WO2000053978A1 - Dehumidifier - Google Patents

Abstract

A dehumidifier which dehumidifies treated air supplied to an air conditioned space, comprising a moisture adsorbing device (103) formed so as to adsorb moisture from the treated air (A) and remove it with regenerated air (B), a condenser (220) formed so as to condense refrigerant and heat the regenerated air (B) fed to the moisture adsorbing device (103) using a resultant condensing heat, a restriction (270) which reduces the pressure of the refrigerant condensed by the condenser (220), an evaporator (210) which is formed so as to evaporate the refrigerant reduced in pressure by the restriction (270) in order to cool the treated air (A) using a resultant evaporating heat, and a sub cooler (280) installed in a refrigerating path between the condenser (220) and the restriction (270), wherein the refrigerant flowing through the sub cooler (280) is cooled by a cooling medium (C) having a temperature equal to or less than the atmospheric temperature.

Description

 l! Jj Description Dehumidifier Technical Field

 The present invention relates to a dehumidifying device t, and more particularly to a dehumidifying air conditioner for dehumidifying process air supplied to an air conditioning room. Background art

 As shown in Fig. 6, there has been a so-called desiccant air conditioning system using a heat pump as a heat source.

 In this air conditioning system, a compression heat pump HP using a compressor 260 is used as a heat pump.

This air-conditioning system passes through the path of treated air A to which moisture is adsorbed by the desiccant drawer 103 and the desiccant port 103 after being heated by the heating source and then adsorbing the moisture. It has a path for regenerated air B that desorbs and regenerates moisture in the desiccant, and before regenerating the desiccant (desiccant) in the treated air and desiccant towels with moisture adsorbed. An air conditioner having a sensible heat exchanger 104 between the regenerated air before being heated by the heating source and a compression heat pump HP, and a high heat source of the compression heat pump HP is used as a heating source. The regeneration air of the air conditioner is heated by a heater 220 to regenerate the desiccant, and the low heat source of the compression heat pump HP is used as a cooling heat source to cool the air processed by the air conditioner by the cooler 210. Cooling is performed. In this air conditioning system, the compression heat pump HP was configured to simultaneously cool the processing air of the desiccant air conditioner and heat the regeneration air. As a result, the driving heat applied from outside to the compression heat pump HP causes the compression heat pump HP to generate a cooling effect for the processing air, and the heat pumped from the processing air by the heat pump operation and the driving heat of the compression heat pump HP. Since the heat generated by summing the above can generate the decent force, multiple effects of the drive energy applied from the outside can be achieved and a great energy saving effect can be achieved. In addition, a heat exchanger 122 is provided between the raw air from the sensible heat exchanger 104 and the heater 220 and the regenerated air exiting the desiccant tower 103. The effect is enhanced.

 Here, the operation of the desiccant air conditioner shown in FIG. 6 will be described with reference to the psychrometric chart of FIG. In Fig. 7, the air condition is indicated by alphabets K to P and Q to X. This symbol corresponds to the letter circled in the width of the flow diagram in Figure 6.

In Fig. 7, the treated air (condition) from the air-conditioned space 101 is absorbed in moisture by the desiccant in the desiccant atmosphere 103, and the absolute humidity is reduced. As a result, the dry-bulb temperature rises to reach the state L, and furthermore, the sensible heat exchanger 104 cools the air while keeping the absolute humidity constant, turns into air in the state M, and enters the cooler 210. Here, the air is further cooled at a constant absolute humidity to become air in state N, and humidified by the humidifier 105 to lower the dry bulb temperature to become air in state P. Will be returned. On the other hand, the outside air in the state Q is sent to the sensible heat exchanger 104, where it cools the processing air to be heated to the state R, enters the heat exchanger 122, and is further heated. It is heated to the state S, and then heated by the heater 220 to the state T. By regenerating the desiccant at the desiccant outlet 103, the absolute humidity is high and the dry bulb temperature drops. In state U, the regenerative air is heated by the heat exchanger 1 2 1 to lower the dry-bulb temperature, and Exhausted EX.

