JPH09170840A - Absorption heat pump - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide an absorption heat pump which can obtain an air conditioning system with a high energy efficiency. SOLUTION: A first heat exchanger 21 is formed for heat exchange between a first evaporator 3 of a first cycle unit C1 and a second absorber 11 of a second cycle unit C2 and a second heat exchanger 20 is formed for heat exchange between a first condenser 4 of the first cycle unit C1 and a second regenerator 12 of the second cycle unit C2. A different medium is used for an absorption working medium of the first cycle unit C1 and a working medium of the second cycle unit C2.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a first cycle device having a first evaporator, a first absorber, a first regenerator and a first condenser to perform an absorption refrigeration cycle. And an absorption composed of a second cycle device having a second evaporator, a second absorber, a second regenerator and a second condenser and operating at a lower temperature than the first cycle device. Regarding heat pump.

[0002]

Desiccant air conditioning systems are known as described in US 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 embodiment of a known desiccant air conditioner thus improved, and FIG. 6 is a Mollier diagram showing the operating state of the air conditioner of the embodiment shown in FIG. In FIG. 5, reference numeral 101 is an air-conditioned space, 102 is a blower, 103 is a desiccant rotor, 104 is a sensible heat exchanger, 105 is a humidifier, 1
Reference numeral 06 is a water supply pipe of a humidifier, 107 to 111 are air passages of 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 129 are air passages for regenerated air. Further, in the figure, alphabets K to V enclosed by circles are symbols showing the state of air corresponding to FIG. 6, SA is supply air, RA is return air, OA is outside air, and EX is exhaust. .

The operation of this conventional 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 thereof 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 decreased and its temperature has increased is sent to the sensible heat exchanger 104 via the path 109 and cooled by exchanging heat with 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 absorbed water in this process, it needs to be regenerated, and in this conventional example, it is performed 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, 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. 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 Mollier diagram. In FIG. 6, the air in the room 101 to be conditioned (processed air: state K) passes through the path 107 and the blower 102.
Is sucked in and pressure-increased to be sent to the desiccant rotor 103 via the path 108, the moisture in the air is adsorbed by the desiccant rotor hygroscopic agent, the absolute humidity 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 having a reduced relative humidity passes through the desiccant rotor 103 to remove moisture from 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 has been performed by repeatedly performing the desiccant regeneration, the dehumidification and the cooling of the treated air.

The coefficient of operation (COP) showing the energy efficiency of the desiccant air-conditioning thus constructed is 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 operating temperature of the hot water for heating the regeneration air was lower than in the initial desiccant air conditioning, but the boiler used as the desiccant regeneration heat source, and Since high-quality energy (exergy) of heat quantity was used as heat quantity of less than 1 at a low temperature of less than 100 ° C., other heat-driven refrigerators (for example, double-effect absorption refrigerator) were used to remove air. There is a drawback that the coefficient of operation (COP) is lower than that of an air conditioning system that cools and dehumidifies.

[0009]

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. By providing an absorption heat pump or refrigerator that can be supplied as an air conditioner, it is possible to improve the energy efficiency of desiccant air conditioning and obtain an air conditioning system that exceeds the energy efficiency of air conditioning systems that cool and dehumidify air using conventional refrigerators. The purpose is to provide a heat pump.

[0010]

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. 1 cycle device, 2nd evaporator, 2nd absorber, 2nd regenerator, 2nd
An absorption heat pump comprising a second cycle device having a condenser of 1) and operating at a lower temperature than the first cycle device, the first evaporator of the first cycle device and the second cycle device of the second cycle device. Forming a first heat exchange device for exchanging heat with a second absorber, and of the first condenser of the first cycle device and the second regenerator of the second cycle device; A second heat exchange device for performing heat exchange is formed between them, and different media are used for the absorption working medium of the first cycle device and the absorption working medium of the second cycle device.

According to the present invention, the absorption working medium of the first cycle device does not generate crystals even at the temperature and vapor pressure at which the absorption working medium of the second cycle device generates crystals.

Further according to the present invention, the working medium of the first cycle device is an absorption working medium using a mixture of lithium bromide and zinc chloride as an absorbing solution and water as a refrigerant, and the working medium of the second cycle device. Is an absorption working medium using lithium bromide as an absorbing solution and water as a refrigerant.

