JP3480772B2 - Absorption heat pump - Google Patents

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an absorption heat pump, and more particularly to an absorption heat pump used as a heat source device for a desiccant type air conditioning system.

[0002]

Desiccant air conditioning systems are well known and are described in U.S. Pat. No. 2,700,537. In the desiccant type air conditioning system shown in this known example, as a heat source for regeneration of the desiccant (hygroscopic agent),
A heat source having a temperature of about 100 to 150 ° C. is required, and an electric heater or a boiler is exclusively used as the heat source. Due to the recent improvement of the desiccant, a desiccant air-conditioning system capable of reproducing the desiccant even at a temperature of 60 to 80 ° C. has been developed and can be operated by a heat source having a low temperature.
FIG. 5 shows an example of a known desiccant air conditioner improved in this way, and FIG. 6 is a Mollier diagram showing the operating state of the air conditioner of the example of FIG. In FIG. 5, reference numeral 10
1 is an air-conditioned space, 102 is a blower, 103 is a desiccant rotor, 104 is a sensible heat exchanger, 105 is a humidifier, 106
Is a water supply pipe of a humidifier, 107 to 111 are air passages for conditioned air, 130 is a blower of regenerated air, 120 is a heat exchanger for hot water and regenerated air (hot water heat exchanger), 121 is a sensible heat exchanger, 122 and 123 are hot water pipes, and 124 to 12
Reference numeral 9 is an air passage for regeneration air.

Also, in the figure, alphabets K to
V is a symbol indicating the state of air corresponding to FIG. 6, and S
A represents supply air, RA represents return air, OA represents outside air, and EX represents exhaust air.

The operation of this known device will be described. In FIG. 5, the air (process air) in the room 101 to be conditioned is sucked by the blower 102 via the path 107 and the pressure is increased to the desiccant rotor 103 via the path 108. Moisture in the air is adsorbed by the desiccant rotor hygroscopic agent and the absolute humidity decreases. During adsorption, the temperature of the air rises due to the heat of adsorption. The air whose humidity has dropped and whose temperature has risen is sent to the sensible heat exchanger 104 via the path 109 and is cooled by exchanging heat with the outside air (regenerated air). The cooled air is sent to the humidifier 105 via the route 110, and the temperature is lowered in the isenthalpic process by water injection or vaporization-type humidification, and the route 111 is used.
And is returned to the air-conditioned space 101.

Since the desiccant adsorbs water in this process, it needs to be regenerated. In this conventional example, it is carried out as follows using outside air. The outside air (OA) is sucked by the blower 130 via the path 124, is pressurized, and is sent to the sensible heat exchanger 104. The processed air is cooled, and the temperature of the outside air itself rises. Flows in and heat-exchanges with the hot air after regeneration to raise the temperature. Further sensible heat exchanger 1
The regenerated air exiting 21 passes through the route 126 and the hot water heat exchanger 1
20 and heated by hot water, the temperature rises to 60 to 80 ° C. and the relative humidity decreases. The regenerated air with reduced relative humidity passes through the desiccant rotor 103 to remove moisture from the desiccant rotor.

The regenerated air that has passed through the desiccant rotor 103 flows into the sensible heat exchanger 121 via the path 128, performs residual heat of the regenerated air before regeneration, and then is discharged to the outside as exhaust gas via the path 129.

The process up to this point will be described with reference to the moist air diagram. In FIG. 6, the air in the room 101 to be conditioned (process air: state K) passes through the path 107 and the blower 102.
Is sucked up and pressure-increased and is sent to the desiccant rotor 103 via the path 108, moisture in the air is adsorbed by the desiccant rotor's hygroscopic agent, the absolute temperature is lowered, and the temperature of the air is raised by the adsorption heat (state L). The air whose humidity has dropped and whose temperature has risen is sent to the sensible heat exchanger 104 via the path 109 and is cooled by exchanging heat with the outside air (regenerated air) (state M). The cooled air passes through the path 110 and the humidifier 105.
The temperature is lowered in the isenthalpic process by water injection or vaporization-type humidification (state P) and returned to the air-conditioned space 101 via the path 111.

