JP2980603B1 - Dehumidifying air conditioner and dehumidifying method - Google Patents

Abstract

An object of the present invention is to provide a compact and dehumidifying air conditioner having a high COP. SOLUTION: The moisture adsorbing device 103 having a desiccant for adsorbing moisture in the processing air, and the moisture adsorbing device 103 is provided on the downstream side of the flow of the processing air with respect to the moisture adsorbing device 103, and the moisture is adsorbed by the desiccant. A processing air cooler 300 for cooling the processing air.
0 is a dehumidifying air conditioner, wherein the processing air is cooled by evaporation of a refrigerant, and the evaporated refrigerant is cooled and condensed by a cooling fluid. The processing air cooler is configured to cool the processing air by evaporating the refrigerant and cool the evaporated refrigerant with the cooling fluid to condense, so it uses the evaporation heat transfer and condensation heat transfer with a high heat transfer coefficient. Therefore, heat transfer between the processing air and the cooling fluid can be achieved with a high heat transfer coefficient. Further, since the heat transfer between the processing air and the cooling fluid is performed via the refrigerant, the components of the dehumidifying air conditioner can be easily arranged.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

The present invention relates to a dehumidifying air conditioner, and more particularly to a dehumidifying air conditioner using a desiccant.

[0002]

2. Description of the Related Art As shown in FIG. 12, there has conventionally been an air conditioning system in which a heat pump as a heat source is combined with a so-called desiccant air conditioner. In the air conditioning system of FIG. 12, a compression heat pump HP using a compressor 260 is used as a heat pump. This air conditioning system desorbs and regenerates moisture in the desiccant by passing through the path of the processing air A to 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. A sensible heat exchanger having a path for the regeneration air B, between the treated air to which moisture has been adsorbed and the regeneration air before regenerating the desiccant (desiccant) of the desiccant rotor 103 and before being heated by the heating source. An air conditioner having an air conditioner 104; and a compression heat pump HP. The regeneration air of the air conditioner is heated by a heater 220 using a high heat source of the compression heat pump HP as a heating source to regenerate the desiccant, and the compression heat pump HP The process air of the air conditioner is cooled by the cooler 210 using the low heat source as a cooling heat source.

In this air conditioning system, the compression heat pump HP is configured to simultaneously cool the processing air of the desiccant air conditioner and heat the regeneration air, so that the compression heat pump HP is driven by driving energy externally applied to the compression heat pump HP. Generates the cooling effect of the processing air, and furthermore, the desiccant can be regenerated by the heat obtained by adding the heat pumped from the processing air by the heat pump action and the driving energy of the compression heat pump HP. High energy saving effect can be obtained. In addition, the regeneration air between the sensible heat exchanger 104 and the heater 220 and the desiccant rotor 10
The heat exchanger 121 with the regenerated air exiting from No. 3 is provided to further enhance the energy saving effect.

The operation of the desiccant air conditioner shown in FIG. 12 will now be described with reference to a psychrometric chart shown in FIG.
In FIG. 13, alphabets K to P and Q to X indicate the state of air. This symbol corresponds to the alphabet circled in the flowchart of FIG.

[0005] In FIG. 13, the processing air (state K) from the air-conditioned space 101 is desiccant adsorbed by the desiccant rotor 103 to lower the absolute humidity, and the desiccant heat of adsorption raises the dry bulb temperature to the state L.
Then, in the sensible heat exchanger 104, the air is cooled in the state M while keeping the absolute humidity constant, and enters the cooler 210. Here, the air is further cooled at a constant absolute humidity to become air in the state N, and humidified by the humidifier 105 to lower the dry-bulb temperature to become air in the state P, and is returned to the air-conditioned space 101. 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 121, and is further heated to the state S. Then, the desiccant is heated by the heater 220 to reach the state T, and the desiccant is regenerated by the desiccant rotor 103. The desiccant itself has a high absolute humidity, the dry bulb temperature decreases, and the state becomes U, and the regenerated air is heated by the heat exchanger 121. As a result, the temperature of the dry bulb itself is lowered, and the air becomes the state V and is exhausted EX.

[0006] Here, referring to the Mollier diagram of FIG.
The operation of the compression heat pump HP shown in FIG.
You. FIG. 14 shows a Mollier diagram of the refrigerant HFC134a.
It is. Point a indicates the state of the refrigerant evaporated in the cooler 210.
And is in a saturated gas state. The pressure is 4.2kg / cm
^Two , Temperature is 10 ° C, enthalpy is 148.83 kcal
/ Kg. This gas was sucked and compressed by the compressor 260
The state at the discharge port of the compressor 260 is indicated by a point b.
I have. In this state, the pressure is 19.3 kg / cm^Two ,temperature
Is 78 ° C. and is in a superheated gas state. This refrigerant gas
Is a heater (cooler or condenser when viewed from the refrigerant side)
It is cooled in 220 and reaches point c on the Mollier diagram. this
The point is a saturated gas state, and the pressure is 19.3 kg / cm.
^Two , The temperature is 65 ° C. Is cooled further under this pressure
It condenses to point d. This point is the state of the saturated liquid,
The pressure and temperature are the same as at point c, and the pressure is 19.3 kg / cm
^Two , Temperature 65 ° C, and enthalpy 122.97k
cal / kg. This refrigerant liquid is reduced by the expansion valve 270.
4.2 kg / cm which is a saturation pressure of 10 ° C.
^Two As a mixture of refrigerant liquid and gas at 10 ° C
A cooler (evaporator from the viewpoint of refrigerant) 210 is reached, where
Removes heat from the processing air, evaporates and removes the point a on the Mollier diagram.
Becomes a saturated gas in a state, and is again sucked into the compressor 260,
The above cycle is repeated.

[0007]

According to the conventional air conditioning system described above, the sensible heat exchanger 104, which preliminarily cools the processing air before cooling it with the cooler 210, plays an important role. However, since the sensible heat exchanger generally occupies a large volume in the system, it has made the system configuration difficult and, as a result, the system has to be enlarged.

Therefore, an object of the present invention is to provide a compact and dehumidifying air conditioner having a high COP.

[0009]

Means for Solving the Problems In order to achieve the above object, a dehumidifying air conditioner according to the first aspect of the present invention is shown in FIG.
, A moisture adsorber 103 having a desiccant that adsorbs moisture in the processing air;
A processing air cooler 300 provided on the downstream side of the flow of the processing air with respect to the processing air 3 to cool the processing air to which moisture has been adsorbed by the desiccant; Is cooled by evaporation of the refrigerant, and the evaporated refrigerant flows in the processing air cooler 300 as a whole in one direction, and is cooled and condensed by the cooling fluid on the downstream side. Here, "to flow in one direction as a whole" means that even if the turbulent flow locally flows in the opposite direction, the gaseous refrigerant and the liquid phase refrigerant flow in the same direction as a whole.

[0010] With this configuration, the processing air cooler is provided, and the processing air cooler is configured to cool the processing air by evaporating the refrigerant, and to cool and condense the evaporated refrigerant by the cooling fluid. Therefore, the heat transfer between the processing air and the cooling fluid can be achieved with a high heat transfer coefficient because the evaporation heat transfer and the condensation heat transfer having a high heat transfer coefficient can be used. Further, since the refrigerant flows in one direction as a whole, the heat transfer coefficient is high. Also,
Since the heat transfer between the processing air and the cooling fluid is performed via the refrigerant,
The arrangement of the components of the dehumidifying air conditioner is facilitated.

