JP2971841B2 - Air conditioning system - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

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.

[0002]

2. Description of the Related Art FIG. 4 shows a conventional 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 desorbs and regenerates moisture in the desiccant by passing through the path A of the processing air in which moisture is adsorbed by the desiccant rotor 103 and passing through the desiccant rotor 103 after being heated by the heating source and adsorbing the moisture. An air conditioner having a regeneration air path B and having a sensible heat exchanger 104 between the treated air having adsorbed moisture and the regeneration air before regeneration of the desiccant rotor 103 and before being heated by the heating source; The first cycle which forms an absorption refrigeration cycle with the vessel 3, the absorber 1, the regenerator 2, and the condenser 4 as main constituent devices, and the evaporator 13, the absorber 11, the regenerator 12, and the condenser 14 are mainly used. As a constituent device, it comprises a second absorption refrigeration cycle that operates at a lower temperature than the first cycle, and has a heat exchange function between the evaporator 3 of the first cycle and the absorber 11 of the second cycle. 21 and an absorption heat pump forming a heat exchange relationship 20 between the condenser 4 of the first cycle and the regenerator 12 of the second cycle, the first cycle of the absorption heat pump. The regenerative air of the air conditioner is heated by the heater 120 to regenerate the desiccant 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, and the heat of evaporation of the second cycle of the absorption heat pump is used as the cooling heat source. This is an air conditioning system in which the cooler 115 cools the processing air of the air conditioner. In this air conditioning system, the absorption heat pump simultaneously cools the processing air of the desiccant air conditioner and heats the regeneration air, so that a high energy saving effect can be obtained.

[0003]

However, since the absorption heat pump serving as the heat source of the system has a refrigeration effect in the first cycle smaller than the absorption heat in the second cycle, it is necessary to operate the absorption heat pump smoothly. It was found that it was necessary to prevent the solution from being over-concentrated in the second cycle. The reason will be described below.

FIG. 5 is a During diagram showing an operation state of an absorption heat pump portion of a conventional desiccant air conditioning system.
Shown in FIG. 5 shows a typical example of a lithium bromide-water system generally used in an absorption refrigerator, and shows a first cycle and a second cycle separately. The alphabetic symbols shown in the figure indicate the states of the absorbing solution and the refrigerant, and the same symbols are circled in FIG.

In FIG. 5, the absorption solution in the first cycle is heated by an external heat source in a regenerator 2 to generate refrigerant vapor and to be concentrated (state c: 175 ° C. in the figure), and then the heat exchanger 5 is cooled. (State d). In the absorber 1, the absorbing solution absorbs the refrigerant evaporated in the evaporator 3, is diluted (state a), and is heated again through the heat exchanger 5 (state b).
Return to the regenerator 2. The refrigerant vapor generated in the regenerator 2 flows into the condenser 4 and condenses (state f). In the condenser 4, the heat of condensation generated during the condensation is transmitted to the regenerator 12 in 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 evaporates (state e). Evaporator 3
In the second embodiment, the heat of evaporation 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 supplied to the regenerator 12
Is heated through the heat transfer tube 20 by the heat of condensation (state f) of the first cycle, generates refrigerant vapor, is concentrated (state C), and then passes through the heat exchanger 15 (state D) to the absorber 11. Reach. In the absorber 11, the absorbing solution absorbs the refrigerant (state E) evaporated in the evaporator 13, is diluted (state A), is heated again through the heat exchanger 15 (state B), and returns to the regenerator 12. 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.
(State e). The refrigerant vapor generated in the regenerator 12 flows into the condenser 14 and condenses (state F). By flowing the heat medium from the condenser heat transfer tube 31 of the second cycle to the absorber heat transfer tube 30 of the first cycle, the absorption solution temperature (state a: 75 ° C. in the figure) of the first cycle becomes the second. Refrigerant condensation temperature of the second cycle (state F: 65 in the figure)
° C). The condensed refrigerant (state F) is sent to the evaporator 13 and evaporates (state E).