Furthermore, referring to the Mollier diagram in Fig. 8, the Sakugawa of the compressed heat pump HP shown in Fig. 6 will be discussed. FIG. 8 is a Mollier diagram of the refrigerant HFC134a. Point a indicates the state of the refrigerant evaporated in the cooler 210 and is in a saturated gas state. The pressure is 0.41 MPa (4.2 kg / cm ² ), the temperature is 10 ° C, and the enamel ruby is 63.2.12 kJ / kg (14.88.83 kca 1 / kg). The state where this gas is sucked and compressed by the compressor 260 and the state at the discharge port of the compressor 260 are indicated by a point b. In this state, the pressure is 1.89 MPa (19.3 kg / cm ² ), the temperature is 78 ° C, and the state is a superheated gas. This refrigerant gas is cooled in the heater (condenser when viewed from the refrigerant side) 220, and reaches point c on the Mollier diagram. This point is in a saturated gas state, the pressure is 1.89 MPa (19.3 kg / cm ² ), and the temperature is 65 ° C. Under this pressure, it is further cooled and condensed, reaching point d. This point is a saturated liquid state, the pressure and temperature are the same as point c, the pressure is 1.89 MPa (19.3 kg / cm ² ), the temperature is 65 ° C, and the Is 514 85 kJ / kg (122.97 kcal / k). This refrigerant liquid is depressurized by the expansion valve 270, decompressed to a saturation pressure of 0.41 MPa (4.2 kg / cm ² ) at a temperature of 10 ° C, and cooled to a temperature of 10 ° C. A cooler (evaporator from the perspective of refrigerant) 210 as a mixture of water and gas, where heat is removed from the treated air and evaporated to become a saturated gas in the state of point a on the Mollier diagram. Then, it is sucked into the compressor 260 again, and the above cycle is repeated.

According to the conventional heat pump as described above, the enthalpy difference indicating the cooling effect of the refrigerant per unit weight is determined by the difference between the saturated gas line at the evaporation pressure of the refrigerant and the saturated liquid line at the condensation pressure. The difference from the evening ruby, that is, in the example of Fig. 8, 6 2 3 1 2-5 14.8 5 = 1 0 8 .27 kJ / kg (1 4 8.8 3-1 2 2.97 7 = 2 5.86 kcal / kg), which is not necessarily large, and the coefficient of performance C〇P of the compression heat pump HP is low. The desiccant air conditioner (dehumidifier IS) using Toppump HP also had to have low C 0 P. Disclosure of the invention

 Therefore, an object of the present invention is to provide a dehumidifier having a high film formation coefficient COP.

 In order to achieve the above object, the dehumidifying apparatus for treated air according to the invention of claim 1 is configured to adsorb moisture from the treated air A and desorb moisture by the regenerated air B as shown in FIG. And a condenser 220 configured to condense the refrigerant and heat the regeneration air B sent to the moisture adsorber 103 with the heat of condensation. A throttle 270 for reducing the pressure of the refrigerant condensed in 20; and an evaporator 21 configured to evaporate the refrigerant reduced in pressure in the throttle 270 and to cool the processing air A by the heat of evaporation. 0; a subcooler 280 provided in a refrigerant path between the condenser 220 and the throttle 270; the refrigerant flowing through the subcooler 280 is cooled by a cooling medium C having a temperature equal to or lower than the atmospheric temperature. It is characterized by being configured to cool.

 Typically, the cooling medium is the outside air, which is the air or the outside air, and the outside air may be used as it is, but it is preferable to spray the water, that is, to vaporize and humidify the water to lower the temperature. Further, as shown in FIG. 4, outside air as a cooling medium may be heated by a subcooler without being vaporized and humidified, and then used as regenerated air. More typically, it is configured to include a compressor 260 that compresses the refrigerant evaporated in the evaporator 210 and sends the compressed refrigerant to the condenser 220.

