JP2001182967A - Dehumidifier/air conditioner - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a dehumidifier/air conditioner which can deal with an air conditioning load under various weather conditions and can sustain optimal temperature and humidity in a room throughout the cooling season. SOLUTION: The dehumidifier/air conditioner comprises a moisture absorber having decicant absorbing moisture in the air being processed and regenerated with regenerating air, a heat pump employing the air being processed as a low heat source and the regenerating air as a high heat source, means for detecting the humidity of a space supplied with the air being processed to which moisture is adsorbed, means for detecting the temperature in the space, and a sensible heat ratio increasing/decreasing means operated based on a humidity detected by the humidity detecting means and a temperature detected by the temperature detecting means.

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 a dehumidifying air conditioner 4 in which a heat pump as a heat source is combined with a so-called desiccant air conditioner. In the dehumidifying air conditioner 4 of FIG. 12, a compression heat pump HP using a compressor 260 is used as a heat pump. The dehumidifying air-conditioning device 4 is configured to process air A to which moisture is adsorbed by the desiccant rotor 103.
And a path 130 of regenerated air B which is heated by a heating source, passes through the desiccant rotor 103 after adsorbing the moisture, and desorbs and regenerates moisture in the desiccant.
Having.

[0003] The dehumidifying air-conditioning apparatus 4 further clarifies between the treated air A to which moisture is further adsorbed and the regenerated air B before regenerating the desiccant (desiccant) of the desiccant rotor 103 and before being heated by the heating source. It has a heat exchanger 104.
The dehumidifying air conditioner 4 uses the regenerated air B as a high heat source of the compression heat pump HP, heats the regenerated air B with a heater (refrigerant condenser) 220 to regenerate the desiccant, and compresses the processing air A. The processing air A is used as a low heat source of the heat pump HP by the cooler (refrigerant evaporator) 21.
It cools at zero.

Here, the operation of the dehumidifying air conditioner 4 shown in FIG. 12 will be described with reference to the psychrometric chart of FIG. In FIG. 13, the states of the processing air A and the regeneration air B are indicated by alphabets K to N and Q to U, respectively. This symbol is shown in FIG.
It corresponds to the alphabet circled in the flow chart of FIG.

In FIG. 13, indoor air RA (processed air A in state K) in the air-conditioned space 101 is desiccant adsorbed by the desiccant rotor 103 to lower the absolute humidity, and the desiccant heat of adsorption causes the dry bulb temperature to decrease. To reach state L. The treated air A is further cooled in the sensible heat exchanger 104 while keeping the absolute humidity constant, becomes air in the state M, and enters the cooler (refrigerant evaporator) 210. Here, the air is further cooled at a constant absolute humidity to become air in the state N, and the air is supplied to the air-conditioned space 101 by SA.

On the other hand, the outside air OA in the state Q is sent to the sensible heat exchanger 104 as regenerated air B, where it is heated to the state R by cooling the processing air A, and When the desiccant is regenerated by the desiccant rotor 103, the absolute humidity rises, the dry-bulb temperature drops, and the exhaust gas EX is exhausted as air in the state U.

[0007] In general, conventional air conditioning apparatus (air conditioner), sensible heat ratio of air-conditioning load, i.e. when the sensible heat is removed from the process air A by the air conditioner 4 and Q _S, the latent heat and Q _L, Q _S / value _(Q S + Q _L) is midsummer maximum load temperature, humidity (e.g., temperature 32 ° C., absolute humidity 20 g / k
g) is determined on the basis of outside air. That is, at the time of maximum load, the air conditioner can sufficiently cool and dehumidify,
The processing air A in the air-conditioned space 101 can be set to a comfortable temperature and humidity.

[0008]

However, during the cooling period, the average temperature of the most frequently used area of the outside air is 27.5 ° C., the average absolute humidity is about 17 g / kg, and the temperature of 32 ° C. seen at the maximum load is 32 ° C. The outside air condition such as the absolute humidity of 20 g / kg is not very long, and the sensible heat ratio of the air conditioning load in the most frequently used area is smaller by about 15%. The ratio does not match.
Therefore, according to the conventional air conditioner, when the air conditioner is used in the most frequently used area, the room temperature is lowered with insufficient dehumidification, so that the occupants are extremely uncomfortable.

Accordingly, an object of the present invention is to provide a dehumidifying air-conditioning apparatus which can cope with an air-conditioning load of high temperature and high humidity during a high summer and can maintain an optimum temperature and humidity in a room during a cooling period.

[0010]

In order to achieve the above object, a dehumidifying air conditioner according to the first aspect of the present invention, as shown in FIG.
A moisture adsorbing device 103 having a desiccant regenerated by the regenerating air B; a heat pump HP using the processing air A as a low heat source and using the regenerating air B as a high heat source; and a space 101 for supplying the processing air A with the moisture adsorbed. Humidity detecting means 401 for detecting humidity; temperature detecting means 402 for detecting the temperature of the space 101; humidity detected by the humidity detecting means 401;
Sensible heat ratio increasing / decreasing means 406 and 407 operated based on the temperature detected by the temperature detecting means 402.

A sensible heat ratio increasing / decreasing device is operated based on the humidity of the space detected by the humidity detecting device and the temperature of the space detected by the temperature detecting device. The temperature can be adjusted and dehumidified to optimize the humidity and temperature of the space regardless of the surrounding humidity and temperature. The sensible heat ratio refers to the ratio of the total of the sensible heat removed from the space and the latent heat removed from the space.

Further, as described in claim 2, claim 1
In the dehumidifying air conditioner described in the above, for example, as shown in FIG. 1, the sensible heat ratio increasing / decreasing means includes a moisture adsorbing capacity increasing / decreasing means 406 of the moisture adsorbing device 103 and the processing air A to which the moisture is adsorbed by the moisture adsorbing device 103. A humidifying amount increasing / decreasing unit 105 (not shown in FIG. 1; see FIG. 9) for humidifying, or a unit 407 for increasing / decreasing the cooling amount of the processing air A by the heat pump HP may be a means. .