In the above dehumidifying air conditioner, a refrigerant evaporator for evaporating the refrigerant condensed in the processing air cooler 300 and further cooling the processing air cooled in the processing air cooler 300 is provided. 210; a booster 260 for increasing the pressure of the refrigerant vaporized by the refrigerant evaporator 210;
A condenser 220 for cooling the refrigerant pressurized by the booster 260 with the regeneration air to condense the refrigerant; the refrigerant condensed by the condenser 220 may be supplied to the processing air cooler 300. For example, a refrigerant path 202 for supplying the refrigerant condensed by the condenser 220 to the processing air cooler is provided.

The booster is, for example, a compressor, and the pressure is increased by compressing the gas with the compressor. However, as in an absorption heat pump, a combination of an absorber that absorbs a refrigerant with an absorbing liquid, a regenerator that regenerates the absorbing liquid, and a pump that pressurizes the absorbing liquid that has absorbed the refrigerant and sends it from the absorber to the regenerator. It may be.

With this configuration, the heat pump HP includes the refrigerant evaporator, the booster, and the condenser, and is configured to supply the refrigerant condensed in the condenser to the processing air cooler. Therefore, the refrigerant used in the processing air cooler and the refrigerant used in the heat pump can be shared.

Further, as shown in claim 3, and as shown in FIG. 9, a condenser 220 and a processing air cooler 30 are provided.
0d, a gas-liquid separator 350 for separating the refrigerant into a refrigerant liquid and a refrigerant gas may be provided. For example, a refrigerant path 202 is provided between the condenser 220 and the processing air cooler 300d, and a gas-liquid separator 350 is provided in the path. The gas-liquid separator itself may function as a refrigerant path.

With this configuration, since the gas-liquid separator is provided, the refrigerant flowing into the processing air cooler for cooling the processing air by evaporation can be mainly composed of the liquid phase, and is condensed by the cooling fluid. It is possible to make the gaseous phase component of the refrigerant to be uniform.

In the above dehumidifying air conditioner,
Using air as the cooling fluid, the processing intake air cooler 300
When condensing the refrigerant in the above, it may be configured to supply liquid moisture together with the air, and in such a configuration, the temperature of the air as a cooling fluid decreases due to heat of vaporization due to evaporation of the liquid moisture, The cooling effect increases.

According to another aspect of the present invention, the above object is achieved.
A first step of cooling the processing air with a refrigerant that evaporates at a first pressure;
A second step of compressing the refrigerant evaporated in the first step to a second pressure; a third step of heating regeneration air for desiccant regeneration with the refrigerant condensing at the second pressure;
A fourth step of desorbing moisture from the desiccant with the regeneration air heated in the third step to regenerate the desiccant; and adsorbing moisture in the processing air with the desiccant regenerated in the fourth step. A fifth step; evaporating the refrigerant condensed in the third step at an intermediate pressure between the first pressure and the second pressure to remove the process air having the water adsorbed in the fifth step. A sixth step of cooling; and a seventh step of condensing the refrigerant evaporated at the intermediate pressure at substantially the same pressure as the intermediate pressure.
And the step of Further, the refrigerant condensed in the seventh step may be used as the refrigerant to be evaporated in the first step.

With this configuration, for example, the first pressure is set to the refrigerant evaporation pressure corresponding to the temperature of the processing air suitable for supplying the air-conditioned space 101, and the second pressure is set to the regeneration temperature of the regeneration air. The so-called economizer cycle can be used by setting the intermediate pressure to the pressure corresponding to the atmospheric temperature as the refrigerant condensing pressure, so that the cooling effect of the refrigerant can be significantly increased, and thus the processing air with a high COP can be obtained. Can be dehumidified.

[0019]

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

FIG. 1 is a flowchart of an air conditioning system having a dehumidifying air conditioner, that is, a desiccant air conditioner according to a first embodiment of the present invention. FIG. 2 is a process air cooling system of the present invention used in the air conditioning system of FIG. FIG. 3 is a schematic cross-sectional view showing an example of a heat exchanger as a heat exchanger, and FIG. 3 is a refrigerant Mollier diagram of a heat pump HP1 included in the air conditioning system of FIG.

Referring to FIG. 1, the configuration of the dehumidifying air conditioner according to the first embodiment will be described. This air conditioning system
The desiccant (desiccant) reduces the humidity of the treated air,
This is to maintain the air-conditioned space 101 to which the processing air is supplied in a comfortable environment. In the drawing, a blower 1 for circulating the processing air along the path of the processing air A from the air-conditioned space 101
02, desiccant rotor 103 filled with desiccant
The processing air cooler 300 and the refrigerant evaporator (cooler as viewed from the processing air) 210 of the present invention are arranged in this order, and are configured to return to the air-conditioned space 101.

A heat exchanger 121 for exchanging heat between the regeneration air before entering the desiccant rotor 103 and the subsequent regeneration air along a path from the outdoor OA to the regeneration air B, a refrigerant condenser (as viewed from the regeneration air) A heater 220, a desiccant rotor 103, a blower 140 for circulating regenerated air, and a heat exchanger 121 are arranged in this order, and are configured to exhaust EX to the outside.

A processing air cooler 300 and a blower 160 for circulating the cooling fluid are arranged in this order along a path from the outdoor OA to the outside air as the cooling fluid C, and the exhaust air is exhausted to the outside. It is configured.

A compressor 260, a refrigerant condenser 220, a throttle 230, a processing air cooler 300, and a throttle 240, which compress the refrigerant evaporated and gasified by the refrigerant evaporator along the refrigerant path from the refrigerant evaporator 210. Are arranged in this order, and return to the refrigerant evaporator 210 again to constitute the heat pump HP1.

The desiccant rotor 103 is formed as a thick disk-shaped rotor that rotates around a rotation axis AX as shown in FIG. 15, and the rotor is filled with a desiccant with a gap through which gas can pass. ing.
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 rotates in one direction around the rotation axis AX, and the processing air A and the regeneration air B flow in and out in parallel with the rotation axis AX. Each drying element 103a, as the rotor 103 rotates,
The processing air A and the regeneration air B are arranged so as to come into contact alternately. In FIG. 15, a part of the outer peripheral portion of the desiccant rotor 103 is shown broken. Although the figure shows a gap between the outer periphery of the desiccant rotor 103 and a part of the drying element 103a, the drying elements 103a are actually bundled and tightly packed in the entire disk. In general, 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) face substantially half of the circular desiccant rotor 103 in parallel with the rotation axis AX. It is configured to flow in a flow format.

The desiccant may be filled in the tubular drying element 103a, the tubular drying element 103a itself may be formed of desiccant, the desiccant may be applied to the drying element 103a, The drying element 103a may be made of a porous material, and the material may contain a desiccant. The drying element 103a may be formed in a cylindrical shape having a circular cross section as shown in the figure, or may be formed in a hexagonal cylindrical shape and bundled to form a honeycomb shape as a whole. In any case, the air is configured to flow in the thickness direction of the disk-shaped rotor 103.

