flows into the condenser 14 and is condensed (state F). The condensed refrigerant (state F) is sent to the evaporator 13 to evaporate (state E).

The operating temperature of the equipment used as the heating source is determined by flowing the heat medium in the following order: condenser heat transfer tube 31 in the second cycle, absorber heat transfer tube 30 in the first cycle, and heat exchanger 61. Refrigerant condensation temperature in the second cycle (state F: 65 ° C in the figure), absorption solution temperature in the first cycle (state a: 75 ° C in the figure), heat exchanger in the first cycle 6 Condensation temperature at 1 (in the state: 95 ° C in the figure) increases in the order of downstream of the heat medium, and therefore the temperature of the heat medium (hot water) that exits the absorption heat pump and enters the air conditioner Higher than.

In this way, the heat of condensation generated during condensation in the condenser 4 of the first cycle is transmitted to the regenerator 12 of the second cycle of the absorption heat pump, but the heat exchange in the first cycle is The heat of condensation that exchanges heat with the hot water in the vessel 61 is not transferred. As a result, the regenerating and concentrating action of the solution in the second cycle is reduced, and the heat of absorption in the second cycle is also reduced, so that it can be balanced with the heat of evaporation in the first cycle. The tendency of the solution to be concentrated can be reduced. The reason will be described below.

As in the above-described conventional example, the ratio of the refrigerating effect of the evaporator to the heat input of the regenerator in the first cycle is calculated by comparing the ratio of the refrigerating effect to the heat input of the regenerator in the second cycle. WO 99/14538 „-. PCT / JP98 / 04179

Let the ratio of the refrigeration effect of the L 0 generator be C 2. The value obtained by dividing the heat output of the condenser by the heat input of the evaporator is defined as RR ₂ in each cycle.

Here, assuming that the heat input to the first cycle is 1, the refrigeration effect Q e of this cycle,

Q e! = C 1

It is.

On the other hand, in the second cycle, part of the heat of condensation from the first cycle is added to the regenerator. Assuming that the proportion of the amount added to the regenerator 1 2 in the second cycle to make the total heat of condensation in the first cycle X is X, the regenerator heat input Qg ₂ is

Q g ₂ = X · C 1 · R. (8)

The refrigeration effect Q e 2 of the second cycle is

Q e ₂ = C ₂ · Q g ₂ = X · C ₂ · C! · R! (9)

The heat of condensation Q c ₂ of the second cycle is

Q c2 = R2-Q e ₂ = X-Ci-C2-Ri-R ₂ (10)

Since the heat of absorption Q a ₂ in the second cycle is the total heat input in the second cycle minus the heat of condensation,

Q a 2 = X (Ci-R ₁ + C ₂ -C iR ₁ -Ci-C ₂ -i-R2) (11) In this absorption heat pump, the evaporator of the first cycle and the Since the absorber exchanges heat, here, the magnitude of the heat of evaporation Q ei in the first cycle and the magnitude of the heat of absorption Q a ₂ in the second cycle are compared. So, taking the difference between them,

Q a2-Q e i = X (Ci-Ri + C2-C i-Ri-Ci-C2-Ri-R2) -Ci

= C i {X-Ri [1 -C ₂ (R ₂ -l)]-1} (12) where the heat of evaporation Q ei in the first cycle and the heat of absorption Q a 2 in the second cycle In order to become, the expression (1 2) needs to be equal to 0, so that X · R i [1 - C 2 (R 2 - 1)] = 1

Needs to be Therefore,

X = l / Ri [1-C ₂ (R2- I)] (13)

Here, for determining the value of X, when determining the value of each variable, since the operating state of the cycle 2 is the same as the conventional example of FIG. 6,: Ri, R _2,

R i = (675-95) / (609-95) = 1.12

R ₂ = (6 3 9-6 5) / (6 0 3-6 5) = 1. 0 6 7

And C ₂ are approximately 0.8 (standard value of single-effect absorption cycle). From equation (13)