With such a configuration, the water adsorption device 10
3 is configured to rotate, and the moisture adsorbing device 10
When the number of rotations adjusting means 406 is provided, the amount of water adsorbed can be changed by adjusting the number of rotations of the water adsorption device 103, and the sensible heat ratio of the cooling effect can be changed. In some cases, the moisture adsorption device 103 is configured not to rotate. Further, even when the moisture adsorption device 103 is configured to rotate, the rotation speed adjusting means 406 of the moisture adsorption device 103 may not be provided.

[0014] Alternatively, since a humidifying amount increasing / decreasing means for humidifying the treated air to which moisture is adsorbed by the moisture adsorbing device is provided, when the dehumidifying ability, that is, the latent heat treating ability is exceeded, the latent heat treating ability is reduced by humidifying to the sensible heat treating ability. And the sensible heat ratio of the cooling capacity can be changed. Alternatively, since means for increasing or decreasing the cooling amount of the processing air by the heat pump is provided, the amount of sensible heat to be removed can be changed, and the sensible heat ratio of heat removed from the air can be changed. Therefore, regardless of the humidity and temperature of the outside air, cooling and dehumidification can be performed to optimize the humidity and temperature of the space.

The rotation speed adjusting means for adjusting the rotation speed may be configured to drive the desiccant rotor as the moisture adsorption device of the present invention by, for example, a variable speed motor. Further, a variable speed reduction gear reducer or the like can be connected to the constant speed motor. The humidification amount increasing / decreasing means may be configured to include a vaporizing humidifier or the like in which the supply amount of water supplied to the processing air is variable. The cooling amount increasing / decreasing means as the sensible heat ratio increasing / decreasing means for increasing / decreasing the sensible heat ratio of heat taken from the processing air is configured, for example, so that the processing air bypasses the cooler. It may be supplemented with outside air.
The processing air is cooled by depriving the sensible heat by a heat pump as a low heat source.

Further, as described in claim 3, claim 1
Or in the dehumidifying air conditioner according to claim 2, when the humidity of the space is lower than a desired value and the temperature is higher than a desired value,
A controller for increasing the sensible heat ratio and controlling the sensible heat ratio increasing / decreasing means so as to decrease the sensible heat ratio when the humidity of the space is higher than a desired value and the temperature is lower than a desired value.

Since a controller is provided, the controller controls the sensible heat ratio increasing / decreasing means to increase the sensible heat ratio of heat removed from air when the humidity of the space is lower than a desired value and the temperature is higher than a desired value. To ensure that the temperature drops, and when the humidity of the space is higher than the desired value and the temperature is lower than the desired value,
The sensible heat ratio can be reduced to ensure that the humidity is reduced.

When the humidity is lower than the desired value and the temperature is higher than the desired value, it means that the temperature is higher than the desired value even if the humidity of the space for supplying the processing air is appropriate. Even when the humidity is lower than the desired value. When the humidity of the space is higher than the desired value and the temperature is lower than the desired value, when the temperature is lower than the desired value even when the humidity is appropriate, the humidity is lower than the desired value even when the temperature is appropriate. Including when it is high. The desired values are, for example, a humidity value and a temperature value that are comfortable for humans. If the dehumidifying air conditioner has a controller, the desired value may be set to the controller.

[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 shows a first embodiment of a dehumidifying air conditioner according to the present invention.
It is a flowchart of the air-conditioning system which has a dehumidifying air-conditioning apparatus which is embodiment of this invention, ie, a desiccant air conditioner. The present dehumidifying air-conditioning apparatus 1 includes a cooling dehumidifying operation for performing cooling and dehumidifying,
This is an apparatus configured to be capable of switching to a dehumidifying operation in which mainly a dehumidifying operation is performed, and to a sensible heat cooling operation in which cooling is mainly performed by removing sensible heat. In addition, in the figure, the solid line is a flowchart in the case where it is suitable for the cooling dehumidifying operation and the sensible heat cooling operation, and the broken line is a flowchart in the case where it is suitable for the dehumidifying operation.

Referring to FIG. 1, the structure of a dehumidifying air conditioner 1 according to a first embodiment will be described. The switching from the cooling dehumidifying operation to the dehumidifying operation is performed by switching a connection of a four-way valve 270 described later from a connection indicated by a solid line in the drawing to a connection indicated by a broken line in the drawing. Switching from the cooling dehumidifying operation to the sensible heat cooling operation is performed by changing the rotation speed of a desiccant rotor described later. The device configuration of the dehumidifying air conditioner 1 is the same for the cooling dehumidifying operation, the dehumidifying operation, and the sensible cooling.

In the dehumidifying air-conditioning apparatus 1, the desiccant (drying agent) mainly lowers the humidity of the processing air A, lowers the temperature of the processing air A with a heat exchanger described later, and controls the air-conditioned space 101 to which the processing air A is supplied. It is intended to maintain a comfortable temperature and humidity environment. Here, the components along the path of the processing air A will be described first. As shown in the figure, the air-conditioned space 101,
Path 107, blower 10 for circulating process air A
2. Path 108, desiccant rotor 103 filled with desiccant as moisture adsorption apparatus of the present invention, path 10
9, air cooler 310 as heat exchanger, path 110,
A refrigerant evaporator (cooler as viewed from the processing air) 210 as a heat exchanger and a path 111 are arranged in this order. Indoor air RA (process air A) in the air-conditioned space 101
Are configured to pass through devices, pipes, and the like in the order described above, and to supply air to the air-conditioned space 101.