In this way, the enthalpy difference ΔQ is generated between the return air (K) and the supply air (P) in the room, whereby the air-conditioned space 101 is cooled. The desiccant reproduction is performed as follows. Outside air (OA: State Q) is route 1
After passing through 24, the air is sucked by the blower 130, the pressure is increased and sent to the sensible heat exchanger 104, the process air is cooled, and the temperature of the device itself rises (state R).
1, and heat-exchanges with the hot air after regeneration to raise the temperature (state S). Further, the regenerated air exiting the sensible heat exchanger 121 flows into the hot water heat exchanger 120 via the path 126, is heated by the hot water, and is heated to 60 to 80 ° C., and the relative humidity is lowered (state T). The regenerated air with reduced relative humidity passes through the desiccant rotor 103 to remove the moisture in the desiccant rotor (state U). Desiccant rotor 10
The regenerated air that has passed through No. 3 flows into the sensible heat exchanger 121 via the path 128, performs the residual heat of the regenerated air before the regeneration to lower the temperature itself (state V), and is then discharged to the outside as exhaust gas via the path 129. To be

In this way, the desiccant air-conditioning is performed by repeating the desiccant regeneration and the dehumidification and cooling of the treated air. The coefficient of operation (CO
P) is shown as a value (ΔQ / ΔH) obtained by dividing the cooling effect ΔQ in FIG. 6 by the regeneration heating amount ΔH. In the conventional desiccant air conditioning, the action of hot water for heating the regeneration air is higher than that in the initial one. Although the temperature has dropped, a boiler is used as the heat source for the desiccant regeneration, and the high-quality energy (exergy) of the heat quantity of 1 of the fuel is still used as the heat quantity of less than 1 at a temperature lower than 100 ° C. Therefore, other heat-driven refrigerators (for example, double-effect absorption refrigerators)
There is a defect that the coefficient of operation (COP) is low as compared with an air conditioning system that cools and dehumidifies the air by using.

[0010]

SUMMARY OF THE INVENTION The present invention has been made in view of the above-mentioned problems, and as a heat source machine instead of a boiler, a drive input heat quantity added from the outside for heating regenerated air and an evaporation pumped from a low temperature. Combined with warm water at an intermediate temperature of about 60 to 80 ° C that can take out the amount of heat added with heat, and cold water at about 15 ° C for cooling that can further cool the air in the process of cooling the treated air performed during the desiccant air conditioning cycle. To provide an absorption heat pump that can be used for an air conditioning system that increases the energy efficiency of desiccant air conditioning and that exceeds the energy efficiency of an air conditioning system that cools and dehumidifies air using a conventional refrigerator by providing an absorption heat pump that can be supplied by With the goal.

[0011]

According to the present invention, there is provided a first evaporator, a first absorber, a first regenerator, and a first condenser for performing an absorption refrigeration cycle. Cycle device, second evaporator, second absorber, second regenerator, second
And a second cycle device for performing an absorption refrigeration cycle that operates at a lower temperature than the absorption refrigeration cycle of the first cycle device, the first evaporator and the second absorption device. A first heat exchange device for exchanging heat with the regenerator, and a second heat exchange device for exchanging heat with the first condenser and the second regenerator,
A medium conveying means for taking out the heat of absorption of the first absorber and the heat of condensation of the second condenser to the outside in order to make the temperature of the absorption solution of the first absorber higher than the refrigerant condensation temperature of the second condenser. The medium conveying means is a path of a medium for carrying out heat exchange by passing in order from the condenser heat transfer tube provided in the second condenser to the absorber heat transfer tube provided in the first absorber. Is. A heat transfer tube for extracting heat of vaporization is provided in the second evaporator.

[0012]

In this specification, the absorption heat pump also includes a refrigerator. Further, the absorption heat of the first cycle device and the condensation heat of the second cycle device are used as outside heat heat so that the absorption solution temperature of the first cycle device becomes higher than the refrigerant condensation temperature of the second cycle device. Since the carrier medium to be taken out is configured to cause a temperature difference, if an absorption heat pump (including a refrigerator) of the present invention is used as a heat source device instead of a desiccant air conditioning boiler,
The amount of heat corresponding to the amount of driving input heat added to the regenerator of the first cycle plus the heat of evaporation of the second cycle is used as the heat of condensation of the first cycle and the heat of absorption of the second cycle. 60 to 8 for heat medium or desiccant regeneration
It can be taken out in the form of warm water with an intermediate temperature of 0 ° C,
Further, the heat of vaporization of the evaporator of the second cycle can be taken out in the form of cold water of about 15 ° C. for cooling that can be used in the process of cooling the air performed during the desiccant air conditioning cycle.
It is possible to provide a desiccant air-conditioning system that can save the primary energy required for desiccant regeneration, increase the cooling effect, and thus have a high coefficient of operation.