In the absorption heat pump thus configured, the driving heat is applied to the regenerator 2 in the first cycle, and the absorber 1 in the first cycle and the condenser 14 in the second cycle.
And the evaporator 1 in the second cycle
3. Use cold energy can be taken out. In this absorption heat pump, the cycles are independent of each other.
It is balanced so that no refrigerant or solution moves from one cycle to the other. However, the heat balance is not balanced, as explained below.

[0007] Now, the rate of refrigeration effect of the evaporator for the heat input of the regenerator of the first cycle to C _1. C ₁ is a so-called coefficient of operation (COP), which is a variable that can be set by design according to the circulation ratio of the solution, etc., and is approximately 0.8. The proportion of the evaporator of the refrigeration effect of the heat input of the regenerator of the second cycle and C ₂ as well. Also, values obtained by dividing the heat output of the condenser by the heat input of the evaporator are defined as R ₁ and R ₂ in each cycle. Since R ₁ and R ₂ have the same refrigerant flow rate, they have a value obtained by dividing the enthalpy change of the refrigerant in the condenser in each cycle by the enthalpy change of the refrigerant in the evaporator. Here, assuming that the heat input to the first cycle is 1,
The cooling effect Qe ₁ of this cycle is Qe ₁ = C ₁ (1).

On the other hand, in the second cycle, since the heat of condensation of the first cycle is added to the regenerator, the regenerator heat input Qg
₂ is Qg ₂ = C ₁ · R ₁ (2) The cooling effect Qe ₂ of the _second cycle is: Qe ₂ = C ₂ · Qg ₂ = C ₂ · C ₁ · R ₁ (3) The heat of condensation Qc ₂ is: Qc ₂ = R ₂ · Qe ₂ = C ₁ · C ₂ · R ₁ · R ₂ (4) The heat of absorption Qa ₂ in the second cycle is condensed from the total heat input in the second cycle Since the heat is subtracted, Qa ₂ = C ₁ · R ₁ + C ₂ · C ₁ · R ₁ -C ₁ · C ₂ · R ₁ · R ₂ (5)

In this absorption heat pump, the evaporator in the first cycle and the absorber in the second cycle exchange heat, so that
Here, the magnitude of the evaporation heat Qe ₁ in the first cycle and the magnitude of the absorption heat Qa _{2 in} the _second cycle will be compared. Therefore, taking the difference between them, Qa ₂ -Qe ₁ = C ₁ · R ₁ + C ₂ · C ₁ · R ₁ -C ₁ · C ₂ · R ₁ · R ₂ -C ₁ = C ₁ [(R _1- 1) -C ₂ · R ₁ (R ₂ -1)] (6) When R ₁ and R ₂ are calculated from the operation state of the cycle of FIG. 5, R ₁ = (675-95) / (609-95) = 1.128 as _{R 2 = (639-65) / (} 603-65) = 1.067 C 1 and C ₂ are approximately 0.8 (standard values of the single-effect absorption cycle), (6) of When the value is obtained, Qa ₂ −Qe ₁ = 0.8 (0.128−0.8 × 1.128 × 0.067) = 0.054> 0, and the heat of absorption in the second cycle is larger. You can see that. If the heat of evaporation Qe ₁ in the first cycle is larger than the heat of absorption Qa _{2 in} the second cycle, the expression (6) ≦
0, and therefore C ₂ ≧ (R ₁ -1) / (R ₂ -1) / R ₁ (7). When this C ₂ is calculated, C ₂ ≧ 0.128 / 0.067 / 1.128 = 1.694, which is a value that cannot be achieved as the COP of the single-effect absorption refrigeration cycle. That is, in this cycle, it is understood that the heat of absorption Qa2 of the _second cycle is always larger than the heat of evaporation Qe1 of the _first cycle.