Next, the components along the path from the outdoor OA to the regeneration air B will be described. As shown, a path 124 from the outdoor OA, a blower 14 for circulating the regenerated air
0, path 125, air heater 320 as heat exchanger,
Path 126, refrigerant condenser 220 as a heat exchanger (heater as viewed from regeneration air) 220, path 127, desiccant rotor 103, path 128, air heater 2 as heat exchanger
30 and the path 129 are arranged in this order. The regenerative air B is taken in from the outdoor OA, passes through the devices, pipes, and the like in the order described above, and is exhausted outdoors.

Next, the components will be described along the refrigerant path in the cooling and dehumidifying operation and the sensible cooling operation. In the figure, the refrigerant compressed by the compressor 260 passes from the path 201 to the refrigerant condenser 220, and further flows from the flow path 202 to the throttle 250,
51, via a four-way valve 270 (in the coupled state shown by the solid line in the figure) as a switching means, from the path 206 to the refrigerant evaporator 210, further through the refrigerant path 207, to the refrigerant evaporator 230, and Path 208, 4-way valve 270, Path 2
09, the refrigerant evaporator 210 and the refrigerant evaporator 230
The compressor 260 is configured to return to the compressor 260 that compresses the refrigerant evaporated and gasified by the above.

The four-way valve 270 is shifted to the connection state shown by the broken line in FIG.
Is performed, the operation becomes suitable for the dehumidifying operation. In this case, the refrigerant is compressed by the compressor 260, passes through the path 201, passes through the refrigerant condenser 220, further passes through the path 202, passes through the throttle 250, the path 251, and the four-way valve 270, and passes through the path 20.
8 to the refrigerant evaporator 230, and further from the refrigerant path 207 to the refrigerant evaporator 210 for further evaporating the refrigerant remaining without evaporating in the refrigerant evaporator 230, and further to the path 20.
Through the equipment, piping, and the like arranged in this order to the six- and four-way valves 270 and the path 209, the refrigerant evaporator 230 and the refrigerant evaporator 210 return to the compressor 260 that compresses the gasified refrigerant. Is configured.

In this case, the refrigerant evaporates almost entirely in the refrigerant evaporator 230, and the refrigerant evaporator 210 evaporates the slightly remaining refrigerant. Therefore, the regeneration air B is cooled by the refrigerant evaporator 230, and the processing air A is hardly cooled. In any case of the cooling dehumidifying operation, the dehumidifying operation, and the sensible heat cooling, the refrigerant liquid is not sucked into the compressor 260 in any case.

Next, the configuration of the heat medium circulation type heat exchanger (sensible heat exchanger) 154 will be described. The heat medium circulation heat exchanger 154 includes an air cooler 310 and an air heater 320. The air heater 320 is connected to the heat medium path 30.
2 are connected. Heat medium path 302 is circulation pump 3
30, the discharge port of the circulation pump 330 is connected to the air cooler 310 by the heat medium path 303,
From here, it communicates with the air heater 320 through the heat medium path 301.

As described above, the circulation pump 330 includes the heat medium path 303, the air cooler 310, and the heat medium path 30.
1. With the heat medium circulation path of the air heater 320 and the heat medium path 302, the heat medium liquid (for example, water, brine) is circulated between the air heater 320 and the air cooler 310. .

As described above, the compressor 260,
Refrigerant condenser 220, refrigerant evaporator 210, refrigerant evaporator 23
The heat pump HP of the present invention includes the zero, the throttle 250, and the four-way valve 270.

The desiccant rotor 103 is formed as a thick disk-shaped rotor that rotates around the rotation axis AX, and the rotor is filled with a desiccant with a gap through which gas can pass. For example, a large number of tubular drying elements are bundled so that the central axis thereof is parallel to the rotation axis AX. The desiccant rotor 103 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 desiccant-containing drying element is arranged to alternately contact the processing air A and the regeneration air B as the desiccant rotor 103 rotates. Generally, the processing air A and the regeneration air B are each parallel to the rotation axis AX, and are each a circular desiccant rotor 1.
It is configured to flow in almost half the area of 03 in a counter-current manner.

The refrigerant condenser 220 through the air cooler 310
Preferably has a plate fin coil structure. That is, a series of tubes are meandered and arranged in the flow of the regeneration air B or the processing air A, and plate fins are attached to the outside of the tubes, that is, on the air flow side, to increase the heat transfer area on the air side. The tubes are arranged so as to cross the air flow at right angles to the air flow, but are preferably arranged so as to meander but oppose the air flow as a whole.

A humidity detecting means 401 for measuring relative humidity and a temperature detecting means 40 for measuring temperature are provided in the air-conditioned space 101.
2 are installed, and the detection signals of the detected temperature (room temperature) and humidity (room relative humidity) are sent to the controller 403.

The desiccant rotor 103 includes the drive belt 4
04 connected to the variable speed motor 405 via the controller 4
The rotation speed adjuster 406 as the rotation speed adjusting means of the present invention, which receives the control signal from the control unit 03, adjusts the output of the variable speed motor 405 so that the desiccant rotor 103 has an appropriate rotation speed. The rotation speed adjustment will be described later. 4-way valve 27
0 is connected to an actuator 407 as a means for increasing or decreasing the cooling amount of the processing air of the present invention, and the actuator 407 receives a control signal from the controller 403 and receives a control signal from the controller 403.
70 is switched.

Here, the flow of the processing air A and the regeneration air B and changes in the state will be described with reference to FIG. First, the cooling and dehumidifying operation will be described. The processing air A and the regeneration air B in this case will be described with reference to the psychrometric chart of FIG.

In FIG. 1, the processing air A from the air-conditioned space 101
(State K) is sucked into the blower 102 through the path 107, is further discharged from the blower 102, and
8 and is sent to the desiccant rotor 103. The treated air A dried by absorbing moisture with the desiccant rotor 103 lowers the absolute humidity and raises the dry-bulb temperature (state L). The processing air A then reaches the air cooler 310 through the path 109, where it exchanges heat with the heat transfer medium circulated by the circulation pump 330, thereby being cooled to a certain extent at a constant absolute humidity and lowering the dry bulb temperature ( State M), path 110
Through the refrigerant evaporator 210. Here, it is further cooled at a constant absolute humidity to lower the dry bulb temperature (state N), and the route 11
1 to the air-conditioned space 101.