[0014]

BEST MODE FOR CARRYING OUT THE INVENTION An embodiment of an absorption heat pump according to the present invention will be described below with reference to FIGS. 1 to 4.

FIG. 1 is a diagram showing the basic structure of an absorption heat pump according to the present invention, which comprises a first evaporator 3, a first absorber 1, a first regenerator 2, a first condenser 4 and A first cycle device that forms an absorption type refrigeration cycle using the first heat exchanger 5 of the absorbing solution as a component device, a second evaporator 13, a second absorber 11, a second regenerator 12, and a second cycle device. Condenser 1
4, and a second heat exchanger 15 for absorbing solution as a constituent device, and a second cycle device that operates at a temperature lower than that of the first cycle device, and a first evaporator of the first cycle device. 3 and the second absorber 1 of the second cycle device
To form a first heat exchanging device 21 for exchanging heat with the first condensing device 1 and the first condenser 4 and the second condensing device of the first cycle device.
Forming a second heat exchanging device 20 for exchanging heat with the second regenerator 12 of the second cycle device, and the absorption solution temperature of the first cycle device is the refrigerant condensing temperature of the second cycle device. The path 32 of the carrier medium that takes out the heat of absorption of the first cycle device and the heat of condensation of the second cycle device to the outside as utilization heat is set so as to be higher than that of the condenser heat transfer pipe 31 of the second cycle device. The heat transfer is performed by passing through the absorber heat transfer tubes 30 of the first cycle device in this order.

The absorption cycle of the absorption heat pump configured as described above will be described below. The absorbing solution of the first cycle device is heated in the regenerator 2 from an external heat source (not shown) via the heat transfer tube 34 to generate refrigerant vapor, and after being concentrated, passes through the heat exchanger 5 and then the absorber 1 Leading to. 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. Since the absorber 1 utilizes the absorption heat generated during absorption, heat is exchanged with a heat medium such as hot water by the heat transfer tube 30. The refrigerant vapor generated in the regenerator 2 is transferred to the condenser 4
Flows in and condenses. In the condenser 4, the heat of condensation generated during the condensation is transferred to the regenerator 12 of the second cycle device by the heat transfer tube 20 having a heat exchange relationship. The condensed refrigerant is sent to the evaporator 3 and evaporated. In the evaporator 3, the heat of evaporation, which is absorbed during evaporation, is transferred from the absorber 11 of the second cycle device by the heat transfer tube 21 having a heat exchange relationship.

The heat transfer tube of the condenser 4 may be directly installed in the regenerator 12 of the second cycle device as in the case of a normal double-effect absorption refrigerator, and the same operation is performed. be able to.

The absorption solution of the second cycle device is the regenerator 1.
At 2, the heat of condensation of the first cycle device is heated through the heat transfer tube 20, the refrigerant vapor is generated, and after being concentrated, the heat is passed through the heat exchanger 15 to the absorber 11. 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 again by the action of the pump 16. In the absorber 11, the absorption heat generated during absorption is transferred to the evaporator 3 of the first cycle device 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. Since the condenser 14 utilizes the heat of condensation generated during condensation, heat is exchanged between the heat medium and the heat transfer tube 31.

Further, the heat medium is caused to flow in the order of the condenser heat transfer tube 31 of the second cycle device to the absorber heat transfer tube 30 of the first cycle device, so that the temperature of the absorbing solution of the first cycle device becomes the second. It becomes higher than the refrigerant condensation temperature of the cycle device. The condensed refrigerant is sent to the evaporator 13 and evaporated. Since the evaporator 13 uses the heat of evaporation that absorbs heat during evaporation, heat is exchanged with a heat medium such as cold water by the heat transfer tube 33. The heat transfer tube of the absorber 11 may be installed directly in the evaporator 3 of the first cycle, and the same operation can be performed.

