JP2000111094A - Dehumidifier/air conditioner and dehumidifying/air conditioning system - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a compact dehumidifier/air conditioner and a dehumidifying/air conditioning system of low heat carrying power. SOLUTION: The dehumidifier/air conditioner comprises a moisture absorber 103 for the air to be processed having desiccant adsorbing/desorbing moisture of regenerated air, a first heat exchanger 120 for bringing a gas phase hot heating medium into liquid phase through heat exchange with the regenerated air disposed on the upstream side of the moisture absorber in the direction of regenerated air flow, and a second heat exchanger 220 for exchange heat with the hot heating medium brought into liquid phase through the first heat exchanger 120 disposed on the downstream side of the moisture absorber 103 in the direction of regenerated air flow. A part of heat used by the first heat exchanger 120 for heating the regenerated air can be recovered from the processed air by the second heat exchanger 220. Heat is carried through the use of phase change of heating medium.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

The present invention relates to a dehumidifying air-conditioning apparatus and a dehumidifying air-conditioning system, and more particularly to a dehumidifying air-conditioning apparatus having a desiccant and a dehumidifying air-conditioning system including such a dehumidifying air-conditioning apparatus.

[0002]

2. Description of the Related Art As shown in FIG. 11, there has been a desiccant air conditioner using a low heat source and a high heat source. In this air conditioner, the path of the processing air A in which moisture is adsorbed by the desiccant rotor 103, and after being heated by the high heat source, pass through the desiccant rotor 103 after adsorbing the moisture to desorb and regenerate moisture in the desiccant. And the path of the regenerated air B. Here, in order to heat the regenerated air with the high heat source, the hot water is supplied to the heat exchanger 120 through the path 151 connected to the high heat source supply port 42, and the hot water returns to the high heat source through the path 152. It is returned to the mouth 43.

[0003] The air conditioner shown in FIG. 11 is arranged between the treated air to which moisture is adsorbed and the regenerated air before regenerating the desiccant (desiccant) of the desiccant rotor 103 and before being heated by the heat exchanger 120. Has a sensible heat exchanger 104, and the regeneration air is heated to some extent by the heat exchanger 104 before being heated by the heat exchanger 120, and the treated air dried by desiccant is cooled to some extent by the heat exchanger 104. Thereafter, the heat is supplied from the low heat source supply port 40 to the heat exchanger 115 through the path 161, and is further cooled by the low heat source discharged to the low heat source return port 41 through the path 162. In the conventional example shown in FIG. 11, the processing air that has exited the heat exchanger 115 is humidified by the humidifier 106, and is supplied to the air-conditioned space 101 while increasing the humidity and simultaneously decreasing the dry bulb temperature.

In this air conditioner, the sensible heat exchanger 104 exchanges heat between the processing air after leaving the desiccant rotor 103 and the regeneration air before entering the heat exchanger 120.
However, the energy saving effect has been enhanced. The high heat source and the low heat source of the conventional apparatus shown in FIG. 11 are provided by a compression heat pump (not shown).

FIG. 12 is a Mollier diagram of a compression heat pump used in the apparatus shown in FIG. This is a Mollier diagram when HFC134a is used as a refrigerant.
Point a indicates the state of the refrigerant evaporated by the evaporator of the heat pump, and is in the state of a saturated gas. The pressure is 4.2kg / c
m ² , temperature 10 ° C., enthalpy 148.83 kca
1 / kg. The state where this gas is sucked and compressed by the compressor of the heat pump and the state at the discharge port of the compressor are indicated by a point b. In this state, the pressure is 24.1 kg / cm ² ,
The temperature is 85 ° C., and the state is a superheated gas. This refrigerant gas is cooled by hot water in the condenser of the heat pump (heats the hot water), and reaches point c on the Mollier diagram. This point is a state of a saturated gas, and the pressure is 24.1 kg / c.
m ² , temperature is 75 ° C. Under this pressure, heat is further removed by hot water and condensed to reach point d. This point is a state of the saturated liquid, and the pressure and the temperature are the same as those of the point c, and the pressure is 2
4.1 kg / cm ² , temperature 75 ° C. and enthalpy 127.13 kcal / kg. This refrigerant liquid is
The pressure is reduced by the expansion valve, and the saturation pressure is 4.2 ° C. at a temperature of 10 ° C.
The pressure is reduced to kg / cm ² and reaches the above-mentioned evaporator as a mixture of a refrigerant liquid and a gas at 10 ° C., where heat is taken from cold water and evaporated to become a saturated gas in the state of the point a on the Mollier diagram. Is sucked into the compressor again, and the above cycle is repeated. FIG. 13 shows how the temperature changes in the heat exchange between the refrigerant and the hot water as the heating medium.

[0006] The chilled water as the cooled cooling medium is supplied to the heat exchanger 115 via a path 161 and is supplied to a path 162.
To the heat pump evaporator. The hot water heated to about 70 ° C. is supplied to the heat exchanger 12 through a path 151.
0, where it is cooled to about 60-65 ° C.
Return to the heat pump condenser via line 152. Further, as the sensible heat exchanger 104, a rotary heat exchanger as shown in FIG. 11 or a cross-flow heat exchanger in which process air and regeneration air flow orthogonally is used.