Next, changes in the flow and state of the regenerated air B in the cooling and dehumidifying operation will be described. As shown in the figure, the regenerated air B (state Q) from the outdoor OA is sucked into the blower 140 through the path 124, is further discharged from the blower 140, and is sent into the air heater 320 through the path 125. Here, heat exchange is performed with the heat medium liquid circulated by the circulation pump 330, and the dry bulb temperature is raised at a constant absolute humidity (state R).

The heat medium liquid to be subjected to heat exchange acts as a medium for heat exchange between the regeneration air B and the processing air A by the circulation of the circulation pump 330. This heat exchange is a sensible heat exchange utilizing a sensible heat change of the heat medium liquid.
Because of the forced circulation at 30, a high heat transfer coefficient can be achieved. In addition, since both the air cooler 310 and the air heater 320 are configured so that the flow of the heat medium liquid and the air are countercurrent as a whole, the heat exchange efficiency is high. In this way, the heat exchange between the processing air A and the regeneration air B can be performed with high efficiency by the simple structure by the air cooler 310 and the air heater 320.

The regeneration air B heated to a certain extent by the air heater 320 is sent to a refrigerant condenser (heater as viewed from the regeneration air) 220 through a path 126, where it is heated and dried at a constant absolute humidity. The temperature is increased (state T). This air is sent to the desiccant rotor 103 through the path 127, where it deprives the desiccant in the drying element of moisture and regenerates it, thereby increasing the absolute humidity and lowering the dry-bulb temperature by the heat of desiccant moisture desorption. (State U). This air passes through the path 128 and passes through the refrigerant evaporator 230, where the state (state V) hardly changes. The refrigerant is a refrigerant evaporator 21
This is because the refrigerant evaporates almost at 0, and the refrigerant evaporator 230 hardly evaporates. Then, the exhaust gas EX is exhausted through the path 129. In FIG. 2, the point representing the state V almost overlaps with the point representing the state U.

Next, in the case of the dehumidifying operation (the state of the air is shown in FIG.
), The changes in the flow and the state of the processing air A and the regeneration air B will be described focusing on the difference from the case of the dehumidifying cooling operation.
In the case of the dehumidification operation, the refrigerant passes through the four-way valve 270, the path 208, passes through the refrigerant evaporator 230, and then passes through the path 207,
It passes through the refrigerant evaporator 210. At this time, the refrigerant is the refrigerant evaporator 2
30 evaporates almost, and the refrigerant evaporator 21
At 0, the refrigerant is hardly evaporated. Therefore, the processing air A is hardly cooled by the refrigerant evaporator 210, and the processing air is returned to the air-conditioned space 101 in a state N substantially equal to the state M. In FIG. 3, the point representing the state N is the state M
Almost overlap with the point representing. The refrigerant evaporator 210
The change of the flow and the state of the processing air A before passing through is the same as in the cooling and dehumidifying operation described above.

On the other hand, the regeneration air B is supplied to the desiccant rotor 1.
After exiting 03, it is cooled by the refrigerant evaporator 230,
With the absolute humidity kept constant, the dry bulb temperature is lowered (state V), and the exhaust gas is exhausted. The flow and the change of the state of the regenerated air B before passing through the refrigerant evaporator 230 are the same as those in the above-described cooling and dehumidifying operation.

Next, changes in the flows and states of the processing air A and the regeneration air B in the case of the sensible heat cooling operation (see FIG. 4 for the state of the air) will be described focusing on the difference from the case of the dehumidifying cooling operation. . The flow of the refrigerant in the case of the sensible cooling operation is the same as that of the cooling and dehumidifying operation described above.
Is decreasing. Therefore, the amount of desiccant to be dehumidified from the processing air A is reduced as compared with the case of the cooling dehumidifying operation.
, The amount of decrease in absolute humidity is small, and the amount of increase in dry bulb temperature is also small. In FIG. 4, the length of the line connecting L and K is shown in FIG.
This is indicated by being drawn shorter than the length of the line connecting L and K in the middle. The flow and the change of the state of the processing air A after passing through the desiccant rotor 103 are the same as those in the cooling and dehumidifying operation.

Further, as the number of rotations of the desiccant rotor 103 decreases, the amount of humidification by which the desiccant humidifies the regeneration air B is reduced as compared with the cooling and dehumidifying operation. Therefore, state T
When the state shifts from the state U to the state U, the amount of increase in the absolute humidity of the processing air A becomes small, and the amount of decrease in the dry-bulb temperature also becomes small. This indicates that the length of the line connecting T and U in FIG. 4 is shorter than the length of the line connecting T and U in FIG. The flow and the change of the state of the regenerated air B before passing through the desiccant rotor 103 and after passing through the desiccant rotor 103 are the same as those in the cooling and dehumidifying operation.

However, if the number of rotations of the desiccant rotor 103 is reduced in steps (for example, three or more steps) in a stepwise manner, and if the number of rotations of the desiccant rotor 103 is reduced to a certain The circulation pump 330 for circulating the liquid may be stopped. This is because when the temperature of the processing air A after passing through the desiccant rotor 103 is lower than the outside air temperature, it is meaningless to perform heat exchange between the processing air A and the outside air.

Next, the flow of the refrigerant between the devices in the cooling dehumidifying operation and the sensible heat cooling operation will be described with reference to the flowchart of FIG.