Since a large amount of regeneration air must be passed through the heat exchanger 121, for example, as shown in FIG. 16, a cross-flow type in which low-temperature regeneration air B1 and high-temperature regeneration air B2 flow orthogonally. And a rotary heat exchanger filled with a heat storage material having a large heat capacity is used instead of the drying element in a structure similar to that of the heat exchanger of FIG. At this time, the processing air A in FIG.
1 corresponds to the regeneration air B and the high-temperature regeneration air B2.

Next, referring to FIG. 2, heat pump HP1
The configuration of a heat exchanger suitable for use in the present invention will be described. In the figure, the heat exchanger 300 includes a first section 310 through which the processing air A flows.
And a second section 320 for flowing outside air as a cooling fluid,
They are provided adjacent to each other with one partition 301 interposed therebetween.

A plurality of heat exchange tubes as fluid passages through which the refrigerant 250 flows are provided substantially horizontally through the first section 310, the second section 320, and the partition wall 301. In the heat exchange tube, a portion penetrating the first section has an evaporating section 251 as a first fluid flow path.
(A plurality of evaporating sections 251A, 251B, 251
C. Hereinafter, when it is not necessary to discuss a plurality of evaporation sections individually, the part passing through the second section is simply a condensing section 252 (a plurality of condensing sections are referred to as 252A). , 25
2B and 252C. Hereinafter, when it is not necessary to discuss a plurality of condensation sections individually, it is simply referred to as 252).

In the form of the heat exchanger shown in FIG. 2, the evaporating section 251A and the condensing section 252A are formed as an integral flow path by one tube. The same applies to the evaporating sections 251B, C and the condensing sections 252B, C. Therefore, in combination with the fact that the first section 310 and the second section 320 are provided adjacent to each other with one partition wall 301 interposed therebetween, the heat exchanger 300 can be formed to be small and compact as a whole. .

In the form of the heat exchanger shown in FIG. 2, the evaporating sections are arranged in the order of 251A, 251B, and 251C from the top in the figure, and the condensing sections are also 252A, 252A, and 252A from the top in the figure.
52B and 252C.

On the other hand, the processing air A is configured to enter the first section in FIG. The outside air, which is a cooling fluid, is configured to enter the second section in the drawing through the duct 171 from below and flow out from above.

Further, in the second section, the upper part thereof, above the heat exchange tube constituting the condensation section 252,
A watering pipe 325 is arranged. Watering pipe 325
Are provided with nozzles 327 at appropriate intervals to condense the water flowing in the watering pipe 325 to the condensing section 2.
It is configured to spray to the heat exchange tube constituting 52.

Further, a vaporizing humidifier 165 is installed at the inlet of the cooling fluid as the second fluid in the second section.
The vaporizing humidifier 165 is made of a material that has a hygroscopic property and a gas permeability, such as a ceramic paper and a nonwoven fabric.

Here, the evaporation pressure in the evaporation section 251 and, consequently, the condensation pressure in the condensation section 252,
That is, the second pressure is determined by the temperature of the processing air A and the temperature of the outside air that is the cooling fluid. The heat exchanger 30 shown in FIG.
No. 0 uses the evaporation heat transfer and the condensation heat transfer, so that the heat transfer coefficient is very excellent and the heat exchange efficiency is very high. In addition, the refrigerant flows from the evaporation section 251 to the condensation section 2.
Since it flows toward 52, that is, it is forced to flow in almost one direction, the heat exchange efficiency between the processing air and the outside air as the cooling fluid is high. Here, the heat exchange efficiency φ means that the inlet temperature of the heat exchanger on the high-temperature side fluid is TP1 and the outlet temperature is T
P2, when the inlet temperature of the heat exchanger of the fluid on the low temperature side is TC1 and the outlet temperature is TC2, when attention is paid to cooling of the fluid on the high temperature side, that is, when the purpose of heat exchange is cooling, φ = (T
P1-TP2) / (TP1-TC1), when attention is paid to heating of a low-temperature fluid, that is, when the purpose of heat exchange is heating,
φ = (TC2−TC1) / (TP1−TC1).

Evaporation section 251, condensation section 2
It is preferable to form a high-performance heat transfer surface by forming a spiral groove such as a linear groove on the inner surface of the barrel of the rifle gun on the inner surface of the heat exchange tube constituting 52. The refrigerant liquid flowing inside usually flows so as to wet the inner surface,
When the spiral groove is formed, the heat transfer coefficient is increased because the boundary layer of the flow is disturbed.

Although the processing air flows through the first section, it is preferable that the fin attached to the outside of the heat exchange tube is processed into a louver shape to disturb the flow of the fluid. Preferably, the fins are similarly configured to disrupt the flow of fluid when the outside air flows into the second compartment but does not spray water. However, when water is sprayed, it is preferable to further provide a corrosion-resistant coating as flat plate fins. This is to prevent corrosive substances possibly mixed in the water from condensing and condensing by evaporation to corrode the fins or tubes. The fins are preferably made of aluminum, copper, or an alloy thereof.

Here, the refrigerant has been described as flowing in one direction from the evaporating section 251 to the condensing section 252. However, for example, a single tube having both ends closed, the evaporating section 251 and the condensing section 252,
Formed as a so-called heat pipe, condensing section 2
The refrigerant condensed in 52 may be returned to the evaporating section 251 by utilizing a capillary phenomenon or the like, where it is evaporated again, and thus the refrigerant may be circulated in one tube. At this time, the heat transfer is still the same using the evaporation heat transfer and the condensation heat transfer, and the heat transfer coefficient can be enjoyed, and the structure becomes simple as a heat exchanger for exchanging heat between the processing air and the cooling fluid. There is an advantage.

The operation of the first embodiment will be described with reference to FIG. 4 and the configuration as appropriate with reference to FIG.
In FIG. 4, the state of air in each part is indicated by alphabetic symbols D, E, K to N, and Q to 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. 4, the processing air (state K) from the air-conditioned space 101 is:
The air is sucked by the blower 102 through the processing air path 107 and is sent to the desiccant rotor 103 through the processing air path 108. Here, the drying element 103a
Water is adsorbed by the desiccant in FIG. 15 to lower the absolute humidity, and the dry bulb temperature is raised by the heat of adsorption of the desiccant to reach the state L. This air is treated air path 1
09 through the first section 310 of the process air cooler 300
Where the absolute humidity is constant and evaporation section 2
Cooled by the refrigerant evaporating in 51 (FIG. 2), it becomes air in the state M, and enters the cooler 210 through the path 110.
Here, the air is further cooled at a constant absolute humidity to be in the state N. This air is dried and cooled, and is treated as a treatment air SA having an appropriate humidity and an appropriate temperature as duct 111.
And is returned to the air-conditioned space 101.

Next, the flow of the regeneration air B will be described. In FIG. 4, the regeneration air (state Q) from the outdoor OA is sucked through the regeneration air path 124 and sent to the heat exchanger 121. Here, heat exchange is performed with the high-temperature regenerated air to be exhausted (air in state U described later) to raise the dry-bulb temperature to become air in state R. This air is sent to a refrigerant condenser (heater as viewed from the regeneration air) 220 through a path 126, where it is heated to increase the dry-bulb temperature and become air in state T. This air is sent through a path 127 to the desiccant rotor 103 where the drying element 10
3a (FIG. 15) deprives the desiccant of moisture and regenerates it, thereby increasing the absolute humidity and lowering the dry-bulb temperature due to the heat of desorption of the desiccant to reach the state U. This air is sucked through a passage 128 into a blower 140 for circulating the regeneration air, sent through a passage 129 to the heat exchanger 121, and as described above, before being sent to the desiccant rotor 103 (state). Q
Exchanges heat with the air), the temperature of the air itself decreases, and the air becomes the state V, and is exhausted EX through the passage 130.