X = 1/1. 1 2 8 [1 — 0.8 (1.0 6 7-1)] = 0.9 3 7 That is, by adding 93.7% of the heat of condensation of the first cycle to the regenerator of the second cycle, the heat of evaporation of the first cycle and the heat of absorption of the second cycle are balanced. In this way, the heating medium is heated by a part of the condensation heat of the first cycle, and is used for heating the regenerator 12 of the second cycle by a certain ratio X of the heat of condensation of the first cycle. The heat of evaporation of the first cycle and the heat of absorption in the second cycle can be balanced to reduce the tendency of the solution in the second cycle to be concentrated.

From the above explanation, the ratio X must be X ^ 1, but for that purpose, from equation (13),

X = 1 / R! [1-C ₂ (R ₂ — 1)] ≤ 1

Therefore,

C ₂ ≤ (R 1-1) / (R ₂ — 1) / R 1 (1 4)

Needs to be Calculating this C ₂ gives

C ₂ ≤ 0.12 1/0 .0 6 7 / 1.12 8 = 1.69 4

Becomes This is, C ₂ that is COP of the second cycle 1. 6 9 4 Unless it exceeds, it indicates that the ratio Χ≤ 1 holds, and this value cannot be achieved as C 0 の in the single-effect absorption refrigeration cycle. ≤ 1 holds. Therefore, by always using a certain percentage X of the heat of condensation in the first cycle to heat the regenerator 12 in the second cycle, the heat of evaporation in the first cycle and the heat of absorption in the second cycle are reduced. Can be balanced.

Next, the operation when the absorption heat pump configured as described above is combined with desiccant air conditioning will be described. In Figure 4, the air in the air-conditioned space 101

The (processed air) is sucked into the blower 102 via the passage 107, is boosted in pressure, and is sent through the passage 108 to the receiver 1103, where it is sucked at the receiver outlet. The moisture in the air is adsorbed by the wetting agent, and the absolute humidity decreases. At the time of adsorption, the temperature of air rises due to heat of adsorption. The air whose humidity has dropped and the temperature has risen is sent to a sensible heat exchanger 104 via a path 109, where it is cooled by exchanging heat with outside air (regenerated air). The cooled air is sent to the cooler 115 via the path 110 and further cooled. The cooled treated air is sent to the humidifier 105 and cooled by water injection or evaporative humidification in the course of an isoruby, and is returned to the air-conditioned space 101 via the route 112.

Since desiccant low water adsorbs moisture in this process, regeneration is necessary. In this embodiment, the following operation is performed using outside air as regeneration air. Outside air (OA) is sucked into the blower 130 through the path 124 and is pressurized and sent to the sensible heat exchanger 104, where it cools the treated air and rises in temperature to the path 125 After that, it flows into the next sensible heat exchanger 1 2 1 and exchanges heat with the hot air after regeneration to increase the temperature. Furthermore, the regenerated air that has exited the sensible heat exchanger 122 flows into the heater 120 via the path 126 and is heated by the hot water, where the temperature rises to 60 to 80 ° C, and the relative humidity decreases. I do. This process changes the sensible heat of the regeneration air. Since the specific heat of air is significantly lower than that of hot water and the temperature change is large, even if the flow rate of hot water is reduced and the temperature change is increased, heat exchange is performed efficiently and the transfer power can be reduced. . The regenerated air whose relative humidity has decreased after exiting the heater 120 passes through the desiccant heater 103 to remove moisture from the desiccant heater and perform a regenerating operation. The regenerated air that passed through the desiccant outlet overnight 103 flows into the sensible heat exchanger 122 via the route 128, and after preheating the regenerated air before regeneration, passes the route 129. Discarded as exhaust ο

