JP2703149B2 - Reheat dehumidifying air conditioner - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a cooling means for cooling and dehumidifying return air from an air conditioning target area, a reheating means for reheating the cooled dehumidified air, and a circulating supply of reheat air to the air conditioning target area. A reheating type provided with a circulating means to perform, and a reheating control means for adjusting an output of the reheating means based on temperature detection such that an in-region temperature becomes a target value in a state where the cooling means is adjusted to a maximum output. The present invention relates to a dehumidifying air conditioner.

[0002]

2. Description of the Related Art Conventionally, in such a reheat type dehumidifying air conditioner, when the cooling means is adjusted to the maximum output, that is, when the cooling means performs the cooling and dehumidifying function at the maximum output, the output of the reheating means is reduced. In order to adjust the amount of air supplied by the circulation means, the following adjustment modes (a) and (b) have been adopted.

(A) As shown in FIG. 6, the supply air temperature for adjusting the output Hh of the reheating means 4B based on the detection of the supply air temperature so that the supply air temperature ts to the target area 2 becomes the set value tssN. The control means 19a 'and the internal temperature ti are set to the target value ti.
i, a variable air flow device 22 for adjusting the supply air volume Q to the target area 2 based on the detection of the in-region temperature is provided. And the supply air temperature control means 19a 'to adjust the output Hh of the reheating means 4B so that the in-region temperature ti becomes the target value tii as a whole.

(B) As shown in FIG.
The output control means x for adjusting the output Hh of the reheating means 4B based on the detection of the temperature in the region, and the adjusted output Hh of the reheating means 4B by adjusting the output of the air supply fan 13 so that the target value tii becomes the target value tii. (Specifically, a proportional relationship to the total cooling output obtained by subtracting the reheating output Hh of the reheating means 4B from the cooling output Hmax of the cooling means 4A). Form to provide.

[0005]

By the way, the situation at the time when the internal temperature ti decreases to the target value tii due to the start-up operation of the cooling, or the initial condition of the air conditioner in the intermediate period where the sensible heat load is small but the latent heat load is large. And so on.
When i is at the target value tii but the local humidity r is high,
In the conventional adjustment modes (a) and (b), the in-region state is adjusted as described below.

That is, in the adjustment mode (a) (see FIG. 7), the state in the area is point a1 '(temperature tii, relative humidity r
1 ′), the internal temperature ti is set to the target value tii.
The supply air volume Q is adjusted to a certain value Q1 'by the variable air volume device 22 so that the cooling means 4A is operated at the maximum output Hcmax at the supply air volume Q1' so that the device dew point temperature tp becomes tp1 '. And the supply air temperature t
The output H of the reheating means 4B so that s is set to the set value tssN.
h is adjusted to Hh1 ′.

In this adjustment state, the state in the range is the temperature t
While i is maintained at the target value tii, the point of change from the point a1 'toward the convergence point b1' in this adjustment state toward the humidity lowering side starts.

Then, the supply air temperature ts is constant (ts = ts
sN), the supply air volume Q is adjusted by the variable air volume device 22 so as to maintain the internal temperature ti at the target value tii.
1 ', and the cooling means 4A has a maximum output Hcmax
, The device dew point temperature tp gradually decreases (tp1 ′ → tp2 ′) with a decrease in the humidity r in the region, and
The output Hh of the reheating means 4B is controlled so that the supply air temperature ts is maintained at the set value tssN in response to the decrease in the device dew point temperature tp.
Is adjusted to the increasing side (Hh1 ′ → Hh2 ′), and in this mode, the convergence point in the adjustment state at each stage gradually shifts to the humidity decreasing side (b1 ′ → b2 ′), and following this, the in-region state is changed. It changes to the lower humidity side (a1 '→ a2').

However, when the in-region state changes to the humidity decreasing side to a certain extent and reaches an equilibrium point a3 '(a point where the in-region state point and the convergence point b3' in the adjustment state at that time coincide), the humidity decreases. , The sensible heat load Gt and the latent heat load Gx in the area are constant thereafter, and the cooling means output Hcmax, the supply air temperature tssN, the supply air volume Q1 ′, the device dew point temperature tp3 ′, and the reheating Means output Hh
In the adjustment state of 3 ', the in-region state is stabilized at the equilibrium point a3'.