Therefore, in the conventional heat source absorption heat pump shown in FIG. 4, since the refrigeration effect of the first cycle is small, the absorption heat of the second cycle cannot be completely cooled. Can not be absorbed by
Since the solution is gradually concentrated, there is a problem that continuous operation cannot be performed.

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.

[0012]

According to the first aspect of the present invention, there is provided a process air path through which moisture is adsorbed by a desiccant, and a desiccant passing through the desiccant after being heated by a heating source and passing through the desiccant after the moisture adsorption. An air conditioner having a path of regeneration air for desorbing and regenerating moisture, a first cycle constituting an absorption refrigeration cycle at least comprising an evaporator, an absorber, a regenerator, and a condenser, and at least an evaporator A second absorption refrigeration cycle which operates at a lower temperature than the first cycle, comprising an absorber, a regenerator, and a condenser as constituent devices, wherein the evaporator of the first cycle and the heat absorber of the second cycle And a heat exchange relationship between the first cycle condenser and the second cycle regenerator and evaporating from the first cycle condenser. Cold to the vessel An absorption heat pump provided with a heat exchanger that cools a refrigerant during cooling, wherein the absorption heat of the first cycle and the condensation heat of the second cycle of the absorption heat pump are used as heating sources to cool the air conditioner. In the air conditioning system to be performed, the absorption heat pump is configured such that the regeneration air or a heating medium for heating the regeneration air is guided to a heat exchanger that cools the refrigerant provided during the refrigerant cooling of the first cycle of the absorption heat pump to exchange heat with the refrigerant. An air conditioning system characterized by the following.

[0013] 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 having a low temperature to the heat exchanger to exchange heat with the refrigerant. The effect of cooling the refrigerant increases, the rate at which the refrigerant self-evaporates and the refrigeration effect is impaired when flowing into the evaporator decreases, the refrigeration effect of the first cycle increases, and the concentration of the solution of the second cycle increases. In addition to prevention and high energy efficiency, the heat possessed by the refrigerant can be recovered and used for heating the desiccant regenerated air, so that the cooling effect of the system increases and high energy efficiency can be obtained.

According to a second aspect of the present invention, the regeneration air or a heating medium for heating the regeneration air is guided to a heat exchanger for cooling the refrigerant provided in the refrigerant path of the first cycle of the absorption heat pump, and the refrigerant and heat are conveyed. After the replacement, the regeneration air or
2. The air conditioning system according to claim 1, wherein a heating medium for heating the regeneration air is guided to the condenser in the second cycle and the absorber in the first cycle to heat the heating medium . 3.

As described above, the heating medium having the lowest temperature is guided to the heat exchanger for cooling the refrigerant provided in the first cycle of the absorption heat pump, and the heat exchanger exchanges heat with the refrigerant. The structure in which the refrigerant is guided to the condenser and the condenser for heating increases the effect of cooling the refrigerant, reduces the rate at which the refrigerant self-evaporates when flowing into the evaporator, and impairs the refrigeration effect. The freezing effect of
In addition to preventing the concentration of the solution in the cycle and achieving high energy efficiency, the heat retained in the refrigerant can be recovered and used for heating the desiccant regenerated air, thereby increasing the cooling effect of the system and achieving high energy efficiency. it can.

[0016]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS 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,
Among them, the part of the heat source absorption heat pump is the evaporator 3,
The first cycle which forms an absorption refrigeration cycle with the absorber 1, the regenerator 2, the condenser 4, and the heat exchanger 5 as main constituent devices, the evaporator 13, the absorber 11, the regenerator 12, and the condenser 1
4. A second absorption refrigeration cycle that operates at a lower temperature than the first cycle, with the heat exchanger 15 as a main component, and the evaporator 3 of the first cycle and the absorber of the second cycle 11 and a heat exchange relationship 20 between the condenser 4 of the first cycle and the regenerator 12 of the second cycle, and
A heat exchanger 40 for cooling the refrigerant is provided in the refrigerant path 8 from the condenser 4 to the evaporator 3 in the cycle of (1). Further, in this embodiment, a sensor 62 for detecting the refrigerant level of the evaporator in the second cycle, a valve 61, a path 64 for sending the refrigerant to the absorber, and a controller 63 are provided.
A means is provided for opening the valve 61 when the solution is over-concentrated by the signal of 2 and sending the refrigerant to the absorber 11 to dilute the solution.