Next, the operation of the absorption heat pump configured as described above will be described with reference to FIG. FIG. 2 is a Duhring diagram showing the cycle of the absorption heat pump of FIG. This figure shows a lithium bromide-water system that is generally used in absorption refrigerators as a representative example. The alphabetical symbols shown in the figure show the states of the absorbing solution and the refrigerant, and the same symbols surrounded by circles are also shown in FIG. The absorbing solution of the first cycle device is heated by an external heat source in the regenerator 2 to generate a refrigerant vapor and be concentrated (state c: 175 ° C. in the figure), and then passes through the heat exchanger 5 (state d) to be absorbed. Reach vessel 1. In the absorber 1, the absorbing solution absorbs the refrigerant evaporated in the evaporator 3, is diluted (state a), is heated again via the heat exchanger 5 (state b) and returns to the regenerator 2. Regenerator 2
The refrigerant vapor generated in 1 flows into the condenser 4 and is condensed (state f). In the condenser 4, the heat of condensation generated during the condensation is transferred to the regenerator 12 of the second cycle device by the heat transfer tube 20 having a heat exchange relationship. The condensed refrigerant is sent to the evaporator 3 and evaporated (state e). In the evaporator 3, the heat of evaporation absorbed during evaporation is transferred from the absorber 11 (state A) of the second cycle device by the heat transfer tube 21 having a heat exchange relationship. The absorbing solution of the second cycle device is heated in the regenerator 12 by the heat of condensation of the first cycle device (state f) through the heat transfer tube 20, generates refrigerant vapor, and is condensed (state C) and then heated. It goes through the exchanger 15 (state D) to the absorber 11. In the absorber 11, the absorbing solution absorbs the refrigerant (state E) evaporated in the evaporator 13, is diluted (state A), and then heat exchanger 1 again.
After being heated through 5 (state B), it returns to the regenerator 12. In the absorber 11, the absorption heat generated during absorption is transferred to the evaporator 3 (state e) of the first cycle device by the heat transfer tube 21 having a heat exchange relationship. The refrigerant vapor generated in the regenerator 12 is
It flows into the condenser 14 and is condensed (state F). Heat medium second
By flowing in order from the condenser heat transfer tube 31 of the first cycle device to the absorber heat transfer tube 30 of the first cycle device.
Solution temperature of the cycle device (state a: 75 in the figure)
C.) becomes higher than the refrigerant condensation temperature (state F: 65 ° C. in the figure) of the second cycle device. The condensed refrigerant (state F) is sent to the evaporator 13 and evaporated (state E).

In the absorption heat pump configured as described above, the high temperature heat applied from the outside to the regenerator 2 of the first cycle device is used for concentrating the cycle solution of the first cycle device and is generated at that time. Since the retained heat of the refrigerant vapor can be reused for the concentration of the cycle solution of the second cycle device, one heat input can concentrate the solution that serves as the driving force for the two refrigeration cycles. In addition, the heat of absorption of the second cycle device is used in the system as the heat of vaporization of the first cycle device.
Therefore, absorption heat can be used in the first cycle device, and condensation heat and evaporation heat can be used in the second cycle device. As shown in FIG. 2, the heat generated in the process of absorption and condensation is 60 ° C. to 8 ° C.
It can be taken out as warm water at 0 ℃,
The evaporation heat of the cycle device can be taken out as cold water at about 15 ° C. Looking at the heat balance of the entire cycle of this embodiment, the heat input to the cycle of this device is
The high temperature heat externally applied to the regenerator of the cycle device and the heat taken from the cold water by the evaporator of the second cycle device, and the heat output from the entire cycle is the first cycle device added to the hot water. And the heat of condensation of the second cycle device.

Therefore, in addition to the high-temperature heat applied from the outside to the regenerator of the first cycle device, the heat taken from the cold water by the evaporator of the second cycle device is added to the hot water, so that it is used by the hot water. The amount of heat possible is greater than the amount of heat applied externally to the regenerator of the first cycle device. As described above, the entire cycle in which the present invention is carried out acts as a heat pump.

Further, the absorption heat of the first cycle device and the condensation heat of the second cycle device are externally controlled so that the temperature of the absorption solution of the first cycle device becomes higher than the refrigerant condensation temperature of the second cycle device. As described below, the transport medium that is extracted as the utilization warm heat, that is, the hot water path, is configured.The heat exchange with the air when using the warm water for desiccant air conditioning is a sensible heat change on the air side, and the specific heat of the air is the warm water. Since the temperature change is significantly lower than that of the above, the heat exchange is performed efficiently even if the flow rate of hot water is decreased to increase the temperature change. The condensation temperature can be set lower than the absorption temperature of the first cycle device on the outlet side,
By doing so, the pressure and temperature of the regenerator 2 of the first cycle device can be lowered, so that the amount of heating to the regenerator 2 of the first cycle device is reduced. Next, the operation when the absorption heat pump configured as described above is combined with desiccant air conditioning will be described with reference to FIGS.