On the other hand, in the adjustment mode (b) (see FIG. 9), the state in the area is point a1 ″ (temperature tii, relative humidity r
1 ″), the cooling means 4A outputs the maximum output Hc
Under the max, the output Hh of the reheating means 4B is adjusted to Hh1 ″ so as to maintain the in-region temperature ti at the target value tii,
Further, the supply air volume Q is adjusted to Q1 "in a predetermined inverse proportional relationship in accordance with the output Hh1" of the reheating unit 4B, and the cooling unit 4A outputs the maximum output Hcmax at the supply air volume Q1 ".
, The device dew point temperature tp becomes tp1 ″.

In this adjustment state, the state within the range is the temperature t
While i is maintained at the target value tii, the point a1 "starts changing from the point a1" to the humidity lowering side toward the convergence point b1 "in this adjustment state.

The cooling means 4A has a maximum output Hcma.
x, the device dew point temperature tp gradually decreases as the in-region humidity r decreases (tp1 ″ → tp2 ″).
On the other hand, the output Hh of the reheating means 4B is adjusted to the increasing side so that the internal temperature ti is maintained at the target value tii (H
h1 ″ → Hh2 ″), and accordingly, the supply air volume Q is adjusted to decrease in a predetermined inverse proportion relationship (Q1 ″ →
Q2 ″), and in this mode, the convergence point in the adjustment state at each stage gradually shifts to the humidity lower side (b1 ″ → b2 ″),
Following this, the state in the area changes to the humidity lower side (a1 ″).
→ a2 ").

However, as in the case of (a) above, the state in the area changes to a lower humidity level to some extent and the equilibrium point a
When the temperature reaches 3 "(the point where the in-region state point and the convergence point b3" in the adjustment state at that time coincide), the in-region state change to the humidity lowering side stops, and thereafter, the sensible heat load Gt and the latent heat load in the region. In a situation where Gx is constant, the cooling means output Hcm
ax, the supply air volume Q3 ", the device dew point temperature tp3", and the reheating means output Hh3 ", the state in the region is stabilized at the equilibrium point a3".

That is, in any of the above-mentioned embodiments (a) and (b), the lowering limits tp3 'and tp3 "of the device dew point temperature tp are determined by the in-region loads Gt and Gx. The decrease in humidity is also limited to a certain extent, and there has been a problem that the improvement in comfort due to low humidity cannot be sufficiently achieved.

An object of the present invention is to adjust the output of the reheating means and the amount of supplied air in a reasonable manner so that the humidity in the area can be reduced more effectively.

[0016]

The reheating type dehumidifying air conditioner according to the present invention is characterized by a cooling means for cooling and dehumidifying the return air from an area to be air-conditioned and a reheating means for reheating the cooled dehumidified air. Circulating means for circulating reheat air to the air conditioning target area; and, in a state where the cooling means is adjusted to the maximum output, the output of the reheating means based on temperature detection so that the temperature in the area becomes a target value. In the configuration provided with the reheat control means for adjusting, the setting means for setting the target value of the device dew point temperature in the cooling means to be lower as the humidity in the detection area decreases based on the detection of the humidity in the air conditioning target area, and In a state in which the cooling unit is adjusted to the maximum output, an air flow control unit that adjusts the supply air flow by the circulation unit based on the detection of the device dew point temperature is provided so that the device dew point temperature in the cooling unit becomes a target value. Is in the door, the operation and effect is as follows.

[0017]

In other words, in the conventional adjustment modes (a) and (b), the lower limit of the device dew point temperature tp is determined by the in-region loads Gt and Gx as described above. According to the characteristic configuration (see FIG. 3), when the supply air volume Q is adjusted so that the device dew point temperature tp becomes the target value tpm when the cooling means 4A is at the maximum output Hcmax, the device dew point temperature tp is reduced. Target value tpm
The humidity r in the detection area decreases (r1 → r2 → r3 → r4...).
...) (Tpm1 → tpm2 → tpm)
3 → tpm4...), It is possible to eliminate the lower limit of the device dew point temperature tp with respect to the decrease in the in-region humidity r as compared with the conventional embodiments. On the other hand, the convergence points b1, b2, b3...
a2, a3... can always be located on the lower humidity side.

[0018]

As described above, according to the characteristic structure of the present invention, it is possible to further reduce the humidity in the region while maintaining the temperature in the region at the target value, and to obtain higher comfort.

Also, by eliminating the lower limit of the dew point temperature of the apparatus,
By maintaining a large gradient of the cooling line from the in-region state point to the saturation state point in the cooling means on the psychrometric chart, the efficiency of lowering the in-region humidity can be improved as compared with the past, and the in-region condition can be comfortably achieved in a short time. It can be in a low humidity state.