On the other hand, the air conditioner is constructed as follows, 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 a path 107, the discharge port of the blower 102 is connected to the desiccant rotor 103 via a path 108, and the processing of the desiccant rotor 103 is performed. The outlet of the air is connected to the sensible heat exchanger 104, which is in a heat exchange relationship with the regeneration air, through the path 1.
09, the processing air outlet of the sensible heat exchanger 104 is connected to the chilled water heat exchanger 115 via the path 110, and the processing air outlet of the cooler 115 is connected via the humidifier 105 and the path 111. The outlet of the processing air of the humidifier 105 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 B connects the outside air to a suction port of a blower 130 for regeneration air via a path 124, and a discharge port of the blower 130 has a sensible heat exchanger 104 in heat exchange relation with the processing air. And the outlet of the regenerated air of the sensible heat exchanger 104 is connected to the low temperature side inlet of another sensible heat exchanger 121 via a path 125, and the low temperature side outlet of the sensible heat exchanger 121 is connected to a heater. 120 and via path 126,
The outlet of the regeneration air from the heater 120 is connected to the desiccant rotor 10.
3 is connected to the regeneration air inlet of the sensible heat exchanger 12 via the path 127 and the exit of the regeneration air of the desiccant rotor 103 is connected to the sensible heat exchanger 12.
1 is connected to the high-temperature side inlet via a path 128, and the high-temperature side outlet of the sensible heat exchanger 121 is connected to an external space via a path 129 to take in regeneration air from the outside and exhaust it to the outside. Has formed.

The path of the heat transfer medium (hot water) for transferring heat between the absorption heat pump section and the air conditioner section passes through the heater 120 in the regeneration air path of the air conditioner after the hot water exits the path 123. , The pump 150, the path 51, the refrigerant cooling heat exchanger 40, the condenser 14, and the absorber 1, and return to the heater 120 in this order. Further, after the cold water exits the cooler 115 in the processing air path of the air conditioner, the path 118 and the pump 160 pass through the path of the heat transfer medium (cold water) for transferring cold heat between the absorption heat pump section and the air conditioner section. , The evaporator 13 and the path 117 to return to the cooler 115 in this order. In the drawing, circled alphabets K to V are symbols indicating the state of air corresponding to FIG. 3, where SA is air supply, RA is return air, and OA.
Represents outside air, and EX represents 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. The absorption solution of the first cycle is heated by a regenerator 2 from an external heat source (not shown) via a heat transfer tube 34 to generate a refrigerant vapor, and after being concentrated, the heat exchanger 5
Through the absorber 1. In the absorber 1, the absorption solution absorbs the refrigerant evaporated in the evaporator 3, and after being diluted, returns to the regenerator 2 through 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 condenses. 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.
Is transmitted to 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 absorbing solution of the second cycle is heated by the regenerator 12 by the heat of condensation of the first cycle via the heat transfer tube 20 to generate refrigerant vapor, and after being concentrated, passes through the heat exchanger 15 and passes through the absorber. It reaches 11. In the absorber 11, the absorbing solution absorbs the refrigerant evaporated in the evaporator 13, and after being diluted, the pump 1
6 returns to the regenerator 12 via the heat exchanger 15 again. 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. The refrigerant vapor generated in the regenerator 12 flows into the condenser 14 and condenses. In the condenser 14, heat is exchanged between the heat medium and the heat transfer tube 31 in order to utilize the heat of condensation generated during the condensation. Further, the heat medium flows in the order of the refrigerant cooling heat exchanger 40 of the first cycle, the condenser heat transfer tube 31 of the second cycle, and the absorber heat transfer tube 30 of the first cycle, so that the heat transfer of the first cycle is performed. The absorption solution temperature, the refrigerant condensation temperature of the second cycle, and the refrigerant temperature at the evaporator inlet of the first cycle increase in this order, and the refrigerant temperature at the evaporator inlet of 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 by a 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. 2 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-water system generally used in an absorption refrigerator. The alphabetic symbols shown in the figure indicate the states of the absorbing solution and the refrigerant, and the same symbols are circled in FIG.