The absorption heat pump in this specification includes a refrigerator. Thus, if the absorption heat pump of the present invention configured as described above is used as the heat source device instead of the boiler for desiccant air conditioning, the first regenerator of the first cycle device and the second recycle device of the second cycle device are used. The amount of heat corresponding to the amount of heat obtained by adding the heat of vaporization of the second cycle device to the amount of drive input heat added to the absorption solution between the outlet of the second absorber and the outlet of the second regenerator is the first cycle device. Used as the heat of condensation of the second cycle device and the heat of absorption of the second cycle device. The heat can be extracted 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, thus saving the primary energy required for desiccant regeneration. Rutotomoni,
It is possible to provide an absorption heat pump that can be used in a desiccant air conditioning system having an increased cooling effect and thus 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 embodying the present invention, which comprises a first evaporator 3, a first absorber 1, a first regenerator 2 and a first condenser 4. A first heat exchanger 5 for absorbing solution is provided, and a first refrigerating cycle for absorption is performed.
Of the cycle device C1, the second evaporator 13, the second absorber 11, the second regenerator 12, the second condenser 14, and the second heat exchanger 15 for the absorbing solution. The second cycle device C2 operates at a temperature lower than that of the first cycle device C1. A heat exchange device 21 is formed between the first evaporator 3 of the first cycle device C1 and the second absorber 11 of the second cycle device C2, and the heat exchange device 21 is formed between the first evaporator 3 of the first cycle device C1 and the second absorber 11 of the first cycle device C1. A heat exchange device 20 is formed between the first condenser 4 and the second regenerator 12 of the second cycle device C2. Also, even when the absorption working medium of the first cycle device C1 and the absorption working medium of the second cycle device C2 are different media, that is, the temperature and vapor pressure at which the absorption working medium of the second cycle device C2 generates crystals, The absorption working medium of the first cycle device C1 is a medium that does not generate crystals. For example, the working medium of the first cycle device C1 is preferably an absorbing working medium which uses a mixture of lithium bromide and zinc chloride as an absorption solution and water as a refrigerant, and the working medium of the second cycle device C2 absorbs lithium bromide. An absorption working medium having a solution and water as a refrigerant is preferable.

The absorption cycle of the absorption heat pump configured as described above will be described below. First cycle device C
The absorbing solution 1 is heated in the first regenerator 2 from an external heat source (not shown) by the heating medium via the heat transfer tube 34 to generate a refrigerant vapor and is concentrated, and then the first heat exchanger 5 To reach the first absorber 1. In the first absorber 1, the absorbing solution absorbs the refrigerant evaporated in the first evaporator 3, and after being diluted, the action of the pump 6 again causes the first heat exchanger 5 to reheat.
And returns to the first regenerator 2. Since the first absorber 1 uses the absorbed 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 first regenerator 2 flows into the first condenser 4 and is condensed. In the first condenser 4, the heat of condensation generated at the time of condensation is transferred to the second regenerator 12 of the second cycle device C2 by the heat transfer tube 20 having a heat exchange relationship, that is, the first heat exchange device. The condensed refrigerant is sent to the first evaporator 3 and evaporated. In the first evaporator 3, the evaporation heat absorbed during evaporation is transferred from the second absorber 11 of the second cycle device C2 by the heat transfer tube 21 having a heat exchange relationship, that is, the second heat exchange device. The heat transfer tube of the first condenser 4 may be directly installed in the second regenerator 12 of the second cycle device C2 as is done in a normal double-effect absorption refrigerator. The action of can be performed.