[0020]

Next, an embodiment will be described.

In FIG. 1, reference numeral 1 denotes a package type air conditioner, which converts return air RA guided from the air conditioning target area 2 into the air conditioner by a return air passage 3 into a dehumidification heat exchanger 4A and a temperature control heat exchanger 4
B is passed sequentially to adjust the temperature and humidity, and the adjusted air is supplied as air supply SA to the target area 2 via the air supply path 5, and in parallel with this, the air is guided from outside to the cabin by the external air path 6. The outside air OA is supplied to the first and second two heat source heat exchangers 7A and 7A.
B is sequentially passed, and the passing air is discarded outside through the exhaust path 8.

Reference numeral 9 denotes an outside air distribution channel for mixing a part of the outside air OA with the return air RA passed through the dehumidifying heat exchanger 4A and the temperature control heat exchanger 4B. 10 denotes heat exchange for the first and second heat sources. This is a return air distribution channel that mixes a part of the return air RA with the outside air OA that passes through the devices 7A and 7B, and the mixture is used to ventilate the target area 2 in parallel with cooling and heating.

The dehumidifying heat exchanger 4A and the first heat source heat exchanger 7A constitute a single heat pump together with the first compressor 11A and the second expansion valve 12A.
And the second heat source heat exchanger 7B, the second compressor 11B,
Constitute another independent heat pump together with the expansion valve 12B,
A state where the heat exchangers 4A and 4B on the temperature and humidity adjustment side function as evaporators and the heat exchangers 7A and 7B on the heat source side function as condensers.
The state in which the heat exchangers A and 4B function as condensers and the heat exchangers 7A and 7B on the heat source side function as evaporators can be selected for each heat pump by switching the refrigerant flow mode.

Reference numeral 13 denotes an air supply fan, and 14 denotes an exhaust fan.

Reference numeral 15 denotes a sensor for detecting the supply air temperature ts,
6 is the temperature of the return air RA (that is, the internal temperature t of the target area 2).
i), a sensor for detecting the relative humidity of the return air RA (that is, the relative humidity r in the target area 2), and 18 a sensor for detecting the surface temperature tp of the dehumidifying heat exchanger 4A. , 19 are air conditioner controllers for controlling the operation of the air conditioner 1 based on the detection information of these sensors.

Reference numeral 20 denotes an air path pressure sensor for detecting the air path static pressure sp in the air supply path 5, and reference numeral 21 sets the air path static pressure sp in the air supply path 5 based on information detected by the air path pressure sensor 20. This is a fan controller that adjusts the output of the air supply fan 13 so as to maintain the value at the value spp.

Reference numeral 22 denotes an object area 2 corresponding to a deviation Δti between the room temperature ti detected by the room temperature sensor 23 and the target value tii.
Is a variable air flow device that adjusts the air supply amount q to each chamber 2a so as to adjust and maintain the room temperature ti of each chamber 2a at the target value ti.

Next, an operation control mode in cooling will be described with reference to FIGS.

When the operation start command is given, the air conditioner controller 19 starts the operation of the air supply fan 13 and the exhaust fan 14, and also controls the dehumidification heat exchanger 4A and the temperature control heat exchanger 4B, respectively. By operating the compressors 11A and 11B at the maximum output, the dehumidifying heat exchanger 4A and the temperature adjusting heat exchanger 4B are operated at maximum cooling outputs Hcmax and Hcmax, respectively. Start the start-up operation for air cooling function.

The variable air flow device 22 is fully opened because each room 2a has been in the cooling stopped state and the detected room temperature ti is higher than the target value tii (state point s in the psychrometric diagram of FIG. 3). Air supply volume Q (=
Σq) becomes the maximum air volume Qmax.

By the start-up operation in the maximum supply air flow state, the temperature ti (room temperature) in the target area 2 gradually decreases, and the accompanying dehumidifying heat exchanger 4A and temperature control heat exchanger 4B. The dehumidification function also gradually lowers the absolute humidity in the area.

When the internal temperature ti (room temperature) decreases to the target value tii (state point a1), the variable air flow amount device 22 adjusts the air supply amount q to each chamber 2a so as to maintain the internal temperature ti at the target value tii. The throttle is adjusted to adjust the overall supply air volume Q to a lower side.

On the other hand, the air conditioner controller 19 controls the return air RA
The startup operation is completed and the dehumidification temperature control operation is started based on the detection temperature ti having decreased to the target value tii.