The absorption solution in the first cycle is heated from an external heat source in the regenerator 2 to generate and vaporize refrigerant vapor (state c: 175 ° C. in the figure), and then passes through the heat exchanger 5 (state d). ) It leads to the absorber 1. In the absorber 1, the absorbing solution absorbs the refrigerant evaporated in the evaporator 3, is diluted (state a), and is heated again through the heat exchanger 5 (state b).
Return to The refrigerant vapor generated in the regenerator 2 flows into the condenser 4 and condenses (state f). In the condenser 4, the heat of condensation generated during the condensation is transmitted 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 cooling heat exchanger 40 (state g), and then sent to the evaporator 3 to evaporate (state e). In the evaporator 3, the evaporation 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 absorbing solution of the second cycle is heated by the regenerator 12 with the heat of condensation of the first cycle (state f) through the heat transfer tube 20, generates refrigerant vapor, and is concentrated (state C).
After that, it reaches the absorber 11 via the heat exchanger 15 (state D).
In the absorber 11, the absorbing solution absorbs the refrigerant (state E) evaporated in the evaporator 13, is diluted (state A), is heated again through the heat exchanger 15 (state B), and returns to the regenerator 12.
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 condenses (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 refrigerant cooling heat exchanger 40 of the first cycle, the condenser heat transfer tube 31 of the second cycle, and the absorber heat transfer tube 30 of the first cycle,
Absorption solution temperature of the first cycle (state a: 75 in the figure)
° C), the refrigerant condensing temperature of the second cycle (state F: 65 ° C in the figure), and the refrigerant temperature at the evaporator inlet of the first cycle (state g: 55 ° C in the figure). In the cycle (1), the refrigerant temperature at the evaporator inlet is the lowest.

As described above, since the refrigerant temperature at the inlet of the evaporator in the first cycle of the absorption heat pump is minimized, the refrigeration effect in the first cycle is increased.
The ability to cool the heat of absorption of the second cycle is increased, thereby mitigating the tendency of the solution of the second cycle to concentrate. The reason will be described below.

In order to find the difference between the heat of absorption in the second cycle and the heat of evaporation in the first cycle, as shown in the above equation (6), R ₁ and R ₂ were calculated for the operation state of the cycle of FIG. Then, by the action of the evaporator inlet enthalpy heat exchanger 40 for R _1, lowers therefore increases the refrigeration effect to 55 ° C., thus R ₁ is small. That is, R ₁ = (675-95) / (609-55) = 1.047 R ₂ = (639-65) / (603-65) = 1.067 C ₁ and C ₂ are the same as in the above conventional example. Assuming that the value of the above equation (6) is approximately 0.8 (a standard value of a single-effect absorption cycle), Qa ₂ −Qe ₁ = C ₁ [(R ₁ −1) −C ₂ · R ₁ ( R ₂ -1)] = 0.8 (0.047−0.8 × 1.047 × 0.067) = − 0.007 <0, and the heat of absorption in the second cycle is slightly smaller. It turns out that it becomes small. In addition, this difference is only a small difference of only 0.9% from 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. The heats of evaporation are almost equal.