[0007]

According to the conventional air conditioning system as described above, the sensible heat exchanger 104 for preliminarily cooling the processing air before cooling it with the cooler 115 plays an important role. However, the sensible heat exchanger 104 generally occupies a large volume in the system, which makes the system configuration difficult and, in turn, necessitates an increase in the size of the system. In addition, the amount of hot or cold water is large, and especially when a dehumidifying air conditioner is used for air conditioning of a building, etc., the diameter of the hot or cold water piping for circulating hot or cold water is large, making construction difficult. The power of the pump that conveys the oil increased, and it was a win.

Accordingly, an object of the present invention is to provide a compact dehumidifying air conditioner, and a dehumidifying air conditioner and a dehumidifying air conditioning system with a small transfer power of a heating medium or a cooling medium.

[0009]

In order to achieve the above object, a dehumidifying air conditioner according to the present invention, as shown in FIG. 1, adsorbs moisture in processing air and removes moisture by regenerating air. Moisture adsorption device 1 having desiccant to be desorbed
03, a first heat exchanger for exchanging heat between the regeneration air and a gaseous heating medium, wherein the first heat exchanger is provided upstream of the flow of the regeneration air with respect to the moisture adsorption device. A second heat exchanger for exchanging heat between the processing air and the heating medium heat-exchanged in the first heat exchanger 120; And a second heat exchanger 220 provided on the downstream side of the flow. Typically, the heating medium that has exchanged heat in the first heat exchanger 120 condenses into a liquid phase, and the second heat exchanger 220 separates the heating medium that has become the liquid phase with the processing air. It is configured to exchange heat.

According to this structure, the heating medium is supplied to the first
And the second heat exchanger, so that the heat corresponding to a part of the heat used for heating the regeneration air in the first heat exchanger is passed through the second heat exchanger. Can be recovered from process air. Also, typically, heat is transferred utilizing the phase change of the heating medium.

According to a second aspect of the present invention, in the above-mentioned apparatus, the third heat exchanger for exchanging heat between the processing air and the liquid-phase cooling medium is provided. And a third heat exchanger 115 provided on the downstream side of the flow of the processing air. At this time,
The third heat exchanger 115 further cools the processing air cooled by the second heat exchanger 220.

Further, as described in claim 3, claim 1
Alternatively, in the dehumidifying air conditioner according to claim 2, as shown in FIG. 8, the first heat exchanger 120 and the second heat exchanger 220
And a switching device 170 that switches the flow of the heating medium heat-exchanged by the first heat exchanger 120. With this configuration, the flow of the heating medium can be switched by the switching device that switches the flow of the heating medium, so that the heating medium can bypass the second heat exchanger 220.

According to another aspect of the present invention, the above object is achieved.
As shown in FIG. 10, the dehumidifying air-conditioning system according to the invention according to the present invention includes: the dehumidifying air-conditioning device according to claim 2; and a cooling medium supplied to the third heat exchanger 115 to the first heat exchanger 120. A heat pump 1 for pumping heat to a supplied heating medium is provided.

With this configuration, since the heat pump is provided, the heat taken in from the cold heat medium by the third heat exchanger can be pumped up and given to the warm heat medium by the first heat exchanger. In addition, heat is transferred by using the phase change of the heat medium, and a natural circulation action typically by gravity can be used, so that the transfer power is extremely reduced.

[0015] Also, as described in claim 5, claim 4
In the dehumidifying air-conditioning system described in 1 above, one heat pump 1
In contrast, a plurality of dehumidifying air conditioners may be provided. With this configuration, it is possible to configure a system in which a plurality of dehumidifying air conditioners use a heating medium that is intensively heated by one heat pump and a cooling medium that is intensively cooled.

Further, as described in claim 6, in the dehumidifying air conditioning system according to claim 4 or 5, the heat pump 1 comprises: a fourth heat exchanger 35 for applying heat to the heating medium; Fifth heat exchanger 2 for removing heat from cold medium
5 may be provided.

Further, as described in claim 7, claim 6
In the dehumidifying air conditioning system described in the above, the fourth heat exchanger 35
Is preferably installed vertically below the dehumidifying air conditioner, and the fifth heat exchanger 25 is preferably installed vertically above the dehumidifying air conditioner.

With such a configuration, typically, in the fourth heat exchanger, the heating medium is heated and vaporized, but the vaporized heating medium is lighter than the liquid heating medium, so that it is relatively vertically heated by natural circulation. Sent to the dehumidifying air conditioner in the upper direction,
Typically, in the fifth heat exchanger, the cooling medium is deprived of heat and liquefied. However, since the liquefied cooling medium is heavier than the gas cooling medium, it is sent to the dehumidifying air conditioner relatively vertically downward by natural circulation. Can be

Further, as described in claim 8, the dehumidifying air-conditioning system according to any one of claims 4 to 7 may further include a refrigerator 9 for removing heat from the cooling medium. . In this case, since the refrigerator 9 is provided, when the cooling load is large, it can be dealt with by operating this in addition to the heat pump 1. At this time, the refrigerator may be provided anywhere in the cooling medium path, but is typically connected to the fifth heat exchanger 25, and for example, the evaporator of the refrigerator may be incorporated in the fifth heat exchanger. Good.