The process up to this point will be described with reference to the psychrometric chart of Fig. 6. The air in the air-conditioned space 101 (processed air: state K) is sucked into the blower 102 through the route 107 and pressurized. Through the route 108 to the desiccant towel 103, where the moisture in the air is adsorbed by the desiccant mouth and the absolute humidity decreases, and the temperature of the air rises due to the heat of adsorption (state L ). The air whose humidity has dropped and the temperature has risen is sent to the sensible heat exchanger 104 via the path 109 and cooled by exchanging heat with the outside air (regenerated air) (state M). The cooled air is sent to the cooler 115 via the route 110 and is further cooled (state N), and the cooled air is sent to the humidifier 105 via the route 111 for water injection or vaporization. By humidification, the temperature decreases during the iso-evening ruby process (state P), and route 1

The air is returned to the air-conditioned space 101 via 1 2. In this way, an en-ubiquity ruby difference △ Q is generated between the return air (state K) and the supply air (state P) in the room, thereby cooling the air-conditioned space 101. .

On the other hand, desiccant regeneration is performed as follows. Outside air for regeneration (O A

: State Q) is sucked into the blower 130 via the path 124 and is pressurized, sent to the sensible heat exchanger 104, cools the processing air, and rises in temperature (state

:: R) Flow into the next sensible heat exchanger 1 2 1 via route 1 2 5 The temperature rises due to heat exchange with warm air (state S). Furthermore, the regenerated air exiting the sensible heat exchanger 121 flows into the heater 120 via the path 126, is heated by the hot water, is heated to 60 to 80 ° C, and the relative humidity is reduced. Although the temperature drops (state T), the relative humidity further decreases in the embodiment of FIG. 4 because the hot water is heated by the heat exchanger 61 having a higher working temperature than the conventional embodiment. The regenerated air, whose relative humidity has decreased, passes through the desiccant towel 103 to remove moisture from the desiccant towel (state U). The regenerated air that passed through the desiccant outlet 103 passed through the path 128 to the sensible heat exchanger 122, and exited the sensible heat exchanger 104 and preheated the regenerated air before regeneration. After the temperature drops (State V), it is discarded to the outside as exhaust gas through the route 12. In the embodiment of FIG. 4, as described above, since the hot water is heated by the heat exchanger 61 having a higher working temperature than in the conventional embodiment, the desiccant regeneration ability is further increased, and the dehumidifying effect is thus reduced. Get higher.

In this way, desiccant air conditioning is performed by repeating regeneration of the desiccant and dehumidification and cooling of the treated air. In addition, the method of using the exhaust accompanying the indoor ventilation as the regeneration air has been widely used in the desiccant air conditioning, but in the present invention, the exhaust from the room may be used as the regeneration air. The same effects as in the present embodiment can be obtained.

Thus, by heating the heat medium in the heat exchanger 61 of the first cycle by a part of the heat of condensation of the first cycle, the regenerator 12 of the second cycle of the absorption heat pump is However, the heat of condensation generated during condensation in the condenser 4 of the first cycle is transferred, but the heat of condensation exchanged in the heat exchanger 61 of the first cycle is not transferred, and the condensation of the first cycle is performed. Only a certain percentage of the heat, X, is transmitted. As a result, the solution of the second cycle The heat of vaporization of the second cycle, and thus the heat of vaporization of the first cycle can be balanced and the tendency of the second cycle solution to thicken can be reduced .

In the present embodiment, in the second cycle, the refrigerant level detection sensor 62 of the evaporator 13, the controller 63, the controller 63, the first control valve 65, the second control A signal path 72 connecting the valve 66 and a signal path 70 connecting the controller 63 and the coolant level sensor 62 are provided so that the coolant level sensor 62 exceeds the set value. When the controller detects that the liquid level has risen, the controller opens the first control valve 65 and throttles the second control valve 66. This is a control operation required when the solution concentration in the first cycle is abnormally concentrated. As described above, this kind of absorption heat pump essentially has the refrigeration effect of the first cycle and the absorption effect of the second cycle. It has a characteristic that it is smaller than heat, and the solution in the second cycle tends to concentrate. To prevent this, the control valve 6 5 It may be possible to always open the air at a predetermined opening and condense the predetermined refrigerant in the heat exchanger 61.