The absorption solution of the second cycle device C2 is the second
Is heated in the regenerator 12 by the heat of condensation of the first cycle device C1 via the heat transfer tube 20, generates refrigerant vapor, and is concentrated and then passed through the second heat exchanger 15 to the second absorber 11. Reach In the second absorber 11, the absorbing solution is transferred to the second evaporator 13
After being absorbed and diluted by the refrigerant, the pump 16 returns to the second regenerator 12 via the second heat exchanger 15 by the action of the pump 16. In the second absorber 11, the absorption heat generated at the time of absorption is transferred to the first evaporator 3 of the first cycle device C1 by the heat transfer tube 21 having a heat exchange relationship, that is, the second heat exchange device. The refrigerant vapor generated in the second regenerator 12 flows into the second condenser 14 and is condensed. Since the second condenser 14 uses 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 transferred from the condenser heat transfer pipe 31 of the second cycle device C2 to the first heat transfer pipe 31.
By flowing the absorber heat transfer tubes 30 of the second cycle device C1 in this order, the temperature of the absorbing solution of the first cycle device C1 becomes higher than the refrigerant condensation temperature of the second cycle device C2.
The condensed refrigerant is sent to the second evaporator 13 and evaporated. Since the second 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 second absorber 11 may be directly installed in the first evaporator 3 of the first cycle device C1, 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. The alphabetical symbols shown in the figure indicate the states of the absorbing solution and the refrigerant, and the same symbols are circled in FIG.
Also described in. The absorbing solution of the first cycle device C1 is heated by an external heat source in the first regenerator 2 to generate a refrigerant vapor and be concentrated (state c: 175 ° C. in the figure) and then the first regenerator 2.
Through the heat exchanger 5 (state d) to the first absorber 1.
In the first absorber 1, the absorbing solution absorbs the refrigerant evaporated in the first evaporator 3, is diluted (state a), and is heated again through the first heat exchanger 5 (state b). Return to regenerator 2. The refrigerant vapor generated in the first regenerator 2 flows into the first condenser 4 and is condensed (state f). In the first condenser 4, the heat transfer tube 20 in which the heat of condensation generated during condensation has a heat exchange relationship
That is, it is transferred to the second regenerator 12 of the second cycle device C2 by the first heat exchange device. The condensed refrigerant is sent to the first evaporator 3 and evaporated (state e). In the first evaporator 3, the heat of evaporation absorbed during evaporation is transferred from the second absorber 11 (state A) of the second cycle device C2 by the heat transfer tube 21 that has a heat exchange relationship, that is, the second heat exchange device. To be done.

In such a cycle, the concentration of the absorbing solution in the operating range of the first cycle device C1 operating at a high temperature is high, so that the temperature suddenly drops or the concentration rises for some reason, for example, during operation. If there is a situation where a power failure suddenly occurs in the heat pump and the operation of the heat pump is stopped, the temperature of the solution is lowered while the solution is still concentrated, and crystals are easily generated. Therefore, in the present invention, the working medium of the first cycle device C1 is used. At the temperature and vapor pressure at which the working medium that is less likely to produce crystals than the working medium of the second cycle device C2, that is, the absorption working medium of the second cycle device C2 generates crystals, is the absorption of the first cycle device C1. A working medium that does not generate crystals is used. As a specific example, the working medium of the first cycle device C1 is preferably an absorption working medium containing a mixture of lithium bromide and zinc chloride as an absorption solution and water as a refrigerant, and the working medium of the second cycle device C2 is preferable. Is preferably an absorption working medium containing lithium bromide as an absorbing solution and water as a refrigerant.

The mixture of lithium bromide and zinc chloride, which is the working medium of the first cycle device C1, does not form crystals in the normal temperature range at the concentration in the operating state shown in FIG.
Known literature (for example, "Frozen" No. 6 issued by the Japan Refrigeration Association)
8 No. 789, p. 722). Therefore, even if a sudden temperature drop or concentration increase occurs for some reason during operation, it is avoided that the working fluid becomes crystallized and the operation cannot be continued. Is formed. In the present invention, since the working media of the first cycle device C1 and the working media of the second cycle device C2 do not mix, different working media can be selected in this way. In addition to the present embodiment, as the working medium, it is also possible to use, as a working medium which hardly causes crystallization, for example, an ammonia / water system or N-methyl-2-pyrrolidone (NMP) /2.2.2 trifluoroethane (TFE) system. Absent.

The concentrated (state C) solution which has generated the refrigerant vapor in the second regenerator 12 reaches the second absorber 11 via the second heat exchanger 15 (state D). Second absorber 11
Then, the absorbing solution absorbs the refrigerant (state E) evaporated in the second evaporator 13, is diluted (state A), and is then heated again via the second heat exchanger 15 (state B) and second regeneration. Return to vessel 12. In the second absorber 11, the absorption heat generated during absorption is transferred to the first evaporator 3 (state e) of the first cycle device C1 by the heat transfer tube 21 having a heat exchange relationship, that is, the second heat exchange device. To be done. The refrigerant vapor generated in the second regenerator 12 flows into the second condenser 14 and is condensed (state F). By flowing the heat medium in the order from the condenser heat transfer tube 31 of the second cycle device C2 to the absorber heat transfer tube 30 of the first cycle device C1, the absorption solution temperature of the first cycle device C1 (state a: in the figure 75 ° C.) is higher than the refrigerant condensation temperature (state F: 65 ° C. in the figure) of the second cycle device C2. The condensed refrigerant (state F) is sent to the second evaporator 13 and evaporated (state E).