In FIG. 1, a compressor 26 compresses a refrigerant.
The refrigerant gas compressed by 0 is guided to a regenerative air heater (refrigerant condenser) 220 via a refrigerant gas pipe (path) 201 connected to a discharge port of the compressor. Compressor 260
The temperature of the refrigerant gas compressed by the heat is increased by the compression heat 260, and the heat heats the regeneration air B. The refrigerant gas itself is deprived of heat and condenses.

The refrigerant outlet of the refrigerant condenser 220 is connected to the passage 20
2 to the throttle 250, where the pressure is reduced and flashed, and the refrigerant reaches the refrigerant evaporator 210 through the path 251, the four-way valve 270, and the path 206. The refrigerant evaporates almost here and exchanges heat with the processing air A to cool the processing air A. The refrigerant that has exited the refrigerant evaporator 210 reaches the refrigerant evaporator 230 via the path 207. The refrigerant is heated by the regeneration air to become superheated steam. Next, the refrigerant that has become superheated vapor is sucked into the compressor 260 through the path 208, the four-way valve 270, and the path 209, and the above cycle is repeated.

Next, the flow of the refrigerant in the dehumidifying operation will be described with reference to FIG. Switching from the cooling dehumidification operation to the dehumidification operation is performed by switching the connection of the four-way valve 270 from the connection indicated by the solid line in the drawing to the connection indicated by the broken line in the drawing. Since the flow from the compressor 260 to the four-way valve 270 is the same as in the case of the cooling and dehumidifying operation, the description is omitted.

The refrigerant that has exited the refrigerant outlet of the refrigerant condenser 220 reaches the throttle 250 through the path 202. However, in the dehumidifying operation, since the four-way valve 270 has been switched from the cooling dehumidifying operation, the pressure is reduced and the flash is discharged. Then, after leaving the four-way valve 270 via the path 251, it reaches the refrigerant evaporator 230 via the path 208. The refrigerant evaporates here and exchanges heat with the regeneration air B to cool the regeneration air B. The refrigerant that has exited the refrigerant evaporator 230 reaches the refrigerant evaporator 210 via the path 207. In the refrigerant evaporator 210, the processing air A is hardly cooled because the refrigerant has already been evaporated in the evaporator 210 and has no cooling ability. Next, the evaporated gas-phase refrigerant passes through the path 206, the four-way valve 270, and the path 209, is drawn into the compressor 260, and repeats the above cycle.

Next, the operation of the dehumidifying air conditioner 1 (see FIG. 1) will be described with reference to FIG. Note that FIG. 1 is referred to for devices. FIG. 5 is a graph in which the horizontal axis represents the room temperature of the air-conditioned space 101 and the vertical axis represents the indoor relative humidity of the air-conditioned space 101. The point P _{0 as the} origin indicates a control target point, and the temperature at that point is t ₀ ° C and the relative humidity is φ ₀ %. The temperature t ₀ ° C is the desired temperature, and the relative humidity φ ₀ % is the desired humidity.

The region _{A 1} is at room temperature is higher than _{t 0} ° C., it is higher than _0% indoor relative humidity φ region, in this region,
The cooling and dehumidifying operation is performed at a normal sensible heat ratio. Area _{A 2} is,
A region where the room temperature is lower than t ₀ ° C. and the room relative humidity is higher than φ ₀ %. In this region, a dehumidifying operation is performed at a sensible heat ratio lower than a normal sensible heat ratio (a small amount of sensible heat is applied so that the room temperature becomes almost constant). Is removed and latent heat is removed to reduce humidity.)
Is performed. Area A ₃ is at room temperature is lower than t ₀ ° C., since the indoor relative humidity is less than phi _0% operation of the dehumidifying air-conditioning apparatus 1 is an area that is not performed. Area A ₄ are the room temperature is higher than t ₀ ° C., is lower than the room relative humidity is phi _0% area, normal sensible heat cooling operation at a high sensible heat ratio than sensible heat ratio (indoor relative humidity is substantially constant In this way, a small amount of latent heat is removed, and sensible heat is removed to lower the temperature.).

The point _{P 1} in the area _{A 1} is the ambient air high temperature during midsummer (e.g. 32 ° C.), high humidity (e.g. absolute humidity 20 g /
(kg), the temperature / humidity condition of the air-conditioned space 101 that can occur in such a case. Is designed so that the temperature and humidity of the air-conditioned space 101 can be set to desired values by removing air and cooling and dehumidifying.

[0052] Within the area _{A 1,} the humidity detecting means 401, temperature temperature detecting means 402, respectively, sends a detection signal to the controller 403 detects the humidity, it is determined that the controller 403 is operating in the area _{A 1,} A control signal is sent to the actuator 406, and the actuator 406 brings the four-way valve 270 into the state shown by the solid line in FIG. Therefore, the refrigerant evaporator 21
0 cools the processing air A, and the refrigerant evaporator 230 does not cool the regeneration air B. Almost no refrigerant evaporates in the refrigerant evaporator 21
This is because it is performed at 0 and almost not performed at the refrigerant evaporator 230. The controller 403 further includes a rotation speed controller 40.
4 to a normal rotation speed (for example, 15 to 20).
(Rotation / hour) to rotate the desiccant rotor 103.
Therefore, the dehumidifying air-conditioning apparatus 1 performs cooling and dehumidifying operation in a predetermined sensible heat ratio as a point conditions of the air conditioning space 101 becomes the point P _0.

Region A₁A point P in₂Means that the sensible heat load is
This is a point that the dehumidification load is not large. Point P₂Is the territory
Area A₁The point P₁Of the same sensible heat ratio as in
The chamber dehumidifying operation is performed, and the condition of the air-conditioned space 101 is P₁
And P₀Move almost parallel to the line connecting
Intersection above, area A₂A point P in₂Move to '. Point P ₂
In ', the room temperature is t₀It is almost equal to ° C and humidity is φ₀%Than
high. Detected by humidity detecting means 401 and temperature detecting means 402
Upon receiving the output signal, the controller 403 sets the condition of the air-conditioned space 101.
Is the area A₂And the actuator 406
To the actuator 406 and the four-way valve 27
0 is set to the state shown by the broken line in FIG.