[0020]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Hereinafter, a first embodiment of the present invention will be described 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.

Referring to the flowchart of FIG. 1, the first embodiment of the present invention will be described.
The configuration of the dehumidifying air conditioner according to the embodiment will be described. This air conditioner lowers the humidity of the processing air with a desiccant (desiccant), and a plurality of air conditioning spaces 6 to which the processing air is supplied.
1A to 1E are maintained in a comfortable environment. In the figure, a blower 102 for circulating the processing air, a desiccant rotor 103 filled with a desiccant, a second heat exchanger 220 of the present invention, a third heat exchanger along the path of the processing air A from the air-conditioned spaces 61A to 61E. The heat exchanger 115 and the humidifier 106 are arranged in this order, and are configured to return the processing air to the air-conditioned spaces 61A to 61E.

Further, the first heat exchanger 120 of the present invention for heating the regeneration air before entering the desiccant rotor 103 along the path of the regeneration air B from the outdoor OA, the desiccant rotor 103, and the circulation of the regeneration air. Are arranged in this order, and are configured to exhaust used regeneration air to the outside.

A pipe 151 for introducing a gaseous heating medium is shown in FIG.
The heat pump HP as a heat medium supply device (to be described later) is connected to the heat medium supply port 42 of the fourth heat exchanger 35 and the gas phase heat medium inlet of the heat exchanger 120. The heat exchanger 120 is a counter-flow heat exchanger configured to exchange heat between the gas-phase heating medium and the regeneration air in counter-flow.
A heating medium outlet of the heat exchanger 120 is connected to a heating medium inlet of the heat exchanger 220 by a heating medium pipe. The heat exchanger 220 is also configured to exchange heat between the heating medium and the processing air in counterflow. The heating medium outlet of the heat exchanger 220 is connected to the heating medium return port 43 of the heat pump by a heating medium pipe 152 (FIG. 2).

A cooling medium pipe 1 for introducing a cooling medium in a liquid phase.
61 is connected to the cooling medium supply port 40 of the heat pump HP and the cooling medium inlet of the heat exchanger 115. The third heat exchanger 115 is configured so that the processing air to be heat-exchanged and the cooling medium exchange heat in counterflow. The cooling medium outlet of the heat exchanger 115 is connected to the cooling medium return port 41 of the heat pump by a cooling medium pipe 162 (FIG. 2).

Desiccant rotor 10 as a moisture adsorption device
3 is connected to a geared motor 105, which is a driving machine that rotates the motor at a rate of about one rotation in a few minutes, by a transmission device such as a chain or a belt.

Next, an example of a heat pump that can be used in the apparatus shown in FIG. 1 will be described with reference to the flowchart of FIG. In the figure, a discharge port of the refrigerant compressor 3 is connected to a fourth heat exchanger 35 which is a refrigerant condenser by a refrigerant gas pipe, and a fourth heat exchanger is provided below the fourth heat exchanger 35. There is an outlet for the refrigerant liquid condensed in 35, and this outlet is connected to the fifth refrigerant evaporator.
Is connected to the heat exchanger 25 by a refrigerant pipe, and an expansion valve 7 as a throttle is provided in the middle of the refrigerant pipe. Above the fifth heat exchanger 25, the fifth heat exchanger 2
There is an outlet for the refrigerant gas evaporated in 5, and this port and the suction port of the compressor 3 are connected by a refrigerant gas pipe. Here, typically, the fifth heat exchanger 25 is installed vertically above the fourth heat exchanger 35.

As shown in FIG. 2, the fourth heat exchanger 35 has, for example, a shell-and-tube structure, in which a refrigerant, which is a working medium of the heat pump HP, flows and condenses. The liquid phase heating medium contacts the outside of the tube and evaporates. A heating medium supply port 42 for supplying a gas phase heating medium from the heat pump HP to the outside is provided at the upper part of the shell, and a heating medium return port 43 for returning the liquid phase heating medium from the outside to the heat pump HP is provided at the bottom of the shell. ing. A heating medium pipe 151 is connected to the heating medium supply port 42, and a heating medium pipe 152 is connected to the heating medium return port 43.

The fifth heat exchanger 25 also has, for example, a shell-and-tube structure, in which a refrigerant as a working medium of the heat pump HP flows and evaporates, and a heating medium flows out of the shell-side tube. Contact and condense. At the lower part of the shell, heat pump H
A cooling medium supply port 40 for supplying the cooling medium from the P to the outside, and a cooling medium return port 41 for returning the gas phase cooling medium from the outside to the heat pump HP are provided at the upper part of the shell. A cooling medium pipe 161 is connected to the cooling medium supply port 40, and a cooling medium pipe 162 is connected to the cooling medium return port 41.

In such a configuration, the fifth heat exchanger 25 is supplied by the gaseous cooling medium from the cooling medium return port 41.
The refrigerant gas heated and evaporated in the compressor is sucked into the compressor 3, compressed, and discharged to the fourth heat exchanger 35. 5th
The cooling medium that has been cooled and condensed by the evaporation of the refrigerant in the heat exchanger 25 is supplied from the cooling medium supply port 40 to the outside.