In the dehumidification and temperature control operation, the air conditioner controller 1
Reference numeral 9 denotes a refrigerant circulation mode in which the dehumidifying heat exchanger 4A continuously functions as an evaporator and performs the air cooling function at the maximum cooling output Hcmax, while the temperature adjusting heat exchanger 4B functions as a condenser, and is cooled by the dehumidifying heat exchanger 4A. An operation mode in which the dehumidified air is reheat-controlled by the temperature-regulating heat exchanger 4B.

Then, the supply air temperature controller 19a in the air conditioner controller 19 detects the detected supply air temperature ts and the target air supply temperature t.
The reheat output Hh of the temperature control heat exchanger 4B is adjusted by adjusting the output of the second compressor 11B so as to adjust and maintain the supply air temperature ts to the target supply air temperature tss according to the deviation Δts from ss.

In other words, in a state where the supply air volume is adjusted by the variable air volume device 22, the variable air volume device 22 and the above-mentioned air supply temperature control unit 19a use these as air supply temperature control means, and the inside temperature ti is adjusted. The reheat output Hh of the temperature control heat exchanger 4B is adjusted so as to reach the target value tii.

Further, the air conditioner controller 19 controls the reheat output Hh.
In parallel with the adjustment of, the calculating unit 19b sequentially determines the target device dew point temperature tpm according to the detected relative humidity r of the return air RA,
On the other hand, the supply air temperature setting unit 19c determines the surface temperature t of the dehumidifying heat exchanger 4A according to the deviation Δtp between the detected surface temperature tp of the dehumidifying heat exchanger 4A and the target device dew point temperature tpm.
The target supply air temperature tss is changed so that p (that is, the temperature corresponding to the device dew point temperature) is set to the target device dew point temperature tpm.

That is, when the target air supply temperature tss is changed, the internal temperature ti (room temperature) is changed to the target value ti in response to the change.
In order to make i, the variable air volume device 22 changes the supply air volume Q, and by changing the supply air volume Q, the maximum cooling output Hcm
The surface temperature tp of the dehumidifying heat exchanger 4A that functions to cool at ax
Is adjusted to the target device dew point temperature tpm,
In other words, in the state where the supply air volume is adjusted by the variable air volume device 22 and the reheat output is adjusted by the above-described air supply temperature control unit 19a, the variable air volume device 22, the supply air temperature control unit 19
a, and the above-described supply air temperature setting unit 19c uses these as the air volume control means so that the surface temperature tp of the dehumidifying heat exchanger 4A becomes the target device dew point temperature tpm and the supply air volume Q
To control the adjustment.

The operation unit 19b is provided with a return air R as shown in FIG.
A relative humidity r (area humidity) and target device dew point temperature tpm
The target device dew point temperature tpm corresponding to the detected relative humidity r of the return air RA is determined based on the setting relationship (tpm = F (r)).
F (r)) is the temperature of the contact point p at the tangent drawn from the state point of each relative humidity r at the temperature tii on the psychrometric chart with respect to the saturation line L on the psychrometric chart.
m (provided that tpm = tpmo (constant) for a relative humidity r above the upper limit of the normal change range, and tpm = tpmu (constant) for a humidity r below the lower limit of the normal change range. ))

In the dehumidification and temperature control operation described above, the state in the area at the time of completion of the start-up operation is indicated by a point a1 (temperature tii) in FIG.
, The target device dew point temperature tpm is determined to be tpm1, whereas the dehumidifying heat exchanger 4A performs a cooling function with the maximum cooling output Hcmax,
Further, the air supply amount Q is adjusted so that the variable air amount device 22 maintains the in-region temperature ti at the target value tii.
Temperature control heat exchanger 4B so that
Surface temperature tp of dehumidifying heat exchanger 4A (that is, device dew point temperature) under the condition where reheat output Hh of is adjusted.
The target supply air temperature tss is changed and adjusted so that the target supply dew point temperature tpm1.
1 (= supply air temperature ts), supply air volume Q1, reheat output Hh1
Adjustment state.

In this adjustment state, the state within the range is the temperature t
While i is maintained at the target value tii, it starts to change from the point a1 toward the humidity lowering side toward the convergence point b1 in this adjustment state.