With this configuration, a subcooler is provided, so that the refrigerant is supercooled. ―

 5 In addition, since the subcooler uses a cooling medium whose temperature is lower than the atmospheric temperature, the COP of the heat pump and the COP of the dehumidifier become extremely high. Further, as described in claim 2, in this dehumidifier {S, the evaporator 210 is disposed downstream of the flow of the processing air A with respect to the moisture adsorber 103; In the path of the processing air between 103 and the evaporator 210, a heat exchanger 300 for cooling the processing air A by the cooling medium C at a temperature equal to or lower than the atmospheric temperature is provided. Is also good.

 With this configuration, since the heat exchanger for cooling the processing air with the cooling medium having a temperature equal to or lower than the atmospheric temperature is provided, the processing air before being cooled by the evaporator can be cooled in advance.

 Further, as described in claim 3, in the dehumidifying device according to claim 1 or 2, it is preferable that water is vaporized and mixed into the cooling medium C. At this time, the temperature of the cooling medium is further reduced because the water is vaporized and humidified by spraying the medium.

 Further, as described in claim 4, in the dehumidifier according to claim 1 or 2 (for example, as shown in FIG. 4), the regeneration air B is used as a cooling medium for cooling the refrigerant flowing through the subcooler 280. It may be configured to be used. At this time, the condenser 220 is preferably arranged downstream of the flow of the regeneration air B with respect to the subcooler 280.

 With this configuration, since the regeneration air B is used as a cooling medium for cooling the refrigerant flowing through the subcooler, the heat released by the subcooler can be used for regeneration of the moisture adsorption device. Also, since the subcooler is located on the upstream side of the condenser, the degree of supercooling of the refrigerant cooled by the subcooler can be increased.

Further, as described in claim 5, the dehumidifier according to claim 4 (and as shown, for example, in FIG. 4) provides the dehumidifier between the condenser 220 and the subcooler 280. A second heat exchanger 122 for exchanging heat between the regeneration air B and the regeneration air B after passing through the moisture adsorption device 103 may be provided in the path of the regeneration air.

 With this configuration, the regeneration air heated by the subcooler can be further heated by the second heat exchanger. In addition, since the subcooler flows the S raw air before being heated in the second heat exchanger, the supercooling of the refrigerant can be sufficiently performed. BRIEF DESCRIPTION OF THE FIGURES

 FIG. 1 is a flowchart of a dehumidifying air conditioner according to a first embodiment of the present invention.

 FIG. 2 is a psychrometric chart illustrating the operation of the dehumidifying air conditioner of FIG.

 FIG. 3 is a Mollier diagram of the heat pump according to the first embodiment. FIG. 4 is a flowchart of a dehumidifying air conditioner according to a second embodiment of the present invention.

 FIG. 5 is a psychrometric chart explaining the operation of the dehumidifying air conditioner of FIG. Figure 6 is a chart showing the mouth of a conventional dehumidifying air conditioner.

 FIG. 7 is a psychrometric chart explaining the operation of the conventional dehumidifying air conditioner shown in FIG.

 FIG. 8 is a Mollier diagram of a heat pump used in the conventional dehumidifying air conditioner shown in FIG.

 FIG. 9 is a perspective view showing an example of the structure of a decinator.

 FIG. 10 is a perspective view showing an example of a cross-flow heat exchanger. BEST MODE FOR CARRYING OUT THE INVENTION

Hereinafter, embodiments of the present invention will be described with reference to the drawings. In addition. In the drawings, the same or corresponding members are denoted by the same or similar reference numerals, and duplicate description is omitted.

 Referring to FIG. 1, the configuration of a dehumidifying air conditioner r (air conditioning system) according to one embodiment of the present invention will be described. In this air conditioning system, the desiccant (drying agent) lowers the humidity of the processing air and maintains the air-conditioned space 101 supplied with the processing air in a comfortable environment.