In the fourth heat exchanger 35, the refrigerant liquid cooled and condensed in the fourth heat exchanger 35 by the evaporation of the liquid-phase heating medium from the heating medium return port 43 passes through the throttle 7. The pressure is reduced and supplied to the fifth heat exchanger 25. While the fourth
The liquid-phase heating medium heated by the condensation of the refrigerant in the heat exchanger 35 becomes a gaseous phase and is supplied from the heating medium supply port 42 to the outside. The subcooler 36 that exchanges heat between the condensed refrigerant liquid from the fourth heat exchanger 35 and the liquid-phase heating medium that returns to the fourth heat exchanger, and supercools the refrigerant liquid, performs the fourth heat exchange. It is provided adjacent to the vessel 35.

Referring to the psychrometric chart of FIG. 3, the operation of the first embodiment shown in FIG. 1 will be described for an example in which a specific temperature is considered. FIG. 1 is referred to as appropriate for the configuration. In FIG. 3, alphabet symbols K to N, P, Q, R,
T and U indicate the state of air in each part. 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. 3, the processing air (state K) at about 27 ° C. from the air-conditioned spaces 61A to 61E passes through the processing air path 107,
02, and is sent to the desiccant rotor 103, which is a moisture adsorption device, through the processing air path 108. Here, the moisture is adsorbed by the desiccant 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 of about 50 ° C. This air is sent to the second heat exchanger 220 through the processing air path 109, where it is kept at a constant absolute humidity by a heating medium (condensed and supercooled in the first heat exchanger 120 as described later). It is cooled to about 38 ° C. state M air and enters the third heat exchanger 115 through the path 110. Here, the absolute humidity is also constant, and it is further cooled by a cooling medium to about 15 ° C.
It becomes the air of the state N. This air is sent to the humidifier 106 through the duct 111, where it changes in enthalpy, raises the absolute humidity, lowers the dry-bulb temperature, and becomes air in state P. Processing air S at temperature
As A, the air-conditioned spaces 61A to 61E
Is returned to.

Next, the flow of the regeneration air B will be described. In FIG. 3, the regeneration air of about 32 ° C. from the outdoor OA (state Q)
Is sucked through the regeneration air path 125 and sent to the first heat exchanger 120. Here the heat pump HP
The dry-bulb temperature is increased by heat exchange with a high-temperature gas-phase heating medium from the air to form air in a state T of about 70 ° C.

The regenerated air in the state T reaches the desiccant rotor 103 through the path 128, where it deprives the desiccant of water and regenerates it, thereby increasing the absolute humidity and drying itself due to the desiccant moisture desorption heat. The ball temperature is lowered to reach the state U. This air is sucked into the blower 140 for circulating the regeneration air through the passage 129, and is exhausted EX through the passage 130.

Here, the relationship between the heat exchanger 120 and the heat exchanger 220 will be described with reference to FIG. First, the heat exchanger 12
The heating medium condensed at a saturation temperature of about 72 ° C. at 0 and becomes liquid by condensation is further subcooled to about 36 ° C.
The 36 ° C. heating medium itself raises the temperature to about 47 ° C. while cooling the processing air as described above.

This is heat recovery for the heating medium.
With the heat recovered in this way, the heating medium returns to the heat pump HP (FIG. 2) in the liquid phase, where the fourth heat exchanger 3
The mixture is heated and evaporated at 5, and is supplied to the heat exchanger 120 in a gaseous state at about 72 ° C. as described above. Then, the regeneration air is heated. As described above, the regeneration air is at about 32 ° C.
To about 70 ° C. Of this temperature rise,
As shown in FIG. 3, the amount of heat recovered by the heat exchanger 220 from the treated air is about 46 ° C. from the state Q of about 32 ° C.
In the state R.

In the heat exchanger 120, the heating medium at about 72 ° C. exchanges heat with the outside air at about 32 ° C., which is used as regeneration air, in a counterflow. The heating medium is initially in the gas phase and first condenses at about 72 ° C. The heating medium in the liquid phase by condensation is supercooled from about 72 ° C. to about 36 ° C. During this time, the regeneration air that exchanges heat with the heating medium is heated from about 32 ° C. to about 7
The temperature rises to 0 ° C.

Next, as described above, the heating medium supercooled to about 36 ° C. exchanges heat in the heat exchanger 220 in a counterflow with the processing air. The heating medium is heated from about 36 ° C to about 47 ° C. During this time, the temperature of the process air that exchanges heat with the heating medium drops from about 50 ° C. to about 38 ° C.

The above processing is performed for a plurality of air-conditioned spaces 61A to 61E.
Although it may be intensively performed by one dehumidifying air conditioner provided for the whole, typically, it is configured to be performed by an individual dehumidifying air conditioner provided for each air conditioning space.

Next, a refrigerant cycle of the heat pump HP will be described with reference to FIG. FIG. 5 shows the refrigerant HFC134a
FIG. 4 is a Mollier diagram when using. In this diagram, the horizontal axis is enthalpy and the vertical axis is pressure. For the configuration of the heat pump HP, FIG. 2 is appropriately referred to.