In the absorption heat pump thus constructed, the high temperature heat applied from the outside to the first regenerator 2 of the first cycle device C1 is utilized for the solution concentration of the first cycle device C1. Since the heat of the refrigerant vapor generated at that time can be reused for the solution concentration of the second cycle device C2, one heat input can efficiently perform the solution concentration that becomes the driving force of the refrigeration effect of the two refrigeration cycles. it can.
Further, the heat absorbed by the second cycle device C2 is used in the entire cycle system as the heat of vaporization of the first cycle device C1. Therefore, absorption heat can be used in the first cycle device C1, and condensation heat and evaporation heat can be used in the second cycle device C2.
As shown in Fig. 2, the heat generated in the process of absorption and condensation is 60
It can be taken out to the outside as warm water of 80 ° C to 80 ° C, and the heat of evaporation of the second cycle device C2 can be taken out to the outside as cold water of about 15 ° C. Looking at the heat balance of the entire cycle system, the heat input into the entire cycle system is the high temperature heat applied from the outside to the regenerator 2 of the first cycle device C1 and the cold water in the evaporator 13 of the second cycle device C2. The heat extracted from the entire cycle system is the heat absorbed by the first cycle device C1 and the heat of condensation of the second cycle device C2 added to the hot water. Therefore, in addition to the high-temperature heat applied from the outside to the regenerator of the first cycle device C1 to the hot water, the heat taken from the cold water by the evaporator of the second cycle device C2 is added, so that it can be used by the hot water. The amount of heat is greater than the amount of heat applied to the regenerator of the first cycle device C1 from the outside. Thus, the present invention has a heat pump function.

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 Mollier diagram showing the operating state of the air conditioning portion of the embodiment of FIG. In the embodiment of FIG. 3, the hot water pipe and the cold water pipe of the absorption heat pump of the embodiment of FIG. 1 are connected to a desiccant air conditioner shown below via a cold water pump 160 and a hot water pump 150, respectively.

The desiccant air conditioner shown in FIG. 3 is constructed as follows. The air-conditioned space 101 is a blower 1 for processing air
02 is connected to the suction port of the blower 102 via the path 107, and the discharge port of the blower 102 is connected to the desiccant rotor 103 and the path 108.
And the outlet of the process air of the desiccant rotor 103 has a sensible heat exchanger 104 in a heat exchange relationship with the regenerated air.
And the outlet of the treated air of the sensible heat exchanger 104 is connected to the cold water heat exchanger 115 via the passage 110, and the outlet of the treated air of the cold water heat exchanger 115 is connected to the humidifier 105. It connects through the path 119, and the outlet of the processing air of the humidifier 105 connects with the conditioned space 101 through the path 111 to form a cycle of the processing air.

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 first absorber 1 of the first cycle device C1 of the hot water path of the absorption heat pump, and the hot water of the hot water heat exchanger 120 is connected. The outlet is connected to the inlet of the second condenser 14 of the second cycle device C2 of the hot water path of the absorption heat pump via the path 123 and the hot water pump 150. Further, the cold water inlet of the cold water heat exchanger 115 is the path 11
7 is connected to the outlet of the second evaporator 13 of the second cycle device C2 of the cold water path of the absorption heat pump, and the cold water outlet of the cold water heat exchanger 115 is the path 118 and the pump 16
0 to the inlet of the second evaporator 13 of the second cycle device C2 in 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 the air corresponding to FIG. 4, and SA is the air supply and RA
Represents return air, OA represents outside air, and EX represents exhaust air.

The operation of this embodiment will be described with reference to FIG.
In the air-conditioned room 101, the air in the room 101 (process air) is sucked by the blower 102 via the path 107, is pressurized, and is sent to the desiccant rotor 103 via the path 108 to adsorb moisture in the air with 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. Further, the regenerated air exiting from the sensible heat exchanger 121 passes through path 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 that of the hot water and the temperature change is large. Therefore, even if the flow rate of the hot water is decreased to increase the temperature change, the heat exchange is efficiently performed. Done. Therefore, the second cycle device C2 corresponding to the hot water inflow side of the absorption heat pump for producing hot water
The condensation temperature of the first cycle device C1 corresponding to the outlet side is
Can be set lower than the absorption temperature of, and by doing so, the pressure and temperature of the first regenerator 2 of the first cycle device C1 can be lowered, so that The amount of heat applied to the first regenerator 2 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. The regenerated air that has passed through the dessicant rotor 103 flows into the sensible heat exchanger 121 via the path 128, and performs residual heat of the regenerated air before regeneration, and then the path 129.
And is discarded outside as exhaust gas.