As described above, the amount of refrigerant condensed in the heat exchanger 61 necessary for balancing the heat of absorption in the second cycle and the heat of evaporation in the first cycle is very small (6.3% in calculation). Therefore, since it is not necessary to pass the entire amount of the heating medium, a path 56 bypassing the heat exchanger 61 may be provided as shown in FIG. 4, and the flow of the hot water in the heat exchanger 61 may be provided. A throttle 80 may be provided in path 56 to prevent the flow rate in paths 53 and 55 from decreasing due to resistance. Alternatively, a pump may be provided in path 53 or 55 (Fig. (Not shown) can be installed. Furthermore, in the present embodiment, the heat exchanger 61 is configured to guide and heat the heat medium for heating the regenerated air of the desiccant air conditioner. However, the desiccant 103 is directly connected to the heat exchanger 61. Guides regeneration air before passing And heat it.

FIG. 7 shows a third embodiment of the present invention. In this embodiment, a heat exchanger tube 35 of a heat exchanger for condensing a part of the refrigerant generated in the regenerator 2 of the first cycle is installed directly inside the condenser 4, and the heat exchanger tube 35 The heat medium that extracts heat is heated by the absorber of the first cycle and the condenser of the second cycle, and the heating amount is adjusted by the hot water outlet path of the absorber 1 in the first cycle of the heat medium path This is configured to be performed by the three-way valve 71 provided in 53. In this embodiment, most of the hot water passing through the three-way valve 71 flows through the path 56, and the remaining part passes through the heat transfer tube 35 via the path 54. In addition, the refrigerant level sensor 62 of the evaporator 13 in the second cycle, the controller 63, a signal path 72 connecting the controller 63 and the three-way valve 71, and a controller 63 A signal path 70 is provided to connect the refrigerant level detection sensor 62 with the refrigerant level detection sensor 62.When the refrigerant level detection sensor 62 detects that the liquid level has risen beyond the set value, the controller 63 Open the path 54 side of the valve 71, narrow the path 56 side to increase the flow rate of hot water passing through the heat transfer tube 35, and increase the amount of refrigerant condensed in the heat transfer tube 35. The amount of refrigerant condensed is reduced, reducing the amount of heat applied to regenerator 12 in the second cycle. Thus, as in the second embodiment, the solution of the second cycle has a reduced regenerating and concentrating action, and accordingly the heat of absorption of the second cycle is also reduced, and the heat of evaporation of the first cycle is reduced. The balance can be balanced and the tendency of the second cycle solution to concentrate can be reduced. The operation of the absorption heat pump and the operation of the desiccant air conditioner are the same as in the second embodiment, and therefore, description thereof will be omitted. Industrial applicability O The present invention is suitable for use as an air conditioner for general dwellings or larger buildings used as, for example, supermarkets, offices and the like.

Claims

The scope of the claims

1. The path of the treated air where moisture is adsorbed by the desiccant, and the path of regenerated air that is heated by the heating source, passes through the desiccant after adsorbing the moisture and desorbs and regenerates the moisture in the desiccant. The first cycle of an absorption refrigeration cycle with an air conditioner having at least an evaporator, absorber, regenerator, and condenser as components, and at least an evaporator, absorber, regenerator, and condenser The apparatus comprises a second absorption refrigeration cycle that operates at a lower temperature than the first cycle, forming a heat exchange relationship between the evaporator of the first cycle and the absorber of the second cycle, And a heat exchange relationship is formed between the condenser of the first cycle and the regenerator of the second cycle, and the refrigerant is cooled in the refrigerant path from the condenser of the first cycle to the evaporator. Heat exchanger And a yield heat pump,

The regenerative air of the air conditioner is heated by using the heat of absorption of the first cycle and the heat of condensation of the second cycle of the absorption heat pump as a heat source to regenerate the desiccant and the second heat of the absorption heat pump. In an air conditioning system that cools the processing air of the air conditioner using the evaporation heat of the cycle as a cooling heat source,

In the first cycle of the absorption heat pump, the heat exchanger for cooling the refrigerant provided in the refrigerant path is guided to the heat exchanger for heating the regenerated air or the regenerated air to exchange heat with the refrigerant. And air conditioning system.