Next, the flow of the outside air C as the cooling fluid will be described. The outside air C (state Q) is sent from the outdoor OA to the second section 320 of the process air cooler 300 through the path 171. Here, first, moisture is absorbed by the humidifier 165,
By changing the isenthalpy and increasing the absolute humidity and lowering the dry-bulb temperature, the air becomes state D. State D is almost on the saturation line of the wet vapor diagram. This air is supplied to the second compartment 3
The cooling medium in the condensing section 252 is cooled while absorbing the water supplied by the watering pipe 325 in the inside 20. This air rises in absolute humidity and dry-bulb temperature substantially along the saturation line, becomes air in state E, and is exhausted EX through the passage 172 by the blower 160 provided in the middle of the passage 172.

Referring now to FIG.
5. The operation of the watering pipe 325 will be described. In the air conditioner as described above, as shown in the cycle on the air side shown in the psychrometric chart of FIG. 4, the amount of heat added to the regeneration air for regeneration of the desiccant of the device is pumped from the processing air by ΔH. Assuming that the heat amount is Δq and the driving energy of the compressor is Δh, ΔH = Δq + Δh. The cooling effect ΔQ obtained as a result of the regeneration based on the heat quantity ΔH 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. That is, it becomes larger as ΔQ−Δq becomes larger in the figure. Therefore, spraying water on the outside air as the cooling fluid is useful for enhancing the cooling effect. In FIG. 4, points indicated as state M ′ and state N ′ conceptually show the positions of state M and state N, respectively, when the vaporizing humidifier 165 and the sprinkling pipe 325 are not used.

Next, the flow of the refrigerant between the devices will be described first with reference to FIG. 1, and then the operation of the heat pump HP1 will be described with reference to FIG.

In FIG. 1, the refrigerant gas compressed by the refrigerant compressor 260 is guided to a regenerative air heater (refrigerant condenser) 220 via a refrigerant gas pipe 201 connected to a discharge port of the compressor. The temperature of the refrigerant gas compressed by the compressor 260 is increased by the heat of compression, and this heat heats the regeneration air. The refrigerant gas itself is deprived of heat and condenses.

The refrigerant outlet of the refrigerant condenser 220 is connected to the inlet of the evaporating section 251 of the processing air cooler 300, which is a heat exchanger, by a refrigerant path 202, and in the middle of the refrigerant path 202 near the inlet of the evaporating section 251. Is provided with a diaphragm 230.

Refrigerant condenser (heater as viewed from regeneration air)
The liquid refrigerant that has exited 220 is depressurized by the throttle 230, expanded, and some of the liquid refrigerant evaporates (flashes). The liquid-gas mixed refrigerant reaches the evaporator section 251 where the liquid refrigerant flows and evaporates to wet the inner walls of the evaporator section tubes to cool the process air flowing through the first compartment.

Evaporation section 251 and condensation section 2
52 is a series of tubes. That is, since the refrigerant gas is configured as an integral flow path, the evaporated refrigerant gas (and the refrigerant liquid that has not evaporated) flows into the condensing section 252 and generates heat by the outside air flowing through the second section and the sprayed water. Deprived and condensed.

The outlet side of the condensing section 252 is connected to a refrigerant evaporator (a cooler for processing air) 210 by a refrigerant liquid pipe 203. A throttle 240 is provided in the middle of the refrigerant pipe 203. The throttle 240 is attached to the refrigerant evaporator 21 immediately after the condensing section 252.
Although it may be anywhere up to the entrance of 0, it is preferable to be as close to the entrance of the refrigerant evaporator 210 as possible. This is because the refrigerant after the throttle 240 becomes considerably lower than the atmospheric temperature, so that the cooling of the pipe must be thickened. Condensing section 252
The refrigerant liquid condensed by the pressure is decompressed and expanded by the throttle 240 to reduce the temperature, enters the refrigerant evaporator 210 and evaporates, and cools the processing air by the heat of evaporation. As the throttles 230 and 240, for example, orifices, capillary tubes, expansion valves, and the like are used.

The refrigerant evaporated and gasified by the refrigerant evaporator 210 is guided to the suction side of the refrigerant compressor 260, and the above cycle is repeated.

Next, referring to FIG. 3, heat pump HP1
The operation of will be described. FIG. 3 is a Mollier diagram when the refrigerant HFC134a is used. In this diagram, the horizontal axis is enthalpy and the vertical axis is pressure.

In the figure, the point a is the state of the refrigerant outlet of the refrigerant evaporator 210 of FIG. 1 and is in the state of saturated gas. The pressure is 4.2 kg / cm ² , the temperature is 10 ° C., the enthalpy is 14
It is 8.83 kcal / kg. This gas is supplied to the compressor 26
A state where the suction compression is performed at 0 and a state at the discharge port of the compressor 260 are indicated by a point b. In this state, the pressure is 19.3k
g / cm ² , the temperature is 78 ° C., and it is in a superheated gas state.

This refrigerant gas is cooled in the refrigerant condenser 220 and reaches a point c on the Mollier diagram. This point is a state of a saturated gas, the pressure is 19.3 kg / cm ² , and the temperature is 6
5 ° C. Under this pressure, it is further cooled and condensed to reach point d. This point is a state of a saturated liquid, and the pressure and the temperature are the same as those of the point c, the pressure is 19.3 kg / cm ² , and the temperature is 6
5 ° C. and enthalpy 122.97 kcal / kg
It is.

The refrigerant liquid is decompressed by the throttle 230 and is evaporated by the evaporating section 25 of the processing air cooler 300 which is a heat exchanger.
Flow into 1. On the Mollier diagram, it is indicated by a point e. The temperature will be about 30 ° C. The pressure is the second pressure of the present invention. In this embodiment, the pressure is 4.2 kg / cm ² and 19.3.
A saturation pressure corresponding to an intermediate value of kg / cm ² , that is, 30 ° C. is obtained. Here, a part of the liquid is evaporated and the liquid and the gas are mixed. In the evaporating section 251, the refrigerant liquid evaporates under the second pressure to reach a point f between the saturated liquid line and the saturated gas line at the same pressure. Here, the liquid has almost completely evaporated. At the point e, the ratio between the refrigerant liquid and the gas is the inverse ratio of the difference between the enthalpy at the point where the 30 ° C. saturated pressure line crosses the saturated liquid line and the saturated gas line and the enthalpy at the point d. As is clear from the diagram, the liquid is more in weight ratio. However, since the volume ratio of gas is overwhelmingly large, the liquid is mixed with a large amount of gas in the evaporating section, and the liquid evaporates while the liquid wets the inner surface of the tube of the evaporating section.

The refrigerant in the state indicated by the point f flows into the condensing section 252. In the condensing section 252, the refrigerant is deprived of heat by the outside air and / or sprayed water flowing through the second compartment and reaches point g. This point is on the saturated liquid line in the Mollier diagram. Temperature 30 ° C, enthalpy 1
It is 09.99 kcal / kg.