In this case, the heat of evaporation Q in the first cycle
When a condition for e ₁ to be larger than the heat of absorption Qa ₂ in the second cycle, that is, a condition satisfying the expression (6) ≦ 0 is obtained, C ₂ ≧ (R ₁ −1) / (R ₂ −1) / R = 10.047 /
0.067 / 1.047 = 0.67, which is a sufficiently achievable COP for the single-effect absorption refrigeration cycle. That is, in this cycle, it can be seen that the heat of absorption Qa2 of the _second cycle and the heat of evaporation Qe1 of the _first cycle can be made substantially equal.

Accordingly, in the heat source absorption heat pump of the embodiment shown in FIG. 1, the absorption heat of the second cycle can be cooled by the refrigerating effect of the first cycle, so that the refrigerant can be absorbed by the absorber in the second cycle. As a result, since the solution does not concentrate, continuous operation becomes possible. Further, as the amount of refrigerant absorbed in the second cycle increases, the evaporator 13
The refrigeration effect 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 (process air) in the room 101 to be air conditioned is sent to the blower 102 through the path 107. The air is sucked, pressurized, sent to the desiccant rotor 103 via the path 108, and the moisture in the air is adsorbed by the desiccant rotor's moisture absorbent, whereby the absolute humidity decreases. At the time of 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 a cooler 115 via a path 110 and further cooled.
The cooled processing air is sent to the humidifier 105, and its temperature is lowered in the isenthalpy process by water injection or vaporization humidification, and is returned to the air-conditioned space 101 via the path 112.

Since the desiccant rotor adsorbs moisture in this process, regeneration is required. In this embodiment, the desiccant rotor is operated as follows using outside air as regeneration air. The outside air (OA) is sucked into the blower 130 via the path 124 and is boosted and sent to the sensible heat exchanger 104, where it cools the processing air to increase its temperature, and passes through the path 125 to the next sensible heat exchanger 121. And heat exchange with hot air after regeneration to increase the temperature. Further, the regenerated air exiting from the sensible heat exchanger 121 passes through path 1
After flowing into the heater 120 through the heater 26, it is heated by the hot water, the temperature rises to 60 to 80 ° C., and the relative humidity decreases. This process is a change in the sensible heat of the regenerated air.Since the specific heat of the air is significantly lower than that of the hot water and the temperature change is large, even if the flow rate of the hot water is reduced and the temperature change is increased, the heat exchange is performed efficiently, The transfer power can be reduced. Heater 12
The regeneration air having a relative humidity lowered after exiting 0 passes through the desiccant rotor 103 to remove moisture from the desiccant rotor and perform a regeneration operation. The regenerated air that has passed through the desiccant rotor 103 flows into the sensible heat exchanger 121 via a path 128,
After preheating the regeneration air before regeneration, it is discarded as exhaust gas through a path 129 to the outside.

The process up to now will be described with reference to the psychrometric chart of FIG. 3. The air in the room 101 to be air-conditioned (process air: state K) is sucked into the blower 102 via the path 107, and the pressure is increased to the path 108. Through the desiccant rotor 103
The moisture in the air is adsorbed by the desiccant rotor 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 decreased and its temperature has increased is sent to the sensible heat exchanger 104 via the path 109 and exchanges heat with outside air (regenerated air) to be cooled (state M). The cooled air is sent to a cooler 115 via a path 110 and is further cooled (state N).
The water is sent to the humidifier 105 through 1 and the temperature is lowered in the isenthalpy process by water injection or vaporization humidification (state P), and is returned to the air-conditioned space 101 via the path 112. In this way, an enthalpy difference ΔQ is generated between the return air (state K) and the supply air (state P) in the room.
As described above, in the embodiment of FIG. 1, the enthalpy of the refrigerant at the evaporator inlet of the heat pump decreases and the refrigerating effect of the heat pump increases, so that the enthalpy difference Δq is smaller than that of the embodiment of FIG. Therefore, the enthalpy difference ΔQ indicating the cooling effect also increases.