2. After the regeneration air or the heating medium for heating the regenerated air is introduced into the heat exchanger for cooling the refrigerant provided in the refrigerant path of the first cycle of the absorption heat pump and heat exchange is performed with the refrigerant, 2 cycle condenser and 1st cycle The air conditioning system according to claim 1, wherein the air conditioning system is configured to be guided to an absorber of a vehicle for heating.

3. The first cycle that forms an absorption refrigeration cycle with at least an evaporator, absorber, regenerator, and condenser as components, and at least an evaporator, absorber, regenerator, and condenser as components. A second absorption refrigeration cycle operating at a lower temperature than the first cycle, forming a heat exchange relationship between the evaporator of the first cycle and the absorber of the second cycle, and In an absorption heat pump that forms a heat exchange relationship between the condenser of the first cycle and the regenerator of the second cycle, the absorption of the first cycle is partially performed by the heat of condensation of the first cycle. An absorption heat pump characterized in that a heat exchange relationship is formed so as to heat a heat medium for extracting heat with a condenser and a condenser in a second cycle.

4. The heat medium after extracting the heat with the condenser of the second cycle and the absorber of the first cycle is heated by a part of the heat of condensation of the first cycle. 3. The absorption heat pump according to 3.

5. Detect the concentration of the absorbing solution in the second cycle, and if the concentration increases above the set value, the heat of condensation in the first cycle will cause the absorption in the first cycle and the condensation in the second cycle. 5. The absorption heat pump according to claim 3, wherein an amount of heat for heating a heat medium from which heat is taken out by the heater is increased.

6. Detect the refrigerant level of the evaporator in the second cycle and check that the level is below the set value. 6. The heat absorption device according to claim 5, wherein when the temperature rises, the amount of heat for heating the heat medium from which heat is taken out by the absorber in the first cycle and the condenser in the second cycle is increased. Single pump.

7. The path of the treated air where moisture is adsorbed by the desiccant, and the path of regenerated air which is heated by the heating source, passes through the desiccant after adsorbing the moisture and desorbs and regenerates the moisture in the desiccant. An air conditioner with a sensible heat exchanger between the treated air to which moisture has been adsorbed and the regeneration air before desiccant regeneration and before being heated by the heating source, and at least an evaporator and absorber A first cycle that forms an absorption refrigeration cycle using a regenerator and a condenser as a constituent device, and at least a lower temperature than the first cycle using a evaporator, an absorber, a regenerator, and a condenser as a constituent device. An operating second absorption refrigeration cycle, forming a heat exchange relationship between the first cycle evaporator and the second cycle absorber, and the first cycle condenser and the second cycle Between the cycle regenerator An absorption heat pump that forms a heat exchange relationship, and heats the regenerated air of the air conditioner using the absorption heat of the first cycle and the condensation heat of the second cycle of the absorption heat pump as a heat source to reduce the desiccant. In an air conditioning system that performs regeneration and cools processing air of the air conditioner by using evaporation heat of a second cycle of the absorption heat pump as a cooling heat source, a part of the heat of condensation of the absorption heat pump in the first cycle An air conditioning system characterized in that a heat exchange relationship is formed so as to heat the regeneration air or a heat medium serving as a heating source for the regeneration air.

8. Regeneration air or a heating medium that heats the regeneration air is led to a heat exchanger that extracts a part of the condensation heat of the first cycle of the absorption heat pump, and the refrigerant and heat 8. The air conditioning system according to claim ⁷ , wherein the air conditioning system is configured to be replaced.