FIG. 4 is a moist air diagram showing the operating state of the air conditioning portion of the embodiment of FIG. In the example of FIG.
The desiccant air conditioner and hot water pump 1 of the absorption heat pump of the embodiment shown in FIG.
60 and a hot water pump 150.
The desiccant air conditioner of FIG. 3 is configured as shown below. The air-conditioned space 101 is connected to the suction port of the blower 102 of the treated air via the path 107, the outlet of the blower 102 is connected to the desiccant rotor 103 via the route 108, and the outlet of the treated air of the desiccant rotor 103 is the regenerated air. Sensible heat exchanger 104 and path 10 that are in a heat exchange relationship with
9, the sensible heat exchanger 104 is connected to the chilled water heat exchanger 115 via the path 110 at the outlet of the treated air,
The outlet of the treated air of the cold water heat exchanger 115 is connected to the humidifier 105 via the path 119, and the outlet of the treated air of the humidifier 105 is connected via the air-conditioned space 101 and the path 111 to cycle the treated air. Form.

On the other hand, the air path for regeneration connects the outside air to the suction port of the blower 130 for regeneration air via the path 124, and the outlet of the blower 130 has a sensible heat exchange in a heat exchange relationship with the process air. The sensible heat exchanger 10 is connected to the vessel 104.
The outlet of the regenerated air of No. 4 is connected to the low temperature side inlet of another sensible heat exchanger 121 via the path 125, and the sensible heat exchanger 121
Of the desiccant rotor 103 is connected to the regeneration air inlet of the desiccant rotor 103 via a path 127, and the regeneration air outlet of the hot water heat exchanger 120 is coupled to the desiccant rotor 103 via a path 126. The outlet of the regenerated air is connected to the high temperature side inlet of the sensible heat exchanger 121 via the path 128, and the high temperature side outlet of the sensible heat exchanger 121 is connected to the external space via the path 129 to regenerate the regenerated air to the outside. Form a cycle of intake from the outside and exhaust to the outside. The hot water inlet of the hot water heat exchanger 120 is connected via a path 122 to the outlet of the absorber 1 of the first cycle device of the hot water path of the absorption heat pump, and the hot water outlet of the hot water heat exchanger 120 is the path 1
23 and the hot water pump 150 to connect to the inlet of the condenser 14 of the second cycle device in the hot water path of the absorption heat pump. The cold water inlet of the cold water heat exchanger 115 is connected to the outlet of the evaporator 13 of the second cycle device of the cold water path of the absorption heat pump via the path 117, and the cold water outlet of the cold water heat exchanger 115 is the path 118 and the pump. It is connected via 160 to the inlet of the evaporator 13 of the second cycle device of the cold water path of the absorption heat pump. In the figure, the alphabets K to V surrounded by circles are symbols showing the state of air corresponding to FIG. 4, SA is supply air, RA is return air, and OA.
Represents outside air and EX represents exhaust.

The operation of this embodiment will be described with reference to FIG.
In, the air in the room 101 to be air-conditioned (processed air) is sucked by the blower 102 via the path 107, is pressurized, is sent to the desiccant rotor 103 via the path 108, and the moisture in the air is adsorbed by the desiccant rotor hygroscopic agent. Absolute humidity drops. During adsorption, the temperature of the air rises due to the heat of adsorption. The air whose humidity has dropped and whose temperature has risen is route 109
After passing through the sensible heat exchanger 104, the sensible heat exchanger 104 is cooled by exchanging heat with the outside air (regenerated air). The cooled air is sent to the cold water heat exchanger 115 via the path 110 and further cooled. The cooled treated air is sent to the humidifier 105, and its temperature is lowered in the isenthalpic process by water injection or vaporization humidification, and is returned to the air-conditioned space 101 via the path 111.