In the figure, point a is the third heat exchanger 115 of FIG.
5 is a state of a refrigerant outlet of the fifth heat exchanger 25 (FIG. 2) for supplying a cooling medium to the air, and is in a state of a saturated gas. The pressure is about 4.2 kg / cm ² , the temperature is about 10 ° C., and the enthalpy is about 148.83 kcal / kg. The state where this gas is sucked and compressed by the compressor 3 and the state at the discharge port of the compressor 3 are indicated by a point b. In this state, the pressure is about 24.1 kg
/ Cm ² , at a temperature of about 85 ° C., and in a superheated gas state.

This refrigerant gas is cooled in the fourth heat exchanger 35 and reaches a point c on the Mollier diagram. This point is a saturated gas state, the pressure is about 24.1 kg / cm ² , and the temperature is about 75 ° 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 about 24.1 kg / cm ² ,
The temperature is about 75 ° C and the enthalpy is about 127.13k
cal / kg. The temperature of the liquid phase heating medium returning to the fourth heat exchanger 35 is about 47 ° C. as described above. The subcooler 36 attached to the fourth heat exchanger 35 exchanges heat with the heating medium, and the refrigerant liquid is subcooled. Thus, the refrigerant liquid is supercooled to a state e of about 55 ° C. The enthalpy at point e is about 119.05 kcal / kg
It is. The refrigerant liquid in this state is reduced in pressure through the throttle 7 and returns to the fifth heat exchanger 25. This point is indicated by f. The refrigerant liquid removes heat from the cooling medium and evaporates and returns from point f to point a. Thus, the refrigerant cycle is repeated.

In the case of this embodiment, the cooling effect is (148.8) as compared with the conventional example shown in the Mollier diagram of FIG.
3-119.05) / (148.83-127.13)
= 29.78 / 21.70 = 1.37, an improvement of about 37%. Such an increase in the cooling effect leads to the movement of the point N to the left (lower dry-bulb temperature) in the psychrometric chart of FIG. 3, thereby increasing the heating capacity of the heating medium,
The efficiency can be increased, the size of the device can be reduced, and the cost can be reduced. Also, here, the case of the compression heat pump has been described, but even in the case of using the absorption heat pump, the sensible heat of the condensed refrigerant is similarly recovered, thereby increasing the cooling effect and increasing the heating capacity of the heating medium. .

Next, with reference to FIG. 6, a description will be given of a change in temperature with respect to a change in enthalpy of the refrigerant and the heating medium in the fourth heat exchanger 35 in the embodiment described above. First, attention is paid to changes in the enthalpy and temperature of the refrigerant. In the figure, the refrigerant is supplied to the fourth heat exchanger 35 in a superheated state (temperature is about 85 ° C., enthalpy is about 158.50 kcal / kg) shown at point b in FIG. This refrigerant gas is cooled by the heating medium, and the state of the saturated gas at the point c shown in FIG.
Enthalpy of about 154.86 kcal / kg). From here, the temperature is kept constant at about 75 ° C. and the heat is taken away, and the enthalpy is increased from about 154.86 kcal / kg to about 127.13 kc.
al / kg. FIG. 5 shows the state of the saturated liquid at point d. From here, it is further cooled down to about 55 ° C. by a heating medium, and reaches a point e shown in FIG.

While the state of the refrigerant changes as described above, the counter-current heating medium is first supplied to the subcooler 36 at about 47 ° C., and starts to exchange heat with the refrigerant at a point corresponding to the point e. Between the points e and d of the refrigerant (actually the point d
At a point corresponding to (). The heating medium exits the subcooler 36, enters the fourth heat exchanger (condenser) 35, and exchanges heat toward a point corresponding to the point d of the refrigerant, and the temperature of the heating medium rises to about 72 ° C. Start evaporation. Thus, the heating medium is vaporized.

The heating medium is supplied in a gas phase from the fourth heat exchanger 35, which is a condenser of the heat pump HP, to the dehumidifying air conditioner and is returned in the liquid phase from the dehumidifying air conditioner. In addition, if the fourth heat exchanger 35 is installed vertically below the dehumidifying air conditioner, the liquid phase heating medium returns to the fourth heat exchanger 35 by gravity, and the gas phase heating medium Can be supplied from the fourth heat exchanger 35 to the dehumidifying air conditioner with a slight pressure difference. That is, since the heating medium flows naturally by the action of gravity, the heat transfer power is extremely small. Further, in particular, the diameter of the pipe 152 through which the liquid-phase heating medium passes can be reduced, and the workability can be improved.

In the present embodiment, since the second heat exchanger 220, which is a heat exchanger for the heating medium, is provided in the processing air system, the operation in the heating operation mode can be performed. In the heating operation mode, the regeneration air is stopped. That is, for example, the blower 140 may be stopped. Then, as the low heat source of the heat pump, for example, outside air may be used. For this purpose, heat from the outside air may be introduced into the fifth heat exchanger 25 using a low heat source heat exchanger (not shown). Alternatively, a heat exchange unit for a high heat source (not shown) is provided in the fourth heat exchanger 35,
What is necessary is just to be able to heat the heating medium.