The process up to this point will be described with reference to the Mollier 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 in and pressure-increased to be sent to the desiccant rotor 103 via the path 108, the moisture in the air is adsorbed by the desiccant rotor hygroscopic agent, the absolute humidity 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 is sent to the cold water heat exchanger 115 via the path 110 and further cooled (state N). The cooled air is sent to the humidifier 105 via the path 119, the temperature is lowered in the isenthalpic process by water injection or vaporization-type humidification (state P), and is returned to the air-conditioned space 101 via the path 111. In this way, an 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 for regeneration (OA: state Q) is sucked by the blower 130 via the path 124, is pressurized and is sent to the sensible heat exchanger 104, cools the process air and raises itself in temperature (state R).
It flows into the next sensible heat exchanger 121 via the path 125 and exchanges heat with the regenerated high temperature air to rise in 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 having a reduced relative humidity passes through the desiccant rotor 103 to remove moisture from the desiccant rotor (state U). The regenerated air that has passed through the dessicant rotor 103 flows into the sensible heat exchanger 121 via the path 128, and performs residual heat of the regenerated air that has left the sensible heat exchanger 104 before regeneration, and the temperature of the regenerated air decreases (state V). ) Route 12
After passing through 9, it is discarded outside as exhaust gas.

In this way, the desiccant is air-conditioned by repeating the desiccant regeneration and the 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 in the present invention. Similar effects can be obtained.

The coefficient of operation (COP) indicating the energy efficiency of the desiccant air-conditioning constructed as described above is shown by the value obtained by dividing the cooling effect ΔQ in FIG. 4 by the amount of regenerated heat, and is added to the regenerated air by the hot water heat exchanger. The amount of heat corresponding to the amount of heat Δq cooled in the cold water heat exchanger out of the obtained amount of heat ΔH is from the treated air to the cold water heat exchanger 115 and the second evaporator 1 of the second cycle device C2 by the heat pump action of the absorption heat pump.
Since it is pumped through 3, the amount of heat actually applied to this system is Δh, which is ΔH minus Δq, 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 desiccant air conditioning system using the absorption heat pump of the present invention will be roughly calculated below. Assuming that the coefficient of operation for the refrigerating effect of the absorption heat pump is approximately 0.6, which is equivalent to the coefficient of operation of the conventional single-effect absorption refrigerator, and the coefficient of operation of the conventional desiccant air conditioning is 1.0, in the embodiment of the present invention, When the amount of heat that is externally heated to the absorption heat pump is set to 1, a heat pump action adds a heat amount of 1.6 to the hot water, and when this heat is used to operate the desiccant air conditioning, the cooling effect is 1.0 (coefficient of operation ) × 1.6 (heating amount) +0.6 (freezing effect: Δq) =
The amount of heat is 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. This value greatly exceeds the coefficient of operation of about 1.2 that the conventional double-effect absorption refrigerator has, and has an extremely high energy saving effect.

[0036]

As described above, according to the present invention, the heat of the treated air in the desiccant air conditioning can be pumped up by the heat pump action of the absorption heat pump and used for heating the regenerated air. Therefore, the desiccant regeneration in the desiccant air conditioning is possible. Therefore, the amount of heat that needs to be applied from the outside is significantly reduced, and the coefficient of operation can be significantly improved, and as a heat source machine, crystals are generated in the working medium of the first cycle device more than in the second cycle device. Even if the working medium that is difficult to use, that is, the temperature and the vapor pressure at which the absorption working medium of the second cycle device generates crystals, the absorption working medium of the first cycle device uses the working medium that does not generate crystals, the operation is in progress. For some reason, sudden temperature drop,
It is possible to provide an absorption heat pump having a highly reliable operation cycle, which prevents the absorption working medium from being crystallized and making it impossible to continue the operation even if a situation in which the concentration increases occurs.

Therefore, according to the present invention, it is possible to provide a desiccant air-conditioning system that consumes less heat source energy for cooling and is excellent in economic efficiency. It is possible to provide an air-conditioning system that exceeds the coefficient of operation of the air-conditioning system that cools and dehumidifies the air-conditioning system, that is, energy efficiency, and to provide a highly reliable absorption heat pump.