 In the figure, a blower 102 for circulating the processing air along the path of the processing air A from the air-conditioned space 101, a desiccant trowel 103 as a desiccant-filled moisture adsorption device, Sprayed to about the wet-bulb temperature of the atmosphere (as a cooling medium at a temperature lower than the atmospheric temperature of the present invention). Heat exchanger 300 for cooling treated air by outside air, refrigerant evaporator ( It is arranged in this order as a cooler (as viewed from the processing air) 210, and is configured to return to the air-conditioned space 101. The heat exchanger (process air cooler) 300 is shown as an orthogonal flow heat exchanger in the figure. The cross-flow type heat exchanger has a structure as specifically shown in FIG. This is the heat exchanger 1 2

It may be a one-way heat exchanger such as the one shown in FIG.

 In addition, heat is exchanged between the regenerated air before entering the blower 140 and the regenerated air after entering the desiccant outlet 103, which circulates the regenerated air along the path from the outdoor OA to the regenerated air B. Heat exchangers 12 1, refrigerant condensers (heaters as viewed from the regenerated air) 2 20, desiccant trolleys 10 3, heat exchangers 12 1 Is configured.

 A blower for circulating outside air as a cooling fluid (cooling medium) along the path from the outdoor O A to the outside air C as a cooling fluid, and a blower 1

A vaporizing humidifier 1 65 that heats the outside air to a temperature close to the wet-bulb temperature by spraying moisture to the outside air circulating at 60, a heat exchanger 300 is arranged in this order, ―

 8 And it is configured to exhaust air to the outside. The vaporizing humidifier 165 is made of a material that is hygroscopic and air-permeable, such as ceramic paper or non-woven fabric. May be configured.

 In addition, the flow of the outside air cooled by the humidifier 165 is branched before being sent to the heat exchanger 300, and a part of the flow is introduced into a subcooler 280, which will be described later. The exhaust is configured to be exhausted. On the other hand, a compressor 260, a refrigerant condenser 220, and a subcooler 28, which compress the refrigerant evaporated and gasified by the refrigerant evaporator 210 along the path of the refrigerant from the refrigerant evaporator 210. 0, throttles 270 are arranged in this order, and return to the refrigerant evaporator 210 again.

 As shown in Fig. 9, the desiccant drawer 103 is formed as a thick disk-shaped mouth that rotates around the rotation axis AX, and through which the air can pass. Desiccant is filled with a gap. For example, a large number of tubular drying elements 103a are bundled so that the central axis thereof is parallel to the rotation axis AX. The rotor 103 is configured to rotate in one direction around the rotation axis AX. Further, the flow path of the processing air A and the flow path of the regeneration air B include a plane including the rotation axis AX, and are provided with their ends close to the surface in the thickness direction of the desiccant port 103. The processing air A and the regeneration air B flow in parallel to the rotation axis AX and flow out. Thus, each of the drying elements 103a is arranged so as to alternately contact the processing air A and the regeneration air B as the mouth 103 rotates.

In such an apparatus, typically, the processing air A (indicated by a white arrow in the figure) and the regeneration air B (indicated by a black solid arrow in the figure) have a rotation axis AX In parallel with each other, each half of the circular desiccant tower 103 is configured to flow in a countercurrent manner.

 Since the heat exchanger 122 must pass a large amount of regeneration air, it has a structure similar to the desiccant rotor in Fig. 9 and is filled with heat storage material with a large heat capacity instead of the dry element. Use a rotating heat exchanger. In this case, the low-temperature regeneration air B 1 corresponds to the processing air A in FIG. 9, and the high-temperature regeneration air B 2 corresponds to the regeneration air B. Further, for example, a cross-flow type heat exchanger as shown in FIG. 10 may be used. At this time, the low-temperature regeneration air B1 corresponds to the processing air A, and the high-temperature regeneration air B2 corresponds to the cooling medium C.

 The operation ffl of the dehumidifying air conditioner according to the first embodiment will be described with reference to the psychrometric chart of FIG. 2 and the configuration as appropriate with reference to FIG. In FIG. 2, the state of air in each part is indicated by the alphabet symbols D to G, E, K to N, Q, R, T to V, and X. This symbol corresponds to the circled alphabet in the flow diagram of FIG.