Thereafter, the relative humidity r in the area decreases (r1
→ r2 → r3 → r4 ...)) and the target device dew point temperature tp
m is sequentially changed to the lower side (tpm1 → tpm2 → tpm3)
On the other hand, in the same manner as described above, the dehumidifying heat exchanger 4A performs the cooling function at the maximum cooling output Hcmax, and the variable air flow rate device 22 sets the in-region temperature ti to the target value tii.
Under the condition that the reheat output Hh of the temperature control heat exchanger 4B is adjusted so that the supply air amount Q is adjusted to maintain the supply air temperature ts at the target supply air temperature tss. Air volume Q
(Q1 → Q2 → Q3 → Q4...) And the reheating output Hh (Hh1 → Hh2 → Hh3 → Hh4...)
...), the surface temperature tp of the dehumidifying heat exchanger 4A.
(That is, the device dew point temperature) so that the target device dew point temperature tpm at each stage is the target supply air temperature tss (the supply air temperature t
s) is gradually changed and adjusted to the lower side, and in this mode, the convergence point b in the adjustment state at each stage is always located on the lower humidity side than the in-area state point a at that time, and the relative humidity r in the area
(B1 → b2 → b3 → b)
4), and the state in the area changes to the lower humidity side (a1, a2, a3, a4,...).

In the dehumidification and temperature control operation, the variable device 22
Reaches the maximum opening degree, the load in the region increases rapidly, etc., so that the detected temperature ti of the return air RA becomes the set upper limit temperature tio (tio> tii, for example, tio = tii +
1 ° C deg) or more, or the dehumidification progresses, and the detected relative humidity r of the return air RA becomes less than or equal to the target humidity rm, or the reheat output is adjusted in the reheat output adjustment of the temperature control heat exchanger 4B. When the output Hh becomes equal to or lower than the set lower limit output Hhmin, the air conditioner controller 19 ends the dehumidification temperature control operation and switches the operation state to the normal cooling operation.

In the normal cooling operation, the air conditioner controller 19
Is a refrigerant circulation mode in which each of the heat exchanger for dehumidification 4A and the heat exchanger for temperature control 4B functions as an evaporator, and is cooled by air with both the heat exchanger for dehumidification 4A and the heat exchanger for temperature control 4B.

Then, in a situation where the variable air volume device 22 continuously adjusts the supply air volume Q so as to maintain the in-region temperature ti at the target value tii, the supply air temperature setting section 19c of the air conditioner controller 19 sets the target air supply volume. The set value tssN for the normal cooling operation is fixedly adopted as the temperature tss. On the other hand, the supply air temperature control unit 19a calculates the deviation between the detected supply air temperature ts and the target supply air temperature tssN for the normal cooling operation. Accordingly, the outputs of the first and second compressors 11A and 11B are adjusted in a predetermined sharing relationship to adjust and maintain the supply air temperature ts to the target supply air temperature tssN for normal cooling operation. Cooling output H of each of the heat exchanger 4A and the temperature control heat exchanger 4B
Adjust the sum of c and Hc '.

The equilibrium state when the normal cooling operation is continued is shown by a dashed line in FIG. 3, and when the operation is switched from the dehumidification temperature adjustment operation to the normal cooling operation, the in-region state is at the time of switching from the dehumidification temperature adjustment operation. The humidity gradually increases from the state point to the state point aN in the equilibrium state indicated by the dashed line, but the air conditioner controller 19
In the normal cooling operation, the detected relative humidity r of the return air RA becomes equal to or higher than the set upper limit humidity ro, or the detected temperature ti of the return air RA becomes the set lower limit temperature ti (tiu <tii, for example, tiu = tii-1 ° C.). deg) or less, the operation state is switched from the normal cooling operation to the dehumidification and temperature adjustment operation again, and thereafter, the normal cooling operation and the dehumidification and temperature adjustment operation are alternately repeated until an operation stop command is given.

In each of the switching from the dehumidifying temperature control operation to the normal cooling operation and the switching from the normal cooling operation to the dehumidifying temperature control operation, the following switching conditions are satisfied for a predetermined time ΔT after the switching. In this case, switching of the operating state is suppressed, thereby preventing hunting switching of the operating state.

[Another embodiment] Next, another embodiment will be described.

In the above-described embodiment, the target apparatus dew point tpm is determined based on only the relative humidity r in the area by adopting the setting relation (tpm = F (r)) as shown in FIG.
As shown in (2), a mode may be adopted in which the target device dew point tpm is determined in a state in which a correction is made on the deviation between the target value tii of the internal temperature ti and the target temperature tii based on the internal relative humidity r and the internal temperature ti.