[Brief description of the 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 view showing an absorption solution cycle device of an embodiment of an 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 diagram showing a Mollier diagram of an air desiccant air conditioning cycle device according to 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. 5 is an explanatory diagram showing a basic configuration of a conventional desiccant air conditioning.

FIG. 6 is an explanatory diagram showing, with a Mollier diagram, a conventional desiccant air-conditioning cycle device for air for desiccant air conditioning.

[Explanation of symbols]

 1 ... 1st absorber 2 ... 1st regenerator 3 ... 1st evaporator 4 ... 1st condenser 5 ... 1st heat exchanger 6 ... Solution pump 7 ... Throttling mechanism 11 ... Second absorber 12 ... Second regenerator 13 ... Second evaporator 14 ... Second condenser 15 ... Second Heat exchanger 16 ... Solution pump 17 ... Throttling mechanism 20 ... Heat transfer tube (first heat exchange device) 21 ... Heat transfer tube (second heat exchange device) 30 ... Heat transfer tube 31 ... Heat transfer tube 32 ... Heat medium (hot water) path 33 ... Heat transfer tube 34 ... Heat transfer tube 101 ... Air-conditioned space 102 ... Blower 103 ... Desiccant rotor 104 ... Microscope Heat-heat exchanger 105 ... Humidifier 106 ... Water supply pipe 107 ... Air path 108 ... Air path 109 ... Air path 110 ... Air path 111 ... Air path 115 ... Cold water heat exchanger 117 ... Cold water path 118 ... Cold water path 119 ... Air path 120 ... Hot water heat exchanger 121 ... Sensible heat exchange Container 122 ... Warm water path 123 ... Warm water path 124 ... Air path 125 ... Air path 126 ... Air path 127 ... Air path 128 ... Air path 129 ... Air path 130・ ・ ・ Blower 150 ・ ・ ・ Hot water pump 160 ・ ・ ・ Cold water pump a ・ ・ ・ State point of absorption refrigeration cycle b ・ ・ ・ State point of absorption refrigeration cycle c ・ ・ ・ State point of absorption refrigeration cycle d ・ ・ ・State point of absorption refrigeration cycle e ... State point of absorption refrigeration cycle f ... State point of absorption refrigeration cycle A ... State point of absorption refrigeration cycle B ... State point of absorption refrigeration cycle C ... State point of absorption refrigeration cycle D ... State point of absorption refrigeration cycle E ... State point of absorption refrigeration cycle F ... State point of absorption refrigeration cycle K ... State point of desiccant air conditioning L ...・ Air state point of desiccant air conditioning M ・ ・ ・ Air state point of desiccant air conditioning N ・ ・ ・ Air state point of desiccant air conditioning P ・ ・ ・ Air state point of desiccant air conditioning Q ・ ・ ・ Desicant air conditioning air State point R ... Desiccant air conditioning air state point S ... Desiccant air conditioning air state point T ... Desiccant air conditioning air state point U ... Desiccant air conditioning air state point V ... Air state point of desiccant air conditioning X ... Air state point of desiccant air conditioning SA ... Air supply RA ... Return air EX ... Exhaust air OA ... Outside air .DELTA.Q ... Cooling effect .DELTA.q ... Absorption heat pump Heating amount of anti-freeze effect ΔH ··· hot water Δh ··· ΔH over Δq

Claims (3)

[Claims] 1. A first cycle device having a first evaporator, a first absorber, a first regenerator and a first condenser for performing an absorption refrigeration cycle, and a second evaporation device. In an absorption heat pump comprising a second cycle device having a cooler, a second absorber, a second regenerator and a second condenser and operating at a temperature lower than that of the first cycle device, Forming a first heat exchanging device for exchanging heat between the first evaporator of the cycle device and the second absorber of the second cycle device, and Forming a second heat exchange device for exchanging heat between the condenser and the second regenerator of the second cycle device, and absorbing the working medium of the first cycle device and the absorption of the second cycle device; An absorption heat pump characterized in that different working media are used. 2. The absorption working medium of the first cycle device does not generate crystals even at a temperature and a vapor pressure at which the absorption working medium of the second cycle device generates crystals. The absorption heat pump according to item 1. 3. The working medium of the first cycle device is an absorption working medium using a mixture of lithium bromide and zinc chloride as an absorption solution and water as a refrigerant, and the working medium of the second cycle device is lithium bromide. The absorption heat pump according to claim 1, which is an absorption working medium that uses water as a refrigerant as the absorption solution.