First, the flow of the processing air A will be described. In FIG. 2, the processing air (state) from the air-conditioned space 101 is sucked in by the blower 102 through the processing air path 107, and the desiccant port 1103 is passed through the processing air path 108. Sent to. Here, the desiccant in the drying element 103a (Fig. 9) absorbs moisture and lowers the absolute humidity, and the heat of adsorption of the desiccant raises the dry bulb temperature to reach state L. This air is sent to the heat exchanger 300 through the processing air path 109, where it is cooled by the outside air cooled to a temperature lower than the atmospheric temperature in the evaporator humidifier 165 while keeping the absolute humidity constant. The air becomes state M, and enters the refrigerant evaporator (cooler as viewed from the processing air) 210 through path 110. Here, the air is further cooled at a constant absolute humidity and becomes state N air. This air is dried and cooled, with moderate humidity Is returned to the air-conditioned space 101 via the duct 111 as the processed air SA at an appropriate temperature.

Next, the flow of the regeneration air B will be described. In FIG. 2, regenerated air from outside 0 A (state Q) is sucked in by a blower 140 through a fresh air path 124 and sent to a heat exchanger 122 through a path 125. Here, heat exchange with the high-temperature regenerated air to be exhausted (air in state U described later) raises the dry-bulb temperature and turns into air in state R. This air is sent through a path 126 to a refrigerant condenser 220 (heater as viewed from the regenerative air), where it is condensed (eg, at 65 ° C) and heated to reduce the dry bulb temperature. This air is raised to become air in state T (for example, 60 ° C) _.c This air is sent to the desiccant tower 103 through the path 127, where the drying element 103a (Fig. 9) Desorbs moisture from the desiccant in it, that is, desorbs water and regenerates it, raising itself in absolute humidity and lowering the dry-bulb temperature due to the heat of desiccant water desorption to reach state U . This air is sent to heat exchanger 122 through route 128 and exchanges heat with the regeneration air (air in state Q) before being sent to desiccant trolley 103 as described above. However, the temperature of the air itself is reduced to state V, and the air is exhausted EX through the path 12 '. Next, the flow of the outside air C as a cooling medium at a temperature lower than the atmospheric temperature will be described. The outside air C (state Q) is sucked from the outdoor OA to the blower 160 through the path 1 、 1, absorbs the moisture with the evaporator humidifier 165, changes the iso-rubber and increases the absolute humidity. Reduce the dry bulb temperature to form state D air. State D is almost on the saturation line of the wet vapor diagram. This air is sent to the subcooler 280 through a route 172. The subcooler 280 is so named because it supercools the refrigerant liquid, but acts as a heater from the perspective of the cooling medium. Cooling medium C is a sub-cooler 280 As it is heated, it reaches point F.

 On the other hand, the path 1Ί2 of the cooling medium C to the subcooler 280 branches off on the way to the path 173, and the path 173 is connected to the heat exchanger 300. The cooling medium sent to the heat exchanger 300 exchanges heat with the heated processing air m (state) via the desiccant rotor 103 to be heated to the point E while keeping the humidity constant. The cooling medium C in this state joins the path 176 via the path 175. In FIG. 2, the cooling medium C at the points E and F is mixed and exhausted as the cooling medium at the point G.

 In the air conditioner as described above, as can be seen from the cycle on the air side shown in the psychrometric chart of FIG. 2, the amount of heat added to the regeneration air for regeneration of the desiccant of the device is ΔΗ, If the amount of heat pumped from the processing air is △ q and the driving energy of the compressor 260 is Ah, then AH = Aq + Ah. The cooling effect ΔQ obtained as a result of the regeneration with the heat quantity △ H increases as the temperature of the outside air (state Q) to be heat-exchanged with the treated air (state L) after the adsorption of moisture is lower. In other words, it becomes larger as A Q — in the figure becomes larger. Therefore, spraying water to the outside air as a cooling medium with a vaporizing humidifier 165 is useful for enhancing the cooling effect.