The cooling medium is supplied from the fifth heat exchanger 25, which is the evaporator of the heat pump HP, to the dehumidifying air conditioner in a liquid phase, and is returned from the dehumidifying air conditioner in a gas phase. If the fifth heat exchanger 25 is installed vertically above the dehumidifying air conditioner, the cooling medium in the liquid phase is supplied from the fifth heat exchanger 25 to the dehumidifying air conditioner by gravity. The vapor-phase cooling medium vaporized by the dehumidifying air conditioner returns to the fifth heat exchanger 25 with a slight pressure difference.
In other words, the cooling medium flows naturally by the action of gravity,
Very little heat transfer power is required. In addition, the diameter of the pipe 161 through which the cooling medium of the liquid phase passes can be reduced, and the workability can be improved.

Next, an example of the mechanical arrangement of the dehumidifying air conditioner described above will be described with reference to FIG. In FIG.
The equipment constituting the apparatus is housed in a rectangular parallelepiped cabinet 700 made of a thin steel plate, for example. Outside air OA suction port used as regeneration air is open at the lower side in the vertical direction, the outside air flows upward from the lower part in the vertical direction, during which it passes through the heat exchanger 120, the desiccant rotor 103, and by the blower 140, Above the cabinet 700, it is arranged so as to be exhausted from an opening of the opened regeneration air. Desiccant rotor 103 is arranged with its rotation axis directed in the vertical direction.

Further, a central portion of the upper surface of the cabinet 700,
An inlet of the processing air RA is open adjacent to the outside air OA exhaust port, a blower 102 is disposed below the outlet, a desiccant rotor 103 is further below the heat exchanger RA, a heat exchanger 220 is below the desiccant rotor 103, and Heat exchanger 11
5 are arranged. The processing air that has passed through them flows sideways at the bottom of the cabinet 700 and changes its flow direction upward, and from the opening provided on the upper surface of the cabinet 700,
It is configured to be supplied to the air-conditioned space. In the drawing, a filter 171 is provided at an outside air opening, and a filter 170 is provided at a processing air intake opening. Humidifier 1
Reference numeral 06 is provided on the downstream side of the heat exchanger 115 in the processing air path.

As described above, the first embodiment does not require the rotary or cross-flow heat exchanger 104 (FIG. 11) used in the conventional apparatus, and is a compact dehumidifying air conditioner. It can be a device.

Next, the configuration of a dehumidifying air conditioner according to a second embodiment of the present invention will be described with reference to the flowchart of FIG. The difference between this air conditioner and the first embodiment is that a switching valve as the switching device of the present invention is provided in the path of the heating medium so that the dehumidifying operation can be easily performed. That is, as shown in FIG. 8, a three-way valve 170 is provided in the heating medium path between the heating medium outlet of the heat exchanger 120 and the heating medium inlet of the heat exchanger 220. 3-way valve 1
A path 153 is connected to the third port of 70, and the path 153 joins the path 152. With such a configuration, during the cooling operation, the three-way valve 170 closes the path 153, and the heat exchanger 120 is closed as in the case of the first embodiment.
The heating medium that has passed through is all operated to enter the heat exchanger 220.

When the device is operated for dehumidification, the three-way valve 1
The heating medium having passed through the heat exchanger 120 by switching 70 is caused to flow to the path 152 through the path 153 bypassing the heat exchanger 220 and to the heating medium return port 43 of the heat pump HP. At this time, the heat of the heating medium is used only for heating the regenerated air in the heat exchanger 120, and the processing air is not cooled in the heat exchanger 220 but is cooled in the heat exchanger 115 only by the cooling medium. It is. In the dehumidifying operation, the humidifier 106 is also stopped.

The above operation will be described with reference to the psychrometric chart of FIG. In FIG. 9, alphabet symbols K to N, P, Q,
R, T, and U indicate the state of air in each part. This symbol corresponds to the alphabet circled in the flowchart of FIG.

First, the flow of the processing air A will be described. In FIG. 9, the processing air at approximately 27 ° C. (state K) from the air-conditioned spaces 61A to 61E is supplied to the desiccant rotor 1 which is a moisture adsorbing device.
It is sent to 03. Here, moisture is adsorbed by the desiccant to lower the absolute humidity, and the dry bulb temperature is increased by the heat of adsorption of the desiccant to reach the state L. Although this air is sent to the second heat exchanger 220, the heating medium does not flow here, so that the air passes through (the state M is shown near the state L for easy understanding, but actually overlaps). 3 heat exchanger 115. Here, the absolute humidity is constant, and the air is cooled by the cooling medium to be in the state N. Humidifier 106
Is also stopped, the air in the state N is supplied to the air-conditioned space 61A-
E. In FIG. 9, the points of the state P are shown near the state N for easy understanding, but they actually overlap. The air in the state N has a dry bulb temperature substantially equal to the air in the state K and has a low absolute humidity.

In the above description, the three-way valve switches whether the entire amount of the heating medium flows to the heat exchanger 220 or whether the entire amount of the heating medium is bypassed. In this case, the cooling amount of the processing air and the heating amount of the regeneration air can be adjusted, so that the temperature in the state N can be set or adjusted freely.