On the other hand, the desiccant is reproduced as follows. The outside air for regeneration (OA: state Q) is sucked into the blower 130 through the path 124 and is boosted, and the sensible heat exchanger 10
4 and cools the processing air to increase the temperature itself (state: R), flows into the next sensible heat exchanger 121 via a path 125, and exchanges heat with the high-temperature air after regeneration to increase the temperature. (State S). Further, 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 (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 regeneration air that has passed through the desiccant rotor 103 flows into the sensible heat exchanger 121 via the path 128, and performs preheating of the regeneration air before regeneration that has exited the sensible heat exchanger 104, thereby lowering its temperature (state V). ) After the route 12
After passing through 9, it is discarded outside as exhaust gas.

The desiccant is air-conditioned by repeating the desiccant regeneration and the dehumidification and cooling of the processing 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. In addition, the sensible heat exchanger 10
The air that has cooled the processing air in step 4 is not used for regeneration but is once exhausted, and fresh air is used as regeneration air as the sensible heat exchanger 121.
It is possible to use a method that leads to

As described above, 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 cooling the refrigerant, the refrigerant is cooled.
The rate of loss of the refrigeration effect due to self-evaporation when flowing into the system is reduced, and a large refrigeration effect is obtained. As a result, the cooling effect of the system increases, and the heat of absorption in the first cycle and the heat of condensation in the second cycle In addition, the sensible heat of the condensed refrigerant of the first cycle, which has conventionally been lost due to self-evaporation, can be recovered and used as a heating source for heating the regenerated air. Therefore, the energy efficiency of the entire air conditioning system is improved as the cooling capacity increases.

In this embodiment, during the second cycle of the heat source absorption heat pump, the sensor 62 for detecting the refrigerant level of the evaporator, the valve 61, and the path 64 for sending the refrigerant to the absorber are provided.
And a controller 63, which is provided with means for opening the valve 61 when the solution is over-concentrated by the signal of the sensor 62 and sending the refrigerant to the absorber 11 to dilute the solution.
This is because the cooling effect of the heat exchanger 40 is not obtained when the load is lost and the temperature of the heat transfer medium (hot water) rises when the air conditioning system is partially loaded.
Since it is assumed that the refrigerating effect of the second cycle is reduced and the absorbed heat of the second cycle cannot be cooled as described above, it is provided as a safety device in such a case. An increase in concentration can be prevented.

This type of means is a well-known technique in a conventional absorption refrigerator, and similar means may be used to measure the refrigerant temperature, pressure and solution temperature and to calculate and dilute it with a microcomputer or the like. Absent. 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 of the first cycle is reduced by the absorption heat of the second cycle. Therefore, it is possible that the evaporation pressure in the first cycle decreases and the solution concentration in the second cycle becomes too low, so that a means for diluting such a solution is also provided in the first cycle. It may be provided to reduce the refrigeration effect.

[0038]

As described above, according to the present invention, at least a first cycle which forms an absorption refrigeration cycle using at least an evaporator, an absorber, a regenerator, and a condenser as components, and at least an evaporator and an absorber A second absorption refrigeration cycle that operates at a lower temperature than the first cycle, using a regenerator and a condenser as constituent devices, and includes a second absorption refrigeration cycle between the first cycle evaporator and the second cycle absorber. And a heat exchange relationship between the first cycle condenser and the second cycle regenerator, and from the first cycle condenser to the evaporator. The refrigerant is cooled in the refrigerant path from the condenser of the first cycle to the evaporator in the first cycle of the heat source absorption heat pump of the air conditioning system in which the desiccant air conditioner is combined with the absorption heat pump having the heat exchanger for cooling the refrigerant in the refrigerant path. Heat exchange The configuration in which the heating medium of the regeneration air in the lowest temperature state is guided to the cooler to cool it, and when the refrigerant flows into the evaporator, the rate at which the refrigeration effect is impaired due to self-evaporation is reduced. Cycle can be made substantially equal to the second heat of absorption,
Therefore, concentration of the solution in the second cycle is prevented,
The smooth operation of the absorption heat pump becomes possible,
Since the retained heat of the refrigerant, which has been conventionally lost, can be recovered and used for heating the desiccant regeneration air, the cooling effect of the entire system is increased, and high energy efficiency can be obtained.