In the above-described embodiment, when there is a difference between the target room temperatures tii of the plurality of target rooms 2a, the average value of the target room temperatures ti and the values determined by proportional distribution according to the volume of each target room 2a. May be set as the unified intra-area temperature target value tii in the air-conditioning target area 2.

As a basic form, the output Hh of the reheating means 4B is adjusted based on the detection of the in-region temperature so that the in-region temperature ti becomes the target value tii, while the cooling means 4A performs the cooling function with the maximum cooling output Hcmax. Output control means x,
Further, a predetermined inverse proportional relationship Q = I (Hh) with respect to the adjusted output Hh of the reheating means 4B by adjusting the output of the air supply fan 13.
(Or a fan that adjusts the supply air volume Q with a predetermined proportional relationship Q = J (Hmax−Hh) to the total cooling output obtained by subtracting the reheating output Hh of the reheating unit 4B from the cooling output Hmax of the cooling unit 4A. In the form in which the control means y is provided (see FIG. 8), setting means for setting a target device dew point temperature tpm lower as the detection area humidity r decreases, and cooling means for setting the target device dew point temperature tpm Based on the detection of the device dew point temperature tp at 4A, the inversely proportional relationship Q = I (Hh) (or the cooling unit output Hm) with respect to the reheating unit output Hh used for adjusting the air supply amount is adopted.
The proportional relationship Q = J (Hmax-Hh)) to the total cooling output obtained by subtracting the reheating means output Hh from ax is changed,
An embodiment may be adopted in which the supply air volume is adjusted so that the device dew point temperature tp is set to the target device dew point temperature tpm.

In order to set the target device dew point temperature tpm to be lower as the in-region humidity r decreases, what specific value of the target device dew point temperature tpm is to be adopted for the in-region humidity r depends on device design conditions and the like. The temperature is not limited to the temperature at the contact point of the tangent line drawn from the in-region state point to the saturation line L on the psychrometric chart.

Instead of changing the supply air volume Q by the fan output adjustment or the variable air volume device 22, the supply air volume Q may be changed by a damper interposed in the return air passage 3 or the like.

In the claims, reference numerals are provided for convenience of comparison with the drawings, but the present invention is not limited to the configuration of the attached drawings by the entry.

[Brief description of the drawings]

FIG. 1 is a configuration diagram of an apparatus.

FIG. 2 is a control flowchart.

FIG. 3 is a psychrometric chart showing a state change.

FIG. 4 is a graph showing the relationship between the in-region humidity and the target device dew point temperature.

FIG. 5 is a graph showing a form of determining a target device dew point temperature in another embodiment.

FIG. 6 is a configuration diagram of a conventional device.

FIG. 7 is a psychrometric chart showing a state change by the conventional device.

FIG. 8 is a configuration diagram of another conventional apparatus.

FIG. 9 is a psychrometric chart showing a state change by another conventional device.

[Explanation of symbols]

 2 Air-conditioning target area 3, 5, 13 Circulation means 4A Cooling means 4B Reheating means 19b Setting means 19a Air flow control means (reheat control means) 19c Air flow control means (reheat control means) 22 Air flow control means Hcmax Cooling means maximum output Hh Reheating means output Q Air supply amount RA Return air r Humidity in the area SA Reheated air ti Temperature in the area tii Target value tp Device dew point temperature tpm Target value

Claims (1)

(57) [Claims] 1. A cooling means (4A) for cooling and dehumidifying return air (RA) from an air conditioning target area (2), a reheating means (4B) for reheating the cooled dehumidified air, and a reheat air (SA). ) To the air-conditioning target area (2).
(5), (13), and in the state where the cooling means (4A) is adjusted to the maximum output (Hcmax), the temperature in the region (ti)
A reheat type dehumidifying air-conditioning apparatus provided with reheat control means (19a) and (22) for adjusting the output (Hh) of the reheat means (4B) based on temperature detection so that the target value (tii) is obtained. The target value (tpm) of the device dew point temperature (tp) in the cooling means (4A) is set lower as the humidity (r) in the detection area decreases based on the detection of the humidity in the area (2). Setting means (19b) and the cooling means (4
In the state where A) is adjusted to the maximum output (Hcmax), the cooling unit (4A) is set based on the detection of the device dew point temperature (tp) such that the device dew point temperature (tp) becomes the target value (tpm). Air volume control means (19) for adjusting the supply air volume (Q) by the circulation means (3), (5), (13)
a) A reheat type dehumidifying air conditioner provided with (19c) and (22).