Next, referring to FIG. 10, FIG.
An embodiment of a dehumidifying air-conditioning system using the dehumidifying air-conditioning apparatus for air-conditioning of a building will be described. In the figure, the heat pump (H
P) 1 is installed on the roof of the building 60. Heat pump 1 is a fifth evaporator for a refrigerant as a working medium.
, A compressor 3 for sucking and compressing the refrigerant gas evaporated therefrom, and a fourth heat exchanger 35 which is a condenser for condensing the refrigerant gas discharged from the compressor 3. An expansion valve 7 for reducing the pressure of the refrigerant liquid and returning the refrigerant liquid to the evaporator 25. Further, a subcooler 36 for supercooling the refrigerant is provided adjacent to the condenser 35. These devices are connected by refrigerant gas piping or refrigerant liquid piping. As the heat pump 1, for example, the heat pump HP described with reference to FIG. 2 is used.

The evaporator 25 is connected to a cooling medium pipe (a gas phase pipe 21 and a liquid phase pipe 20) for a cooling medium from which heat is removed by evaporation of the refrigerant. The condenser 35 includes a heating medium pipe (a liquid phase pipe 31 before heating, a gas phase pipe 3 after heating) for a heating medium heated by condensation of the refrigerant.
0) is connected. The cooling medium pipes 20 and 21 and the heating medium pipes 30 and 31 are arranged from the air conditioning space 61A on the uppermost floor to the lowermost floor 61E (in FIG. 10, a five-story building of A to E is shown, but is not limited to this. No)).

The dehumidifying air conditioners (DSCs) 70A, 70B and 70 similar to those described with reference to FIGS. 1 and 8 are placed in a region having a large latent heat load such as a space on the north side of each floor or a center (core).
C, 70D, and 70E are provided respectively. The dehumidifying air conditioner 70A is provided with an opening for taking in outside air OA and an opening for exhaust EX.
A processing air duct for supplying A) to the air-conditioned space is connected. The dehumidifying air conditioner 70A has a cooling medium pipe 2
0, the branch pipe 41A from the cooling medium pipe 21, the branch pipe 42A from the heating medium pipe 30,
The branch pipe 43A from the heating medium pipe 31 is connected. Dehumidifying air conditioners 70B, 70C, 70 on other floors
The same applies to D and 70E. The branch pipe 40A is shown in FIG.
The branch pipe 41A corresponds to the pipe 162,
The branch pipe 42A is connected to the pipe 151, and the branch pipe 43A is connected to the pipe 15
2 respectively.

Further, fan coil units 51A, 51B, 51C, 51D and 51E are installed in areas (perimeters) where the sensible heat load is large, such as the space near the window on the south side of each floor. A branch pipe 44A from the cooling medium pipe 20 and a branch pipe 45A from the cooling medium pipe 21 are connected to the dehumidifying air conditioner 51A. The same applies to the dehumidifying air conditioners 51B, 51C, 51D, and 51E on other floors.

In the air conditioning system having such a configuration, the latent heat load processing for obtaining the so-called dehumidifying effect of the cooling load is performed by the desiccant air conditioners 70A to 70E, and the sensible heat load processing by the solar radiation of the perimeter portion is performed by the fan coil unit. This is performed at 51A to 51E. In the conventional cooling, since the latent heat load treatment is also performed with cold water, it is necessary to cool the air to a temperature equal to or lower than the dew point temperature. Therefore, it is common to supply the cold water at a temperature of 5 to 7 ° C. However, in this system, only the sensible heat load process needs to be performed for the cooling medium, so that the temperature of the cooling medium is about 10 ° C. lower than the air temperature. In the desiccant air conditioner, regeneration air at 60 to 80 ° C is required for desiccant regeneration, and therefore, a heating medium at 70 to 90 ° C is supplied.

In the dehumidifying air-conditioning system according to the embodiment of the present invention, since the fifth heat exchanger 25, which is a refrigerant evaporator and a cooling medium condenser of the heat pump 1, is installed on the roof of a building, The low-temperature liquid-phase cooling medium is supplied to the dehumidifying air conditioners 70A to 70E or the fan coils 51A to 51E by gravity due to natural convection. Return to the heat exchanger 25.

In the present embodiment, the cooling medium is supplied to each of the dehumidifying air conditioners 70A to 70E and the fine coil units 51A to 51E by gravity in the liquid phase. A trap is provided to prevent the supply of excess liquid cooling medium.

Further, since the fourth heat exchanger 35 which is a condenser of the refrigerant of the heat pump 1 and an evaporator of the heating medium is installed in the basement of the building, the heating medium in a high temperature and a gaseous phase is naturally generated by gravity. Dehumidifying air conditioners 70A to 70E by convection
Is supplied to the heating medium, and the heating medium whose temperature has been reduced to a liquid phase returns to the fourth heat exchanger 35 by natural convection due to gravity.

As described above, a pump or a compressor for transferring the heat medium is not required, and when the heat medium is provided, only a low-head pump needs to be installed in the liquid phase line, so that the heat transfer power is extremely small. I'm done.

In the embodiment shown in FIG. 10, a refrigerator 9 is provided which is connected to the fifth heat exchanger 25 and removes heat from the cooling medium in the fifth heat exchanger 25. The refrigerator 9 is a compression type refrigerator, and its evaporator is constituted by a heat exchange tube L incorporated in the fifth heat exchanger 25. When the cooling load of the building increases and the amount of heat pumped by the heat pump 1 cannot be satisfied with the cooling load, the refrigerator 9 is operated to help cool and condense the cooling medium. The refrigerator 9 is not limited to the compression type, but may be an absorption type.