[Brief description of the drawings]

FIG. 1 is an illustration showing a basic configuration of an embodiment of an air conditioning system using a desiccant according to the present invention.

FIG. 2 is an explanatory diagram showing, in a During diagram, an absorption solution cycle of a portion of the absorption heat pump of FIG.

FIG. 3 is an explanatory diagram showing a desiccant air-conditioning cycle of air of the air-conditioning system of FIG. 1 in a psychrometric chart.

FIG. 4 is an explanatory diagram showing a basic configuration of a conventional desiccant air conditioning system.

5 is an explanatory diagram showing a desiccant air-conditioning cycle of air of the air-conditioning system of FIG. 4 in a psychrometric chart.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 1st absorber 2 1st regenerator 3 1st evaporator 4 1st condenser 5 1st heat exchanger 6 Solution pump 7 Throttle mechanism 11 2nd absorber 12 2nd regenerator 13 Second evaporator 14 Second condenser 15 Second heat exchanger 16 Solution pump 17 Throttle mechanism 20 Heat transfer tube (heat exchange mechanism) 21 Heat transfer tube (heat exchange mechanism) 30 Heat transfer tube (heat exchange mechanism) 31 Transfer Heat tube (heat exchange mechanism) 33 Heat transfer tube (heat exchange mechanism) 34 Heat transfer tube (heat exchange mechanism) 53 Heat medium (hot water) path 61 Valve 62 Sensor 63 Controller 64 Refrigerant path 101 Air conditioning space 102 Blower 103 Desiccant rotor 104 Sensible heat Exchanger 105 humidifier 106 water supply pipe 107 air path 108 air path 109 air path 110 air path 111 air path 115 chilled water heat exchanger 117 chilled water path 118 chilled water Road 119 Air path 120 Hot water heat exchanger 121 Sensible heat heat exchanger 122 Hot water path 123 Hot 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 ΔQ Cooling effect Δq Refrigeration effect of absorption heat pump ΔH Heating amount by hot water

Claims (2)

(57) [Claims] 1. A process air path through which moisture is adsorbed by a desiccant, and a regeneration air path through which heat is applied by a heating source, passes through the desiccant after adsorbing the moisture, and desorbs and regenerates moisture in the desiccant. An air conditioner having, at least an evaporator, an absorber, a regenerator, a first cycle which forms an absorption refrigeration cycle with a condenser as a constituent device, and at least an evaporator, an absorber, a regenerator, and a condenser as a constituent device, 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 A heat exchanger for forming a heat exchange relationship between a first cycle condenser and a second cycle regenerator and cooling the refrigerant in a refrigerant path from the first cycle condenser to the evaporator. Established A heat recovery pump, wherein the heat absorption heat of the first cycle and the heat of condensation of the second cycle of the absorption heat pump is used as a heating source to heat the regeneration air of the air conditioner to regenerate the desiccant and to perform the regeneration of the absorption heat pump. An air conditioning system that cools the processing air of the air conditioner using the heat of evaporation of the second cycle as a cooling heat source, wherein the regeneration air is supplied to a heat exchanger that cools a refrigerant provided in a refrigerant path of a first cycle of the absorption heat pump. Alternatively, an air conditioning system, wherein a heating medium for heating the regeneration air is guided to exchange heat with a refrigerant. Wherein After the first regeneration the refrigerant provided in the refrigerant passage in the heat exchanger for cooling air or direct the heating medium for heating the regeneration air exchanges heat with the refrigerant cycle of the absorption heat pump, the Heat regeneration air or regeneration air
The air conditioning system according to claim 1, wherein a heating medium is guided to the condenser in the second cycle and the absorber in the first cycle to heat the medium .