The refrigerant liquid at the point g is passed through the throttle 240 and
The pressure was reduced to a saturation pressure of 4.2 kg / cm ² ,
A refrigerant evaporator 210 as a mixture of refrigerant liquid and gas at 10 ° C.
, Where heat is taken from the processing air and evaporated to become a saturated gas in the state of the point a on the Mollier diagram.
0, and the above cycle is repeated.

As described above, the processing air cooler 30
In 0, the refrigerant evaporates from the point e to the point f in the evaporating section 251, and changes state from the point f to the point g in the condensing section 252. Very high heat transfer coefficient.

Further, as the compression heat pump including the compressor 260, the refrigerant condenser (regeneration air heater) 220, the throttles 230 and 240 and the refrigerant evaporator 210, when the processing air cooler 300 is not provided, the refrigerant condenser The refrigerant in the state at the point d in 220 is supplied to the refrigerant evaporator 210 through the throttle.
Enthalpy difference available in the refrigerant evaporator 210 is 148.83-122.97 = 25.86 kcal
/ Kg, but in the case of the heat pump HP1 used in the present embodiment provided with the processing air cooler 300, 148.83-109.99 = 38.84 kcal.
/ Kg, and the amount of gas circulating through the compressor for the same cooling load, and thus the required power, can be reduced by 33%. That is, even if the compressor 260 is of a single-stage type, it can have the same effect as an economizer in which a plurality of stages (for example, a two-stage type) sucks flash gas into an intermediate stage.

Next, a dehumidifying air conditioner according to a second embodiment incorporating a heat pump HP2 according to another embodiment will be described with reference to FIG. Except that water is used as a cooling fluid flowing to the second section of the processing air cooler 300b,
The configuration and operation are the same as those of the first embodiment. In the figure,
In a cooling tower 470 installed outdoors, cooling water cooled to about 32 ° C. in summer is guided to a suction port of a cooling water pump 460 through a cooling water pipe 471 connected to the bottom of the cooling tower 470. Through the cooling water pipe 472 connected to the discharge port, it is sent to the second section 320 of the processing air cooler 300b.

The second section 32 of the processing air cooler 300b
In the case of 0, the cooling water flows outside the heat exchange tube perpendicular to the tube by removing the baffle plate provided to be perpendicular to the heat exchange tube. A cooling water pipe 473 is connected to a cooling water outlet of the second section 320, and is configured to return the cooling water whose temperature has increased in the processing air cooler 300 b to the cooling tower 470. As described above, in the first embodiment of FIG. 1, the refrigerant is condensed in the condensing section by the outside air, whereas in the second embodiment, the refrigerant is condensed in the condensing section by the cooling water. ing. The refrigerant cycle of the heat pump HP2 is the same as that in FIG.

Next, referring to the table of FIG. 6, the first embodiment of the present invention will be described.
The operation mode of the dehumidifying air conditioner and the operation of each device according to the embodiment will be described. As shown in the table, the dehumidifying air conditioner of the first embodiment can operate in a cooling operation mode and a dehumidification operation mode. In the cooling operation mode, all of the desiccant rotor 103, the blower 102, the blower 140, the blower 160, the water spray 325, and the compressor 260 are operated or operated. The flows of the cooling fluid, the refrigerant, and the like are as described above.

In the dehumidification mode, the desiccant rotor 10
3. The blower 102, the blower 140, and the compressor 260 are operating, but the blower 160 is stopped, and the water spray 325 is not operating. At this time, in FIG.
Since the outside air C which is the cooling fluid is not flowing and the water is not sprayed to the second section 320, heat is not taken from the refrigerant between the throttles 230 and 240. Most transiently, the process air flowing through the first section 310 may heat (or cool) the refrigerant, but ultimately the evaporation temperature of the refrigerant between the throttles 230 and 240 causes the process air to cool. It is at the same level as the temperature and balance, so there is no heat flow. Accordingly, considering the psychrometric chart of FIG. 4, there is no cooling between the state L and the state M, and the processing air is only cooled by the refrigerant evaporator 210 after being dehumidified by the desiccant rotor 103. The state in which the treated air is returned to the air-conditioned space has a lower absolute humidity than the state K, and the dry-bulb temperature is not much different from the state K. That is, this operation mode is basically a dehumidification operation mode. In the second embodiment shown in FIG. 5, if the cooling water pump 460 is stopped, the same dehumidifying operation mode as described above is possible.

Referring to FIG. 7, an example of the mechanical arrangement of the dehumidifying air conditioner described above will be described. In FIG. 7, devices constituting the apparatus are housed in a cabinet 700. The cabinet 700 is formed as a rectangular parallelepiped housing made of, for example, a thin steel plate, and has a suction opening for the processing air RA opened at the lower side in the vertical direction. A filter 501 is provided at the opening to prevent dust from the air-conditioned space from being brought into the device. The blower 102 is installed in the cabinet 700 inside the filter 501, and the suction port thereof communicates with the processing air suction port of the cabinet through the filter 501.

A compressor 260 and a blower 140 are arranged in a space below the cabinet so as to be arranged substantially horizontally in the horizontal direction. Also, the compressor 260 and the blower 1
Above 40, desiccant rotor 103 is arranged with its rotation axis directed vertically. Desiccant rotor 103
Is connected to an electric motor 105, which is also a driving machine whose rotation axis is directed vertically in the vicinity thereof, by a belt, a chain, and the like, and is configured to be rotatable at a low speed of about one rotation in several minutes. Thus, the desiccant rotor 10
By arranging 3 so as to be rotated in a substantially horizontal plane about a rotation axis oriented in the vertical direction, the height of the entire apparatus can be kept low, and the apparatus can be made compact. In addition, if most of the blowers 102 and 140, which are movable elements or rotating bodies, including the heavy compressor 260, and the desiccant rotor 103 are collected in the lower part of the apparatus, the lower part of the cabinet 700, that is, near the foundation, the influence of vibration will be reduced. And the installation stability of the device is increased.

The outlet of the blower 102 is connected to a desiccant rotor by a passage 108. The passage 108 is formed so as to be separated from other portions by, for example, a thin steel plate similar to that forming the cabinet 700. The processing air flows into an area of about half (semicircle) of the circular desiccant rotor 103.

Vertically above the desiccant rotor 103,
In particular, a first section 310 of the process air cooler 300, that is, an evaporating section 251 is disposed above a half (semicircle) region where the process air flows. Path 109 connecting desiccant rotor 103 and first section 310
Are formed in the structure of FIG. 7 as a narrow space between the horizontally placed rotor and the tubes of the evaporation section, also horizontally placed (and the fins attached to these tubes).

Above the first section 310 in the vertical direction, a refrigerant evaporator 210 is arranged with its cooling pipe horizontal. In the example shown in FIG. 7, the route 110 is
Although the space is between 0 and the refrigerant evaporator 210, since both are closely arranged, the space hardly exists. Above the refrigerant evaporator 210 in the vertical direction, an opening for blowing the supply air SA into the air-conditioned space is provided in the cabinet 700.