Therefore, the refrigerant evaporator 210 does not cool the processing air A, and the refrigerant evaporator 230 cools the regeneration air B. Therefore, the amount of sensible heat removed from the processing air A decreases, and the room temperature is maintained at approximately t ₀ ° C.

The controller 403 rotates the desiccant rotor 103 at a normal rotation speed without changing the control signal sent to the rotation speed controller 406. Therefore, the dehumidification amount of the processing air A is substantially maintained, and the value of the latent heat to be removed is substantially maintained. Therefore, the dehumidifying air conditioner performs a dehumidifying operation in which dehumidification is mainly performed at a low sensible heat ratio lower than the sensible heat ratio of the cooling dehumidifying operation. Therefore, the point of the condition of the air-conditioned space 101 moves from the point P ₂ ′ toward the origin substantially along the vertical axis.
Cooling and dehumidification are performed so as to reach the point P0 under the condition ( ₁ ).

Area A₁Inside and the dehumidification load is too large
P, which is a point where the sensible heat load is large ₃Is the temperature t₀° C
Much higher, humidity is φ₀It is a little higher than%.
Point P ₃Is the area A₁The point P₁As in
First, the cooling and dehumidifying operation at the sensible heat ratio is performed,
The point under condition 101 moves and crosses the horizontal axis at the right of the origin.
Area A₄A point P in₃Move to '. Point P₃´
Temperature is t₀Much higher than ℃, humidity is φ₀About equal to%
No. Detected by humidity detecting means 401 and temperature detecting means 402
Upon receiving the signal, the controller 403 checks the condition of the air-conditioned space 101.
Point is area A₄And the actuator 407 determines
The control signal is sent to the actuator 407 so that the four-way valve 27
0 is maintained in the state shown by the solid line in FIG.

Therefore, the refrigerant evaporator 210 cools the processing air A, and the refrigerant evaporator 230 does not cool the regeneration air B. Therefore, the value of the sensible heat removed from the processing air A is substantially maintained. The controller 403 further includes a rotation speed controller 40.
4, the rotation speed controller 404 rotates the desiccant rotor 103 at a rotation speed lower than the normal rotation speed (for example, 1 to 5 rotations / hour). Therefore, the processing air A
, The amount of dehumidification (latent heat) dehumidified by the desiccant rotor 103 decreases.

Since the value of the water to be removed, that is, the value of the latent heat is largely reduced and the value of the sensible heat to be removed is substantially maintained, the dehumidifying air conditioner 1 mainly has a high sensible heat ratio higher than the sensible heat ratio of the cooling and dehumidifying operation. A sensible heat cooling operation in which heat is removed is performed. Processing point conditions of the air conditioning space 101 of the air A along a substantially horizontal axis to move toward the origin, perform as cooling and dehumidifying condition of the air conditioning space 101 becomes the point P _0.

FIG. 6 shows that the desiccant rotor 103
The sensible heat ratio of the dehumidifying air-conditioning apparatus 1 when rotated, that is, the ratio of the sensible heat deprived from the processing air A by the dehumidifying air-conditioning apparatus 1 to the sum of the sensible heat and the latent heat deprived from the processing air A (cooling capacity) Is an experimental value. In FIG. 6, the vertical axis represents the sensible heat ratio, the horizontal axis represents the temperature of the outside air, and the absolute humidity of the outside air is used as a parameter. FIG. 6 shows that the value of the sensible heat ratio is approximately 0.950 to 0.5.
970, indicating that the ratio is in the range of high sensible heat ratio.

FIG. 7 shows a case where the desiccant rotor is rotated 15 times per hour as an example, and the air-conditioned space 101 is on the middle floor of a building made of steel bars.
The sensible heat ratio between the outside air temperature (horizontal axis) and the air-conditioning load of the air-conditioned space 101 when the air-conditioned space 101 is ventilated twice per hour while cooling and dehumidifying so as to be 0.5 g / kg. It is the figure which displayed the relationship of (vertical axis) using absolute humidity as a parameter.

According to the figure, the sensible heat ratio is about 0.5 when the temperature is 32 ° C. and the humidity is 20 g / kg during the high summer.
75, but the outside air temperature is 27.5 ° C and humidity is 17 g /
In the case of kg, the sensible heat ratio is about 0.65. For example, when the outdoor air temperature is 27.5 ° C., if the cooling and dehumidifying is performed at a sensible heat ratio of 0.75, the latent heat is not sufficiently removed because the sensible heat ratio is too high. Look down. Therefore, residents feel very uncomfortable.

Referring to FIG. 8, an example of the mechanical arrangement of the dehumidifying air conditioner described above will be described. In the figure, the humidity detecting means 401 and the temperature detecting means 402 are omitted, and the equipment constituting the apparatus is housed in a cabinet 700. Cabinet 700 is formed as a rectangular parallelepiped housing made of, for example, a thin steel plate, and has a vertically upwardly-opened ceiling with an intake port for inhaling room air RA (process air A). A filter 501 is provided at the opening to prevent dust from the air-conditioned space 101 from being brought into the device. The blower 102 is installed in the cabinet 700 inside the filter 501, and the suction port of the blower 102 is supplied to the processing air A of the cabinet 700 through the filter 501.
To the suction port.

The outlet of the blower 102 is directed downward in the vertical direction, and the desiccant rotor 103 is disposed below the outlet with the rotation axis AX directed vertically. The desiccant rotor 103 is coupled to a variable speed motor 405, which is a driving machine also arranged in the vicinity thereof with the rotation axis directed in the vertical direction, by a belt, a chain, or the like as a torque transmitting member, and 1 to 5 rotations / hour or It is configured to rotate at a low speed of about 15 to 20 rotations / hour.