 Here, returning to FIG. 1, the configuration and operation of the heat pump HP1 will be described. In the figure, the refrigerant gas compressed by the refrigerant compressor 260 flows through the refrigerant gas pipe 201 connected to the discharge port of the compressor 260, and the condenser (regenerated air heater) 22 It is configured to be guided to 0. The temperature of the refrigerant gas compressed by the compressor 260 is increased by the heat of compression, and the heat heats the regenerated air. The refrigerant gas itself is deprived of heat and condenses.

The refrigerant outlet of the heater 220 is connected to the refrigerant inlet of the subcooler 280 by a refrigerant path 202, and the refrigerant outlet of the subcooler 280 is cooled. _

 The expansion valve 270 is connected to a refrigerant evaporator 210 via a refrigerant path 204, and is connected to an expansion valve 270 serving as a restrictor via a medium path 203. The subcooler has, for example, a seal-and-tube structure. Alternatively, a structure may be employed in which one tube having a fin attached to the outside where the cooling medium flows flows in a meandering manner.

 From the condenser 220 to the expansion valve 270, the condensing pressure is almost maintained, and the refrigerant liquid is supercooled by the humidified and cooled outside air C in the subcooler 280 under the condensing pressure. The supercooled refrigerant is then decompressed by the expansion valve 270 to the evaporation pressure in the evaporator 210.

 By cooling the processing air in the evaporator 210, the refrigerant that has obtained heat and evaporates and gasified is guided to the suction port of the refrigerant compressor 260, and the above cycle is repeated.

 The operation of the heat pump HP1 in the air conditioning system of FIG. 1 will be further described with reference to the Mollier diagram of FIG. FIG. 3 is a Mollier diagram when refrigerant HFC 134a is used. In this diagram, the horizontal axis is Enbi Ruby and the vertical axis is pressure. Here, the case of FIG. 3A will be described first. The Mollier diagram in FIG. 3B is a diagram illustrating, in another embodiment, the vicinity of a saturated liquid line having a point corresponding to the point d in the diagram in FIG. 3A. FIG. 3B will be described later.

In FIG. 3A, point a is the state of the refrigerant outlet of the refrigerant evaporator 210 in FIG. 1, and is in the state of a saturated gas. Evaporation pressure is 0.41MPa (4.2kg / cm2), temperature is 10. C and Enbi rubi are 6 23.12 kJ / kg (148.83 kcal / kg). The state where this gas is sucked by the compressor 260 and compressed to the condensing pressure is shown by a point b. In this state, the pressure is 1.89 MPa (19.3 kg / cm ² ), the temperature is about 78 ° C, In state.

This refrigerant gas is cooled in the refrigerant condenser 220, and reaches a point c on the Mollier diagram. Point c is a saturated gas state, the pressure is 1.89 MPa (19.3 kg / cm-) and the temperature is 65 ° C. Under this pressure, it is further cooled and condensed, reaching point d. This point is a saturated liquid state, the pressure and temperature are the same as point c, the pressure is 1.89 MPa (19.3 kg / cm ² ), and the temperature is 65. C, and Enbi rubi is 51.4.85 kJ / kg (12.2.97 kca1 / kg).

The refrigerant liquid in the state at the point d is supercooled by the subcooler 280 while maintaining the condensing pressure (ignoring the pressure loss due to the flow) and reaches the point e. At point e, the pressure is the condensing pressure of 1.89 MPa (19.3 kg / cm ² ), the temperature is 35 ° C, and the enzymatic ruby is 46.7.83 kJ / kg (1 1 1.74 kcal / kg). However, when the vaporizing humidifier 165 is provided as shown in Fig. 1, the temperature of the cooling medium C can be reduced to about 27 ° C even in the middle of summer, so the temperature at point e is 30 ° C. It can also be about.

The refrigerant liquid in this state is reduced in pressure by the expansion valve 270 to reach the point j. Point: i is, 0. 4 1 MP a (4. 2 kg / cm 2) pressure is evaporating pressure, temperature 1 0. C, and the envy ruby is 46.78.3 kJ / kg (ll. 74 kcal / kg).

 By cooling the processing air, the refrigerant liquid itself obtains heat and evaporates to reach point a, and repeats the above cycle.