On the other hand, an outside air inlet is opened above the side of the cabinet 700, and a filter 502 for blocking dust from outside air is provided here. The space inside the filter 502 constitutes the path 124, and the cross-flow type heat exchanger 121 is installed so as to define a part of the space. A refrigerant condenser 220 is arranged at one outlet side of the heat exchanger 121. Refrigerant condenser 2
In 20, the heat exchanger tubes are arranged substantially horizontally, and are arranged substantially side by side with the refrigerant evaporator 210. A space below the refrigerant condenser 220 in the vertical direction and between the desiccant rotor 103 constitutes a path 127, through which the remaining half of the desiccant rotor 103 on the processing air side described above is left. It is configured such that the regeneration air is guided to half the area. A space vertically below a half area of the desiccant rotor 103 through which the regeneration air passes forms a path 128, and a blower 140 is installed in this space with its suction port facing the space. Blower 14
0 outlets are facing sideways and cabinet 700
Is connected to the heat exchanger 121 by a path 129 defined in the vertical direction. The regenerated air passing therethrough is defined by the heat exchanger 121 and the cabinet 700 in the heat exchanger 121 through a flow path orthogonal to the flow path of the air guided through the path 124 described above. After reaching the path 130 which is a space, the exhaust air is exhausted through an opening formed in the cabinet 700.

Further, an outside air intake port is opened on the side of the cabinet 700 and almost immediately above the intake port of the processing air. A filter 503 is provided in this opening to prevent outside dust from being brought into the apparatus. The space inside the filter 503 forms a path 171, and a humidifier 165 is provided substantially horizontally above this space. The space above the humidifier 165 is the second compartment 320
And the condensing section 252 is provided in this space.
Heat exchange tubes are arranged substantially horizontally. Condensing section 252 and evaporating section 25 described above
Reference numeral 1 denotes an integral tube. A watering pipe 325 is disposed in a space above the condensing section 252 so that water can be sprayed from above the tubes (and fins) of the condensing section 252. The watering pipe 325 is provided with a control valve, and is configured to appropriately adjust the amount of water to be sprayed. For example, the humidifier 165 is adjusted to be moderately moist and not too moist. In addition, the lower part of the space constituting the path 171 is a drain pan, and is configured so that excess water can be discharged to the outside of the cabinet 700 when water is excessively sprayed with a watering pipe. The space above the second section 320 in the vertical direction is also a path 172, and an air outlet is opened in a portion of the cabinet 700 above this space. This air outlet is provided with a blower 160
Is provided.

On the other hand, a refrigerant pipe 201 for sending the refrigerant gas discharged from the compressor 260 to the refrigerant condenser 220 is provided so as to run up along the bottom of the cabinet 700 and further rise. A first throttle (also serving as a refrigerant header) 230 is provided below the refrigerant condenser 220, and decompresses the condensed refrigerant to guide it to the evaporating section 251. The refrigerant decompressed via the throttle is sent to the evaporation section 251 composed of a plurality of tubes and evaporates. The header 24 for continuously collecting the refrigerant condensed in the condensing section 252
0 is provided at the outlet of the condensation section 252.
The refrigerant pipe from the header 240 rises from the header 240 and is decompressed by a throttle 270 provided near the uppermost portion. In addition, as shown in FIG.
7, the aperture 270 in FIG. 7 may be omitted. At this time, the pressure in the refrigerant evaporator 21
Insulation until reaching 0 must be sufficient.

A refrigerant pipe 205 connecting the evaporator 210 and the compressor 260 is provided vertically downward from the evaporator 210. The throttle 270 is connected to the refrigerant evaporator 21.
The opening degree, that is, the degree of restriction may be adjusted by a temperature controller in which a temperature sensing part is attached to the evaporating tube of 0. By doing so, excess refrigerant liquid is supplied to the refrigerant evaporator 210,
As a result, suction of the liquid refrigerant into the compressor 260 can be prevented.

Referring to FIG. 8, a description will be given of a heat exchanger 300d as a processing air cooler suitable for use in a dehumidifying air conditioner according to another embodiment of the present invention. Heat exchanger 300d
Can be used in place of the heat exchanger 300 in the heat pump HP1 described with reference to FIG. In the figure, the heat exchanger 300d is provided with a processing fluid A as a first fluid.
The point that the first section 310 for flowing the air and the second section 320 for flowing the outside air B as the second fluid are provided adjacent to each other with one partition wall 301 therebetween is shown in FIG. Same as the exchanger.

The arrangement of the evaporation sections 251A, B and C, the arrangement of the condensation sections 252A, B and C, the sprinkling pipe 325, the evaporative humidifier 165, the processing air paths 109 and 1
10. The arrangement of the outside air path 171 is the same as that of the heat exchanger shown in FIG.

Headers 450A, B, and C are connected to the evaporation sections 251A, B, and C, and refrigerant pipes 430A, 430B, and 43 are connected to the headers 450A, B, and C, respectively.
0C is connected. Also, each evaporating section 251
Each of A, B, and C includes one or more typically two or more (six in the example of FIG. 8) heat exchange tubes, and the plurality of heat exchange tubes are connected to each header 4.
50A, B, and C.

The refrigerant gas pipe 340 is connected to the heat exchanger 300 d
Pass through the first compartment 310 via the tube 341. The tube 341 is disposed so as to penetrate the partition 301 and further penetrate the second section 320. In the example of FIG. 8, two tubes 341 are arranged in parallel,
Is divided into three passes. Here, the portion inside the second section 320 of the tube 341 has a structure in which fins are attached to the outside of the tube to promote heat exchange, similarly to the condensation sections 252A, 252B, and 252C. This part is called a condensation section 252D. The condensing section 252D is arranged on the upstream side of the outside air flow of the condensing section 252C, between the condensing section 252C and the vaporizing humidifier 165. In the condensation section 252D, the refrigerant gas is deprived of heat by the outside air as the second fluid and condenses. The condensing section 252D may be arranged on the downstream side of the outside of the condensing section 252A.

The tube 341 hardly contributes to heat exchange in the first section, so that it effectively bypasses the first section 310. Thus, the first section 310 is actually structurally bypassed, ie, the first section 310
Of the condensing section 252D in the second compartment
May be arranged so as to be connected.

Headers 455A, 455B, and 455C are provided on the refrigerant liquid outlet side of the condensing sections 252A, 252B, and 252C, respectively, and the condensing sections 252A, 252B, and 252C each composed of a plurality of tubes are integrated. . The piping from each header is further combined into one header 370 (FIG. 9).
03 is connected to the expansion valve 270. The refrigerant liquid from the condensing section 252D is
And joined to the path 203 on the downstream side of the header 370. Note that the pipe 345 may be connected to the header 370.

A dehumidifying air conditioner (desiccant air conditioner) according to a third embodiment of the present invention incorporating a heat pump HP3 including a heat exchanger 300d will be described with reference to the flowchart of FIG. FIG. 10 shows the heat pump H of FIG.
It is a Mollier diagram explaining the refrigerant cycle of P3.

The path of the processing air and the path of the regeneration air are shown in FIG.
The description is omitted because it is the same as that of the air conditioner of the embodiment.

Here, the refrigerant path of the heat pump HP3 will be described. In the figure, a refrigerant gas compressed by a refrigerant compressor 260 is guided to a regenerative air heater 220 via a refrigerant gas pipe 201 connected to a discharge port of the compressor. The temperature of the refrigerant gas compressed by the compressor 260 is increased by the heat of compression, and the heat heats the regeneration air (described later).
The refrigerant gas itself is deprived of heat and condenses.

The refrigerant outlet of the heater 220 is connected to the heat exchanger 30
The refrigerant passage 202 is connected to the entrances of the 0d evaporation sections 251A, B, and C by a refrigerant path 202. A throttle 360 such as an expansion valve is provided in the middle of the refrigerant path 202. The restriction 360 and the evaporation sections 251A, B, and A gas-liquid separator 350 is provided between C and C.