Also, including the heavy compressor 260,
Blowers 102, 140 which are movable elements or rotating bodies,
Most of the desiccant rotor 103 is collected in the lower part of the apparatus, the lower part of the cabinet 700, that is, near the foundation. Further, the compressors 260,
A sensible heat blower 140 is arranged in a space below the cabinet 700.

An air cooler 310 and a refrigerant evaporator 210 are arranged below the outlet of the blower 102 and further below the desiccant rotor 103. The air cooler 310 and the refrigerant evaporator 210 are integrally formed.

In this way, the path 107 of the processing air A
To 109 (main part) are directed from the uppermost part to the lowermost part of the cabinet 700, that is, are configured to guide the processing air A from the upper part to the lower part in a substantially vertical direction. Then, the processing air A that has exited the refrigerant evaporator 210 is configured to flow through a flow path extending substantially horizontally through the bottom of the cabinet 700. Further on, the route 111 is
Paths 107 to 109 from the upper part in the vertical direction to the lower part
The processing air A is formed in parallel from the bottom to the upper side from the lower side, and reaches the outlet of the processing air A provided on the ceiling portion of the cabinet 700 along with the intake of the processing air A to supply air SA.

On the other hand, on the lower side wall of the cabinet 700, an outside air OA intake is provided, in which a filter 502 is provided similarly to the filter 501 described above. A compressor 260 is provided inside the filter 502 and at the lowest part of the cabinet 700.

Above the compressor 260 and below the desiccant rotor 103 (below an almost half area opposite to the area of the desiccant rotor through which the processing air A described above passes).
, An air heater 320 is provided, and a refrigerant condenser 220 is further provided above the air heater 320. The air heater 320 and the refrigerant condenser 220 are connected to the air cooler 310 and the refrigerant evaporator 21.
As in the case of 0, they are integrally formed.

A circulation pump 330 is provided vertically below the refrigerant evaporator 210 and the air heater 320.

Above the desiccant rotor 103, a blower 140 is installed with its discharge port directed vertically upward and connected to the ceiling of the cabinet 700. Although the blower 140 is shown in FIG. 1 as being provided on the upstream side of the air heater 320, the operation is the same if the blower is provided at the last part of the flow path of the regeneration air B, just before the exhaust EX.

As described above, the regeneration air flow path is the path 1
25, 127 to 129 are formed so that the regeneration air B flows from the lowermost part to the uppermost part in the cabinet 700, that is, from the lower part in the vertical direction to the upper part.

The processing air A is directed downward from above in the vertical direction.
A partition 701 installed in the vertical direction is provided between the processing air flow path for flowing the air and the regeneration air flow path for flowing the regeneration air B upward from below in the vertical direction. are doing.

Next, a dehumidifying air conditioner 2 according to a second embodiment will be described with reference to FIG. FIG. 1 of the present dehumidifying air conditioner 2
Is different from the first embodiment in that a humidifier 105 for humidifying the processing air A is provided immediately before the processing air A is supplied to the air-conditioned space 101 by the air supply SA. . Humidifier 105 as humidification amount increasing / decreasing means of the present invention
Are the water supply pipe 410 in which the nozzle 411 is processed, the water supply pipe 4
And a control valve 408 with an actuator 409 connected to the control valve 10. The control valve 408 is actuated by an actuator 409,
Is controlled by a control signal from the controller 403,
Activate The control valve 408 controls water supply to the water supply pipe 410, and sprays water from the nozzle 411.

In the case where the condition of the air-conditioned space is in the area A ₄ (FIG. 5) and the humidity is low and the temperature is high, the cooling capacity of the air conditioner has a marginal latent heat treatment capacity, but the sensible heat treatment capacity is insufficient. ing. In this case, by performing humidification by the humidifier 105, sensible heat can be removed by heat of vaporization of water, so that sensible heat can be increased. In other words,
The latent heat treatment capability can be converted to a sensible heat treatment capability to increase sensible heat.

Referring to FIG. 10, the mechanical arrangement in the case where the dehumidifying air conditioner 2 includes the humidifier 105 will be described. The dehumidifying air conditioner 2 shown in FIG. 10 has a structure in which a humidifier 105 is added to the dehumidifying air conditioner 1 of FIG. Humidifier 105
Is attached to the lowermost part of the flow path flowing vertically downward of the regenerating air flow path, just before the flow path turns horizontally and makes a U-turn and flows vertically upward. As the humidifier, a well-known vaporizing humidifier may be used instead of the spray nozzle.

Referring to FIG. 11, a dehumidifying air conditioner 3 according to a third embodiment will be described. The configuration of the dehumidifying air conditioner 3 is different from that of the first embodiment shown in FIG. 1 in that a bypass path in which the processing air A bypasses the refrigerant evaporator 210 without providing a four-way valve in the refrigerant path. 113, and route 1
The control valve 412 is provided to control the flow rate of the processing air A flowing from 10 into the bypass path 113 and flowing to the path 111. The control of the bypass flow rate by the control valve 412 is not performed during the cooling dehumidification operation or the sensible heat cooling operation, that is, the processing air A is prevented from flowing through the bypass path 113, and the bypass flow rate is controlled during the dehumidification operation. It is desirable. The control of the control valve 412 is performed by sending a control signal from the controller 403 to the actuator 413 of the control valve 412.

Since the amount of the processing air A passing through the refrigerant evaporator 210 is controlled, the value of the sensible heat taken from the processing air A by the refrigerant evaporator 210 is controlled. By doing so, in the case of the dehumidifying operation, the amount of sensible heat taken from the processing air A by the refrigerant evaporator 210 can be reduced. In addition, the rotation speed of the desiccant roller is changed to a normal rotation speed (for example, 15 to 20).
Rotation / hour), the processing air A
, The value of the latent heat deprived of by the desiccant can be maintained, so that the sensible heat ratio can be reduced. Since a part of the processing air A bypasses the refrigerant evaporator 210, the liquid-phase refrigerant that has not evaporated in the refrigerant evaporator 210 evaporates in the refrigerant evaporator 230.