As described above, the compression including the compressor 260, the refrigerant condenser (regeneration air heater) 220, the subcooler 280, the throttle 270, and the refrigerant evaporator (processing air cooler) 210 When a sub-cooler is not provided as a heat pump, the refrigerant in the state of point d in the refrigerant condenser 220 is cooled through a throttle. In order to return to the medium evaporator 210,...: The available Ruby difference in the medium evaporator 210 is 6 2 3.1 2-5 1 4.85 = 1 0 8.2 7 k J / kg (1 48.83-1 22.97 = 25.86 kcal / kg), whereas the heat pump HP1 with subcooler 280 is i 6 2 3. 1 2-4 6 7. 8 3 2 1 5 5.29 kJ / kg (1 4 8.83 3-1 1 1.74 = 3 7.09 kcal / kg) However, the amount of gas circulating through the compressor for the same cooling load, and consequently the required power, can be significantly reduced (by about 30%).

 In addition, the subcooler 280 cools the refrigerant liquid with outside air at or below the atmospheric temperature. In other words, it is not the outside air heated by the heat exchanger 122, nor the outside air heated by another heat exchanger, but rather the outside air that has been humidified and cooled by a vaporizing humidifier. The effect of increasing the difference in enthalpy that can be used in the refrigerant evaporator 210 is remarkably high.

 In the embodiment of FIG. 1, the outside air via the vaporizing humidifier 165 is used as the cooling medium, but the outside air may be directly introduced into the subcooler without passing through the vaporizing humidifier 165. In this case as well, the outside air hits the cooling medium at a temperature lower than the atmospheric temperature.

 In any case, a large amount of heat source existing in the natural world can be used as a cooling medium as a cold heat source, so that the energy saving effect is high.

Next, a dehumidifying air conditioner according to a second embodiment will be described with reference to FIG. Unlike the first embodiment, as the cooling medium for cooling the refrigerant liquid by the subcooler 280, regenerated air that does not pass through a vaporizing humidifier is used. That is, the subcooler 280 is inserted and arranged in the path of the regeneration air connecting the blower 140 and the heat exchanger 122. The regeneration air outlet of the blower 140 and the regeneration air inlet of the subcooler 280 are connected by the regeneration air path 125 A, and the subcooler 2 The regeneration air outlet of 80 and the heat exchanger 1 21: fresh air inlet are connected by the route 125B.

 Further, the refrigerant outlet of the condenser 220 and the refrigerant inlet of the subcooler 280 are connected to the refrigerant path I by a refrigerant path 202, and the refrigerant outlet of the subcooler 280 and the expansion valve 270 are connected to the refrigerant path 2 The connection is made at 03. Other basic configurations are the same as those of the embodiment of FIG.

 The operation of the dehumidifying air conditioner according to the second embodiment will be described with reference to the psychrometric chart of FIG. 5 and the configuration as appropriate with reference to FIG. However, the same parts as those in FIGS. 1 and 2 are omitted. Alphabet symbols indicate the state of air in each part, and these symbols correspond to FIGS. 4 and 5 in the same manner as in the first embodiment.

 First, the flow of the processing air A is basically the same as that of the first embodiment, and therefore the description is omitted.

 Regarding the regeneration air B, in FIG. 5, the regeneration air (state Q) from the outdoor O A is sent to the subcooler 280 through the path 125 A via the blower 140. Here, the regenerated air is the cooling medium (the same temperature as the atmospheric temperature) of the present invention having a temperature equal to or lower than the atmospheric temperature. Here, it is heated by the high-temperature refrigerant liquid from the condenser 220 to become the air in the state F, and is sent to the heat exchanger 122 through the path 125B. Here, heat exchange with the high-temperature regenerated air (air in state U) to be exhausted raises the dry-bulb temperature to become air in state I, and then exhausted through desiccant air, etc. Until this is done, it is the same as in the first embodiment.