The liquid refrigerant which has exited the heater (cooler or condenser as viewed from the refrigerant side) 220 is decompressed by an expansion valve 360 as a first throttle, expands and a part of the liquid refrigerant evaporates (flashes). ). The refrigerant mixed with the liquid and gas is
The refrigerant liquid and the refrigerant gas are separated by the gas-liquid separator 350, and the refrigerant liquid reaches the evaporating sections 251A, B, and C, and the refrigerant evaporates in the tubes of the evaporating section and flows through the first section. To cool.

Evaporation section 251 and condensation section 2
52 is a series of tubes, ie, configured as an integral flow path, so that the evaporated refrigerant gas (and the non-evaporated refrigerant liquid) flows into the condensing section 252 and passes through the second section. The heat is deprived by the flowing outside air and the sprayed water and condensed.

The outlet side of the condensing section 252 is connected to an expansion valve 270 as a second throttle by the refrigerant liquid pipe 203.
Further, it is connected to a cooler 210 by a refrigerant pipe 204. The refrigerant liquid condensed in the condensing section 252 is decompressed and expanded by the throttle 270 to reduce the temperature, and
And evaporates, and the process air is cooled by the heat of evaporation. As the throttles 360 and 270, for example, an orifice or a capillary tube other than the expansion valve may be used.

Cooler (evaporator as viewed from refrigerant side) 210
The refrigerant evaporated and gasified by the above is guided to the suction side of the refrigerant compressor 260, and the above cycle is repeated.

The gas-liquid separator 350 includes a container into which a mixture of gas and liquid flows, and a baffle plate 355 disposed in the container so as to face the inlet of the gas-liquid mixture. I have. The gas-liquid mixture collides with the baffle plate 355 and the liquid is separated from the gas, and the gas flows out of the gas outlet provided in the vessel alongside the gas-liquid mixture inlet, and is connected to the gas outlet. Heat exchanger 300 through refrigerant pipe 340
Flow to d. The refrigerant liquid flows out from a liquid outlet provided vertically below the container of the gas-liquid separator. Refrigerant pipes 430A, 430B, and 430C are connected to the liquid outlets, and communicate with the evaporation sections 251A, 251B, and 251C, respectively.

Referring to the Mollier diagram of FIG. 10, a heat exchanger 30 according to an embodiment of the present invention in the air conditioning system of FIG.
The operation of the heat pump HP3 including Od will be described. FIG. 10 is a Mollier diagram when the refrigerant HFC134a is used. In this diagram, the horizontal axis is enthalpy and the vertical axis is pressure.

In the figure, points a, b, c and d are the same as those in the Mollier diagram of FIG. 3 and will not be described. The refrigerant liquid in the state at the point d is decompressed by the throttle 360 and the gas-liquid separator 350
Flows into. Here, the separated refrigerant gas is used as the gas at the intersection point h between the saturated pressure line and the isopressure line of the saturation pressure corresponding to 40 ° C.
It flows into the tube 341 through 40. Here, heat is deprived and condensed by outside air (outside air cooled by water from a vaporizing humidifier and a watering pipe), and reaches a saturated liquid gland, and is typically supercooled, and exceeds a saturated liquid gland. It reaches point i of the cooling liquid phase.

The liquid separated by the gas-liquid separator 350 is
This is the liquid in the state of point g on the saturated liquid gland. The liquid in the state at the point i and the liquid in the state at the point g are mixed in the header 370, decompressed by the expansion valve 270, the pressure is 4.2 kg / cm ² , and the temperature is 10
° C refrigerant (mixture of gas and liquid).

As described above, in the heat exchanger 300d according to the embodiment of the present invention, the evaporating section 251 is provided.
The refrigerant introduced into the heat exchange tubes (heat transfer tubes) constituting A, B, and C hardly contains any gaseous components. Therefore, the amount of the refrigerant guided to the evaporating sections 251A, B, and C becomes uniform, and thus the evaporating sections 251A, B, and C
The cooling of the first fluid by evaporation in the condenser becomes uniform, and the amount of refrigerant condensed in the heat transfer tubes of the condensation sections 252A, B, and C is occupied by the refrigerant evaporated in the evaporation sections 251A, B, and C. When a gas phase is contained, non-uniform heat transfer occurs, particularly in a condensing section containing a large amount of gas phase, but such a problem does not occur if only a liquid layer is used.

Thus, the heat pipe function of each heat transfer tube (the phase change of the refrigerant, especially the heat transfer function by evaporation and condensation)
Since the amount of heat transferred by the heat becomes uniform between the heat transfer tubes,
Uniform heat transfer can be performed in the entire heat exchanger 300d, and the inconvenience of air as the first fluid and the second fluid passing without being involved in heat transfer can be prevented. Therefore, in the dehumidifying air conditioner using the heat exchanger 300d, the heat exchange efficiency between the processing air as the first fluid and the cooling medium (outside air) or the regenerated air as the second fluid is improved and the operation reliability is improved. Improvement can be achieved.

Hereinafter, embodiments of the present invention will be described using specific numerical values. The calculation condition is that the heat transfer amount is 2USR
t, the evaporation temperature is 10 ° C., the economizer temperature is 40 ° C., the condensation temperature is 65 ° C., the refrigerant is HFC134a, and the diameter of the pipe is 12 mm. Further, the inner diameter of the heat transfer tube is 8.3 mm, and the number of heat transfer tubes is 40 (in the case of a three-stage arrangement as shown in FIG. 8,
For example, each row has a staggered arrangement of 13, 14, and 13). Here, by reading and calculating the enthalpy of each point with reference to the Mollier diagram of FIG. 10, the refrigerant circulation amount is:
2 × 3024 / (138.83-113.51) = 17
1.23 kg / h = 0.0476 kg / s.

Comparative Example: The gas-liquid two-phase refrigerant expanded by the expansion valve is supplied to the heat exchanger 1 using a distributor.
It branches into a number of heat transfer tubes configured in the path. In the second heat exchanger, the number of branches is large because the heat transfer tubes must be arranged in one pass.

Dryness immediately after the expansion valve: (122.97-1)
13.51) /39.42=0.242 (39.42)
Is the enthalpy difference between points h and g in FIG. 10) Specific volume of the two-phase mixed refrigerant immediately after the expansion valve: 0.000872
61 × (1−0.242) + 0.020032 × 0.2
42) = 0.00551 m ³ / kg Flow rate 1 (out of 3 pipes with an inner diameter of 12 mm): 0.00551
× 0.0476 × 4 / (0.012 × 0.012 × 3.
14 × 3) = 0.773 m / s Flow velocity 2 (40 tubes in heat transfer tube with inner diameter 8.3): 0.005
51 × 0.0476 × 4 / (0.0083 × 0.008
(3 × 3.14 × 40) = 0.121 m / s At a flow rate of 1, the refrigerant flows in the pipe in a substantially uniform gas-liquid mixture, but at a flow rate of 2 branching to the heat transfer tube, the flow rate is too slow. Is a flow in which two gas-liquid phases are separated by gravity, and a gas phase flows upward and a liquid phase flows downward. Since the flow velocity after branching becomes extremely slow as described above, it is difficult to distribute the gas-phase refrigerant in a state of being uniformly mixed with the liquid-phase refrigerant. As a result, the flow looks different before and after the branch,
Refrigerant cannot be distributed uniformly.