Since the desiccant rotor has adsorbed water in this process, it needs to be regenerated. In this embodiment, the outside air is used as the regenerating air to perform the following procedure. The outside air (OA) is sucked by the blower 130 via the path 124, is pressurized, and is sent to the sensible heat exchanger 104. The processed air is cooled, and the temperature of the outside air itself rises. Flows in and heat-exchanges with the hot air after regeneration to raise the temperature. Furthermore, the regenerated air that exits the sensible heat exchanger 121 is route 1
After passing through 26, it flows into the hot water heat exchanger 120 and is heated by the hot water, and the temperature rises to 60 to 80 ° C., and the relative humidity decreases. This process is a sensible heat change of the regenerated air, and the specific heat of the air is significantly lower than the hot water and the temperature change is large. Therefore, even if the flow rate of the hot water is reduced and the temperature change is increased, the heat exchange is efficiently performed.

Therefore, the condensing temperature of the second cycle device, which is the inflow side of the hot water of the absorption heat pump for producing hot water, can be set lower than the absorption temperature of the first cycle device, which is the exit side, and by doing so. Since the pressure and temperature of the regenerator 2 of the first cycle device can be lowered, the amount of heating to the regenerator 2 of the first cycle device is reduced. Further, since the flow rate is reduced by increasing the temperature difference of the hot water used, the transport power is reduced. The regeneration air that has exited the hot water heat exchanger 120 and has reduced relative humidity passes through the desiccant rotor 103 to remove moisture from the desiccant rotor and perform regeneration. Desiccant rotor 103
The regenerated air that has passed through the path passes through the path 128 and the sensible heat exchanger 1
After flowing into No. 21 and performing residual heat of the regenerated air before regeneration, it is discharged to the outside as exhaust gas via the route 129.

The above process will be described with reference to the moist air diagram. In FIG. 4, the air in the room 101 to be conditioned (process air: state K) passes through the path 107 and the blower 102.
Is sucked up and pressure-increased and is sent to the desiccant rotor 103 via the path 108, the moisture in the air is adsorbed by the absorbent of the desiccant rotor 103, the absolute temperature decreases, and the temperature of the air rises due to the heat of adsorption (state L). The air whose humidity has decreased and whose temperature has risen is sent to the sensible heat exchanger 104 via the path 109 and exchanges heat with the outside air (regenerated air) to be cooled (state M). The cooled air is sent to the cold water heat exchanger 115 via the path 110 and further cooled (state N). The temperature of the cooled air is lowered via the path 119 (state P) and returned to the conditioned space 101 via the path 111. In this way, the enthalpy difference ΔQ is generated between the return air (state K) and the supply air (state P) in the room, whereby the air-conditioned space 101 is cooled. The desiccant reproduction is performed as follows. The outside air (OA: state Q) for regeneration is sucked by the blower 130 via the path 124 and the pressure thereof is increased, so that the sensible heat exchanger 104 is heated.
To the next sensible heat exchanger 121 through the path 125 (state R) path 125 to cool the treated air and heat-exchange with the hot air after regeneration to raise the temperature ( State S). Further, the regenerated air exiting the sensible heat exchanger 121 flows into the hot water heat exchanger 120 via the path 126, is heated by the hot water, and is heated to 60 to 80 ° C, and the relative humidity is lowered (state T). The regenerated air with reduced relative humidity passes through the desiccant rotor 103 to remove the moisture in the desiccant rotor (state U). The regenerated air that has passed through the desiccant rotor 103 passes through the path 128 and the sensible heat exchanger 121.
Of the regenerated air that has flowed out of the sensible heat exchanger 104 before being regenerated and the temperature of the regenerated air itself has dropped (state V), and is then discharged to the outside via the path 129 as exhaust gas.

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

The coefficient of operation (COP) indicating the energy efficiency of the desiccant air-conditioning thus constructed is shown by the value obtained by dividing the cooling effect ΔQ in FIG. 4 by the amount of regenerated heat, and it is added to the regenerated air by the hot water heat exchanger. The amount of heat corresponding to the amount of heat Δq cooled by the cold water heat exchanger out of the obtained amount of heat ΔH is pumped up from the treated air through the cold water heat exchanger 115 and the evaporator 13 of the second cycle by the heat pump action of the absorption heat pump. Therefore, the amount of heat actually applied to this system is Δh obtained by subtracting Δq from ΔH, which corresponds to a sensible heat change from state X to state T in the figure.