A bypass line through which the refrigerant bypasses the refrigerant evaporator 210 is provided, and a control valve is provided in the bypass line to control the bypass amount of the refrigerant, thereby controlling the amount of sensible heat with which the processing air A is taken by the refrigerant evaporator 210. However, the sensible heat ratio can be increased or decreased.

An adsorbing step of adsorbing moisture in the processing air with a moisture adsorber having a desiccant; a regenerating step of regenerating the desiccant with regenerating air; and a pumping step of pumping heat from the processing air to the regenerating air. A humidity detecting step of detecting a humidity of a space for supplying the processing air to which the moisture is adsorbed; a temperature detecting step of detecting a temperature of the space; a humidity detected in the humidity detecting step; A step of increasing / decreasing a sensible heat ratio of a dehumidifying cooling capacity for treating the processing air based on the temperature detected in the step; the processing air may be dehumidified by a dehumidifying method.

In the above-described dehumidifying method, the moisture adsorbing device is further configured so that the process air and the regenerated air are brought into contact with the desiccant alternately by rotating; Including a step of adjusting the number of revolutions of the adsorption device; a dehumidification method may be used.

The step of increasing / decreasing the sensible heat ratio may include a step of adjusting a humidification amount of the process air after the process air is cooled by the heat pump as a low heat source.

When the humidity of the space is higher than a predetermined humidity set value and the temperature is higher than a predetermined temperature set value, the operation is performed in a standard operation state, and the humidity of the space is lower than a predetermined humidity set value.
When the temperature of the space is higher than a predetermined temperature set value, the operation may be an operation in which the sensible heat ratio is increased from the standard operation state. Typically, the sensible heat ratio may be increased by lowering the rotation speed of a desiccant rotor, which is a moisture adsorption device. For example, when the number of revolutions in the standard operation state is 15 to 20 revolutions / hour, 1
Up to 5 rotations / hour can also be used. Further, the sensible heat ratio may be increased by humidifying the processing air cooled by the heat pump as a low heat source.

Further, when the humidity of the space is higher than a predetermined humidity set value and the temperature is lower than the predetermined temperature set value, the operation may be performed with the sensible heat ratio reduced from the standard operation state. Typically, the process air is cooled by the heat pump as a low heat source. By reducing the amount of cooling, the sensible heat ratio can be reduced.

[0084]

As described above, according to the present invention, since the sensible heat ratio increasing / decreasing means is operated based on the detected humidity and the detected temperature, it can cope with the air conditioning load under various weather conditions. In addition, it is possible to provide a dehumidifying air conditioner that can maintain the inside of a space at an optimum temperature and humidity even when weather conditions change.

[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 psychrometric chart for explaining the operation of the dehumidifying air conditioner of FIG. 1 during a dehumidifying cooling operation.

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

FIG. 4 is a psychrometric chart for explaining the operation of the dehumidifying air conditioner of FIG. 1 during a sensible heat cooling operation.

FIG. 5 is a graph illustrating an operation of the dehumidifying air conditioner of FIG. 1;

FIG. 6 is a graph showing the sensible heat ratio of the dehumidifying air conditioner when the desiccant rotor of the dehumidifying air conditioner of FIG. 1 is rotated once per hour.

7 is a graph showing the sensible heat ratio of the air conditioning load when the air conditioning space on the middle floor of the reinforced building is cooled and dehumidified at the rate of twice per hour by the dehumidifying air conditioning apparatus of FIG.

FIG. 8 is a schematic front sectional view showing an example of the actual structure of the dehumidifying air conditioner of FIG.

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

FIG. 10 is a schematic front sectional view showing an example of the actual structure of the dehumidifying air conditioner of FIG. 9;

FIG. 11 is a flowchart 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.

[Explanation of symbols]

 1, 2, 3 Dehumidifying air conditioner 101 Air conditioning space 102, 140 Blower 103 Desiccant rotor 105 Humidifier 154 Water circulation heat exchanger 210 Refrigerant evaporator 220 Refrigerant condenser 230 Refrigerant evaporator 250 Restrictor 260 Compressor 270 Four-way valve 310 Air Cooler 320 Air heater 330 Circulating pump 401 Humidity detecting means 402 Temperature detecting means 403 Controller 404 Torque transmitting member 405 Inverter motor 406 Speed controller 408 Control valve 409 Actuator 410 Water supply pipe 411 Nozzle 412 Control valve 413 Actuator

Claims (3)

[Claims] 1. A moisture adsorbing device having a desiccant that adsorbs moisture in processing air and is regenerated with regeneration air; a heat pump using the processing air as a low heat source and using the regeneration air as a high heat source; Humidity detecting means for detecting humidity in a space for supplying the adsorbed processing air; temperature detecting means for detecting a temperature in the space; humidity detected by the humidity detecting means; and humidity detected by the temperature detecting means. A sensible heat ratio increasing / decreasing means operated based on the temperature; 2. The sensible heat ratio increasing / decreasing means, the moisture adsorbing capacity increasing / decreasing means of the moisture adsorbing device, the humidifying amount increasing / decreasing means for humidifying the processing air to which moisture is adsorbed by the moisture adsorbing device, or the processing air by the heat pump. The dehumidifying air conditioner according to claim 1, wherein the air conditioner is at least one of means for increasing and decreasing the cooling amount of the air conditioner. 3. When the humidity of the space is lower than a desired value and the temperature is higher than a desired value, the sensible heat ratio is increased. When the humidity of the space is higher than a desired value and the temperature is lower than a desired value, The dehumidifying air conditioner according to claim 1 or 2, further comprising a controller that controls the sensible heat ratio increasing / decreasing means so as to decrease the sensible heat ratio.