Example: Dryness immediately after expansion valve: 0 Specific volume of liquid refrigerant immediately after expansion valve: 0.00082611 m
³ / kg Flow rate 3 (out of three pipes with an inner diameter of 12 mm): 0.00087
261 * 0.0476 (1-0.242) * 4 / (0.
012 x 0.012 x 3.14 x 3) = 0.0928 m
/ S Flow rate 4 (40 tubes, inside 8.3 heat transfer tube): 0.000
87261 × 0.0476 (1-0.242) × 4 /
(0.0083 × 0.0083 × 3.14 × 40) =
0.0146 m / s As described above, both the flow velocity 3 and the flow velocity 4 are slow and only the liquid phase flows, so that they can be uniformly distributed to the heat transfer tubes.

FIG. 11 shows an example of a typical mechanical arrangement of a dehumidifying air conditioner according to the third embodiment having the flow shown in FIG. In the example shown in this figure, the heat exchanger 300 in the first embodiment described with reference to FIG.
0d. Other basic configurations are the same as those in FIG. Also in this mechanical arrangement, the heat exchanger 300d is disposed vertically above the desiccant rotor 103 and vertically below the cooler 210.
The heater 220 is connected to the desiccant rotor 10 placed horizontally beside the cooler 210 and with the rotation axis oriented vertically.
3 above. The gas-liquid separator 350 is connected to the first section 310 of the heat exchanger 300 d below the heater 220.
Are arranged in the vicinity. The second section 320 is placed outside the air circulation region of the desiccant rotor 103, and is disposed in a processing air flow path that flows upward from below vertically.

In such a structure, the refrigerant condensed in the heater (refrigerant condenser) 220 flows into the gas-liquid separator 350 through the expansion valve 360, and the separated refrigerant liquid is supplied to the first liquid refrigerant.
Into the evaporation section in the compartment. Then it is condensed in the condensing section. The gas-phase refrigerant separated by the gas-liquid separator 350 is directly led to the heat exchange tube in the second section, where it is condensed.

[0098]

According to the present invention, a processing air cooler is provided. The processing air cooler is configured to cool the processing air by evaporating the refrigerant, and to cool and condense the evaporated refrigerant by the cooling fluid. Since the evaporation heat transfer and the condensation heat transfer having high coefficients can be used, heat transfer between the processing air and the cooling fluid can be achieved with a high heat transfer coefficient. Further, since the heat transfer between the processing air and the cooling fluid is performed via the refrigerant, the components of the dehumidifying air conditioner can be easily arranged.

When a heat pump is constituted by including a refrigerant evaporator, a compressor and a condenser, and the refrigerant condensed by the condenser is supplied to the processing air cooler, the refrigerant used in the processing air cooler is reduced. The refrigerant used in the heat pump can be shared, and the efficiency of the dehumidifying air conditioner can be significantly increased.

[Brief description of the drawings]

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

FIG. 2 is a schematic sectional view of a heat exchanger suitable for use in a heat pump used in the dehumidifying air conditioner of FIG.

FIG. 3 is a Mollier diagram of a heat pump used in the dehumidifying air conditioner of FIG.

FIG. 4 is a psychrometric chart for explaining the operation of the dehumidifying air conditioner of FIG. 1;

FIG. 5 is a flowchart of a dehumidifying air conditioner according to a second embodiment of the present invention.

FIG. 6 is a table showing an operation mode of a dehumidifying air conditioner according to an embodiment of the present invention and an operation of each device.

FIG. 7 is a schematic front sectional view showing an example of the actual structure of the dehumidifying air conditioner according to the first embodiment of the present invention.

FIG. 8 is a schematic structural view of a heat exchanger suitable for use in a heat pump used in a dehumidifying air conditioner according to a third embodiment.

FIG. 9 is a flowchart of a dehumidifying air conditioner according to a third embodiment of the present invention.

FIG. 10 is a Mollier diagram of a heat pump used in the dehumidifying air conditioner according to the third embodiment.

FIG. 11 is a schematic front sectional view showing an example of an actual structure of a dehumidifying air conditioner according to a third embodiment of the present invention.

FIG. 12 is a flowchart of a conventional dehumidifying air conditioner.

FIG. 13 is a psychrometric chart for explaining the operation of the conventional dehumidifying air conditioner shown in FIG.

FIG. 14 is a Mollier diagram of a heat pump used in the conventional dehumidifying air conditioner shown in FIG.

FIG. 15 is a perspective view showing an example of the structure of a desiccant rotor.

FIG. 16 is a perspective view showing an example of a cross-flow heat exchanger.

[Explanation of symbols]

101 Air-conditioned space 102, 140, 160 Blower 103 Desiccant rotor 121 Heat exchanger 165 Vaporization humidifier 210 Refrigerant evaporator 220 Refrigerant condenser 251A, 251B, 251C Evaporation section 252A, 252B, 252C, 252D Condensing section 230A, 230B, 230C 240A, 240B, 240C Restrictor 260 Compressor 300, 300b, 300d Process air cooler 310 First section 320 Second section 325 Sprinkling pipe 350 Gas-liquid separator 470 Cooling tower 501, 502, 503 Filter 700 Cabinet HP1, HP2 , HP3 heat pump

Claims (4)

(57) [Claims] A moisture adsorbing device having a desiccant for adsorbing moisture in the processing air; and a water adsorbing device provided on a downstream side of the flow of the processing air with respect to the water adsorbing device, wherein the moisture is adsorbed by the desiccant. A processing air cooler for cooling the processing air; the processing air cooler cools the processing air by evaporating a refrigerant, and flows the evaporated refrigerant in one direction as a whole in the processing air cooler. A dehumidifying air conditioner configured to be cooled and condensed by a cooling fluid on a downstream side; 2. A refrigerant evaporator for evaporating the refrigerant condensed by the processing air cooler and further cooling the processing air cooled by the processing air cooler; and evaporating to a gas by the refrigerant evaporator. A booster for boosting the refrigerant; and a condenser for cooling and condensing the refrigerant pressurized by the booster with regeneration air; supplying the refrigerant condensed in the condenser to the processing air cooler. The dehumidifying air conditioner according to claim 1, wherein: 3. The gas-liquid separator according to claim 1, further comprising a gas-liquid separator for separating the refrigerant into a refrigerant liquid and a refrigerant gas between the condenser and the processing air cooler. Dehumidifying air conditioner. 4. A first step of cooling the processing air with a refrigerant that evaporates at a first pressure; a second step of increasing the pressure of the refrigerant evaporated in the first step to a second pressure; A third step of heating the regenerated air for regenerating the desiccant with the refrigerant condensing at a pressure of; and a fourth step of desorbing moisture from the desiccant with the regenerated air heated in the third step to regenerate the desiccant. A fifth step of adsorbing moisture in the treated air with the desiccant regenerated in the fourth step;
A sixth step of evaporating the refrigerant condensed in the third step at an intermediate pressure between the first pressure and the second pressure, and cooling the processing air to which the moisture has been adsorbed in the fifth step. And a seventh step of condensing the refrigerant evaporated at the intermediate pressure at substantially the same pressure as the intermediate pressure; a method of dehumidifying process air.