The flow of the outside air C as a cooling medium at a temperature equal to or lower than the atmospheric temperature enters the state E via the heat exchanger 300 in the same manner as in the first embodiment, and is exhausted in this state. The Mollier diagram is similar in basic form to Figure 3. However, the temperature at the point e is slightly higher than in FIG. 3 because the outside air that does not pass through the vaporizing humidifier 165 is used for cooling the refrigerant liquid. However, since the regeneration air is heated before flowing into the heat exchanger 122, the temperature of the regeneration air can be raised, or the same situation as when the regeneration air is introduced into the desiccant room overnight. Then, the heat exchanger 122 can be configured more compactly than in the first embodiment.

 As described above, the subcooler 280 uses the outside air existing in a large amount in the natural world as the cooling heat source, and uses the outside air before being heated by another heat exchanger. Can be significantly increased.

 As described above, the case where the outside air or outside air cooled to near the wet-bulb temperature by evaporating moisture is used as the cooling medium at a temperature lower than the atmospheric temperature used in the subcooler 280 has been described. Cooling tower water may be used, or river water may be used. As described above, as a cooling medium having a temperature equal to or lower than the atmospheric temperature, a cooling medium that exists in a large amount in nature can be used.

In the embodiment shown in FIGS. 1 and 4 described above, a throttle (not shown) may be inserted and arranged in the refrigerant path 202 between the condenser 220 and the subcooler 280. The Mollier diagram in this case is as shown in Fig. 3B. That is, the pressure is reduced from the point d through the throttle, a part of the refrigerant liquid is flushed (vaporized), and flows into the subcooler 280 in a state of the point d ′ where the refrigerant liquid and the refrigerant gas are mixed. Enter. The cooled and flushed gas condenses again and reaches the point e 'on the saturated liquid line. From points e and, the pressure is reduced by a diaphragm 270 to point j. That is the same as in Figure 3A. In this embodiment, in the subcooler 280, since the refrigerant in the mixed state of liquid and gas is involved in heat exchange, Therefore, the heat transfer rate of the refrigerant increases because the flow velocity of the refrigerant increases and the heat transfer by condensation can be used.

 As described above, according to the present invention HJ], a dehumidifier having a sub-cooler allows the refrigerant to be supercooled and a large difference in the en-ubiquity per unit of refrigerant, thereby significantly improving the COP. Can be provided. Industrial applicability

 The present invention relates to a dehumidifier for dehumidifying processing air supplied to an air-conditioned space, and is applicable to a desiccant air-conditioning system using a heat pump as a heat source.

Claims

The scope of the claims 1. a moisture adsorber configured to adsorb moisture from the treated air and desorb moisture with the regenerated air;  A condenser configured to condense a refrigerant and heat the raw air sent to the moisture adsorber with the heat of condensation;  A restrictor for reducing the pressure of the refrigerant condensed in the condenser;  An evaporator configured to evaporate the refrigerant decompressed by the throttle, and to cool the processing air with the heat of evaporation;  A subcooler provided in a refrigerant path between the condenser and the throttle;  A refrigerant flowing through the subcooler is cooled by a cooling medium having a temperature equal to or lower than an atmospheric temperature;  Dehumidifier for processing air. 2. The evaporator is arranged downstream of the flow of the processing air with respect to the moisture adsorber;  The method according to claim 1, further comprising a heat exchanger that cools the processing air with a cooling medium having a temperature equal to or lower than the ambient temperature in a path of the processing air between the moisture adsorber and the evaporator. 2. The process air dehumidifier according to 1. 3. The process air dehumidifier according to claim 1 or 2, wherein water is vaporized and mixed into the cooling medium. WO GO / 53978 _ PCT / JP00 / 01391  1 9 4. configured to use regenerated air as a cooling medium for cooling a refrigerant flowing through the subcooler;  The condenser is arranged downstream of the flow of the regeneration air with respect to the subcooler. The dehumidification of the processing air according to claim 1 or 2, 5. In the path of the regeneration air between the condenser and the subcooler, a second heat exchanger for exchanging heat between the regeneration air and the regeneration air after passing through the moisture adsorption device is provided. The dehumidifying device for treated air according to claim 4, wherein