Therefore, the operation coefficient is ΔQ / (ΔH-Δq)
= ΔQ / Δh. Comparing the coefficient of operation of FIG. 4 with the coefficient of operation of the conventional example of FIG. 6, in the embodiment of the present invention, the refrigerating effect ΔQ of the numerator is increased by Δq compared to the conventional example, and the heating amount of the denominator is compared to the conventional example. By .DELTA.q, and thus the denominator is decreased and the numerator is increased, so that the coefficient of performance is significantly improved. The coefficient of operation of the absorption heat pump of the present invention is roughly calculated below. The coefficient of operation for the refrigeration effect of the absorption heat pump is set to about 0.6, which is the same level as the conventional single-effect absorption refrigerator.
Assuming that the coefficient of operation of the conventional desiccant air conditioning is 1.0, in the embodiment of the present invention, if the amount of heat that is externally heated to the absorption heat pump is taken as 1, the amount of heat of 1.6 is added to the hot water due to the heat pump action. When the desiccant air conditioning is operated by this heat, the cooling effect is 1.0 (coefficient of operation) x 1.
6 (heating amount) +0.6 (freezing effect: Δq) = 2.2. Therefore, the coefficient of operation of the present invention is 2.2 (cooling effect) /1.0 (heat input to absorption heat pump) = 2.2.
Becomes This value is 1. with the conventional double-effect absorption refrigerator.
This is much higher than the coefficient of operation of about 2 and has an extremely high energy saving effect.

[0033]

As described above, according to the present invention, the heat of the treated air of the desiccant air conditioner can be pumped up by the heat pump action of the absorption heat pump and used for heating the regenerated air. The amount of heat that needs to be added is greatly reduced, and the coefficient of operation can be significantly improved. Therefore, according to the present invention, the consumption of heat source energy for cooling can be reduced, and it is possible to provide a desiccant air conditioner having excellent economical efficiency.
It is possible to provide an air conditioning system that exceeds the coefficient of operation of an air conditioning system that cools and dehumidifies air using the conventional dual-effect absorption refrigerator, that is, the energy efficiency.

[Brief description of drawings]

FIG. 1 is an explanatory diagram showing the basic configuration of an embodiment of an absorption heat pump according to the present invention.

FIG. 2 is an explanatory diagram showing the absorption solution cycle of one embodiment of the absorption heat pump according to the present invention in a Duhring diagram.

FIG. 3 is an explanatory diagram showing a basic configuration of an embodiment in which the absorption heat pump according to the present invention is used as a heat source device for desiccant air conditioning.

FIG. 4 is an explanatory view showing a desiccant air conditioning cycle of air, which is an embodiment using the absorption heat pump according to the present invention as a heat source device for desiccant air conditioning, in a moist air diagram.

FIG. 5 is an explanatory diagram showing a basic configuration of a conventional desiccant air conditioning.

FIG. 6 is an explanatory diagram showing a desiccant air conditioning cycle of air in a conventional desiccant air conditioning as a moist air diagram.

Claims (2)

(57) [Claims] 1. A first evaporator (3), a first absorber (1), a first regenerator (2) and a first condenser (4) for performing an absorption refrigeration cycle. 1 cycle device,
From the absorption refrigeration cycle of the first cycle device, which comprises a second evaporator (13), a second absorber (11), a second regenerator (12) and a second condenser (14) In an absorption heat pump including a second cycle device that performs an absorption refrigeration cycle that operates at a low temperature, a first heat exchanger that performs heat exchange between the first evaporator (3) and the second absorber (11). A heat exchange device (21) and a second heat exchange device (20) for exchanging heat between the first condenser (4) and the second regenerator (12) are provided, and the first heat exchanger (21) is provided. In order to make the absorption solution temperature of the first absorber (1) higher than the refrigerant condensation temperature of the second condenser (14) and the absorption heat of the first absorber (1) and the second condenser (14). A medium conveying means for extracting the heat of condensation to the outside is provided, and the medium conveying means is the second condenser (1
4) It is a path of a carrier medium for passing heat through the condenser heat transfer pipe (31) provided in the inside and the absorber heat transfer pipe (30) provided in the first absorber (1) in this order. An absorption heat pump characterized by. 2. The absorption heat pump according to claim 1, wherein the second evaporator (13) is provided with a heat transfer tube (33) for taking out heat of evaporation.