The fourth heat exchanger 35 may be provided with a high heat source (not shown). The high heat source is constituted by a heat exchange tube separately incorporated in the fourth heat exchanger 25.
When a heating operation is performed, when a latent heat load is large and a dehumidifying operation is required, or when the heat pump 1 pumps up heat, when a heating load or a dehumidifying load cannot be satisfied, a high heat source is operated to generate heat. The medium can be heated to help evaporate.

In the embodiment described above, a refrigerant for a refrigerator can be used as the heating medium or the cooling medium. Further, since the heating medium and the cooling medium are separated into different systems, different media can be used. Further, the refrigerant may be the same as the refrigerant used in the heat pump 1, but may be a different refrigerant. In ordinary building air conditioning, a medium suitable for a heating medium is, for example, HFC134a, HFC
245 ca, and a medium suitable for the cooling medium is, for example, H
FC407C, HFC410A, and HFC134a.

[0069]

As described above, according to the present invention, the heating medium supplied from the heating medium supply device is configured to flow in the order of the first heat exchanger and the second heat exchanger. First
The heat corresponding to a part of the heat used for heating the regenerated air in the heat exchanger can be recovered from the treated air in the second heat exchanger, and a compact dehumidifying air conditioner can be provided. Becomes In addition, since heat is transferred using the phase change of the heat medium, it is possible to provide a dehumidifying air-conditioning system with extremely low transfer power.

[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 flowchart of a heat pump suitable for use in the dehumidifying air conditioner of FIG.

FIG. 3 is a psychrometric chart for explaining the operation of the dehumidifying air conditioner of FIG. 1;

FIG. 4 is a diagram for explaining heat exchange between a heating medium and processing air and between a heating medium and regeneration air in the embodiment considered in FIG. 3;

FIG. 5 is a Mollier diagram of a heat pump used in the dehumidifying air conditioner of FIG.

FIG. 6 is a diagram illustrating heat exchange between a refrigerant and a heating medium in the embodiment considered in FIG. 3;

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 shown in FIG. 1;

FIG. 8 is a flowchart of a dehumidifying air conditioner according to a second embodiment of the present invention.

FIG. 9 is a psychrometric chart explaining the operation of the dehumidifying air conditioner of FIG. 8;

FIG. 10 is a flowchart showing an example of a dehumidifying air conditioning system according to an embodiment of the present invention.

FIG. 11 is a flowchart of a conventional dehumidifying air conditioner.

FIG. 12 is a Mollier diagram of a heat pump used in the conventional dehumidifying air conditioner of FIG.

FIG. 13 is a diagram illustrating heat exchange between a refrigerant and a heating medium of the heat pump in FIG. 12;

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Heat pump 3 Compressor 7 Expansion valve 20 and 21 Cooling medium pipe 30 and 31 Heating medium pipe 25 5th heat exchanger (refrigerant evaporator) 35 4th heat exchanger (refrigerant condenser) 51A-51E Fan coil unit 61A to 61E Air conditioning space 70A to 70E Dehumidifying air conditioner 102, 140 Blower 103 Desiccant rotor 106 Humidifier 115 Third heat exchanger 120 First heat exchanger 220 Second heat exchanger 700 Cabinet HP heat pump

Claims (8)

[Claims] 1. A moisture adsorbing device having a desiccant for adsorbing moisture in processing air and desorbing moisture by regeneration air; a first heat exchanger for exchanging heat between the regeneration air and a gaseous heating medium A first heat exchanger provided on the upstream side of the flow of the regeneration air with respect to the moisture adsorption device; and the heat exchanged with the processing air and the first heat exchanger. A second heat exchanger for exchanging heat with a medium, comprising: a second heat exchanger provided downstream of the flow of the processing air with respect to the moisture adsorption device; Dehumidifying air conditioner. 2. A third heat exchanger for exchanging heat between the processing air and a cooling medium in a liquid phase, the heat exchanger being provided on the downstream side of the flow of the processing air with respect to the second heat exchanger. Third
The dehumidifying air conditioner according to claim 1, further comprising a heat exchanger. 3. A switching device for switching a flow of the heat medium exchanged by the first heat exchanger between the first heat exchanger and the second heat exchanger. Item 1
Or the dehumidifying air conditioner according to claim 2. 4. A dehumidifying air conditioner according to claim 2,
From the cooling medium supplied to the third heat exchanger,
And a heat pump for pumping heat to a heating medium supplied to the heat exchanger of the present invention. 5. The dehumidifying air conditioning system according to claim 4, wherein a plurality of said dehumidifying air conditioners are provided for one heat pump. 6. The heat pump according to claim 4, further comprising: a fourth heat exchanger for applying heat to the heating medium; and a fifth heat exchanger for removing heat from the cooling medium.
Or the dehumidification air conditioning system according to claim 5. 7. The fourth heat exchanger is installed vertically below the dehumidifying air conditioner relative to the dehumidifying air conditioner.
The dehumidifying air-conditioning system according to claim 6, wherein the heat exchanger is installed vertically above the dehumidifying air-conditioning device. 8. The dehumidifying air-conditioning system according to claim 4, further comprising a refrigerator for removing heat from the cooling medium.