JPH05296531A - Air conditioner - Google Patents

Abstract

PURPOSE:To perform an efficient reduction of a humidity within a region by a method wherein a dew formation point temperature of a target device is determined in response to a detected humidity within the region, and an output of a cooling means and an amount of feeding air ate adjusted in such a manner that the detected temperature within the region may become the target temperature while the dew formation point temperature of the device becomes the dew formation point temperature of the target device. CONSTITUTION:A ventilation RA from an air conditioned region 2 is cooled with a cooling means 4, and the cooling air is supplied as a suction air SA to an air conditioned region 2 through circulation means 3, 5 and 11. Output from the cooling means 4 and an amount of suction air Q are adjusted by a control means 19 in response to a sensing of temperature in such a manner that the temperature within the region becomes the target temperature. In this case, the control means 19 determines the dew formation point temperature of the target device by a calculation means 19a in response to a humidity within the detected region in such a manner that the dew formation point temperature for target device is decreased as the humidity within the detected region is decreased. Then, the output of the cooling means 4 and the amount of air supplied Q are adjusted with an adjusting means in such a manner that the detected temperature within the region may become the target temperature while the dew formation point temperature becomes the dew formation point temperature of the target device. With such an arrangement, an efficient reduction of humidity within the region can be carried out up a much lower humidity region.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a circulation means for cooling return air from an air conditioning target area by a cooling means and supplying the cooling air to the air conditioning target area as supply air, and a temperature inside the area to a target temperature. Thus, the present invention relates to an air conditioner equipped with control means for adjusting the output of the cooling means and the amount of air supply based on temperature detection.

[0002]

2. Description of the Related Art Conventionally, in the air conditioner as described above,
The following (a) or (b) has been adopted as a specific mode of adjusting the output of the cooling means and the supply air amount by the control means.

(A) Temperature in detection zone ti and target temperature tii
The output H of the cooling means is adjusted in accordance with the deviation Δti from the output of the cooling means, and the supply air amount Q is adjusted in a predetermined proportional relationship with the output H of the cooling means.

(B) Detection area temperature ti and target temperature tii
The supply air amount Q is adjusted in accordance with the deviation Δti from the output air flow rate, and the output H of the cooling means is adjusted so as to maintain the supply air temperature ts at a constant value tss with respect to the adjustment of the supply air amount.

[0005]

By the way, the situation at the time when the internal temperature ti falls to the target temperature tii due to the start-up operation of the cooling, or the initial situation where the latent heat load is large but the sensible heat load is large in the intermediate period, etc. And the internal temperature ti
Is at the target temperature tii but the internal humidity r is high,
In the adjustment mode of (a) above (see FIG. 6), while the in-zone state is the point a (humidity ra), the in-zone temperature ti is maintained at the target temperature tii under the situation where the in-zone humidity r is high. The output H of the cooling means (output per unit air supply amount on the psychrometric chart) is adjusted (H = H1), and the air supply amount Q is adjusted in a predetermined proportional relationship according to the adjusted output H1 of the cooling means. , The cooling line a-p1 (apparatus dew point temperature tp1) is operated on the air diagram.

In this adjusted state, the accompanying dehumidifying function associated with air cooling by the cooling means gradually changes the in-zone state to the humidity lowering side, and with this in-zone state change, the readjustment of the cooling means output H with respect to the in-zone state change, And, in a state in which the supply air amount is adjusted in proportion thereto, the cooling line gradually shifts to the lower side as shown by the chain line in the figure.

Then, when the internal state changes to the state of a point b (humidity rb) where the load G (the sum of the sensible heat load Gt and the latent heat load Gx) and the output H (= H2) of the cooling means balance, the inside of the region changes. The decrease of the humidity r stops, and equilibrium is reached in the state of the cooling line bp2 (device dew point temperature tp2).

On the other hand, in a similar situation where the internal temperature ti is at the target temperature tii but the internal humidity r is high (b)
In the adjustment mode (see FIG. 7), the in-zone state is point a (humidity r
In the situation where the inside humidity r is high in a) and the supply air temperature ts does not decrease to the set value tss even if the cooling means is operated at the maximum output Hmax, the cooling means outputs the maximum output Hma.
In contrast to this, the air supply amount Q is adjusted so that the in-zone temperature ti is continuously maintained at the target temperature tii, and is operated in the state of the cooling line a-p3 (device dew point temperature tp3) on the air diagram. To be done.

In this adjusted state, the internal dehumidifying function of the cooling means gradually changes the in-zone state to the humidity lowering side,
With the change in the in-zone state, the cooling line gradually shifts to the lower side as shown by the chain line in the figure in a state in which the supply amount adjustment is performed while keeping the cooling means output H at the maximum Hmax for a while. However, when the in-zone state changes to the point c and the supply air temperature ts drops to the set value tss (note that in this description, the supply air temperature ts = approximate device dew point temperature tp,
It is assumed that the device dew point temperature tp has dropped to the set value tss), and thereafter, the supply air temperature ts (device dew point temperature tp).
While adjusting the output H of the cooling means to the lower side so as to maintain the set value tss, the supply air amount Q is adjusted so as to maintain the in-zone temperature ti at the target temperature tii. Is continuously changed, and the cooling line moves further downward from c-p4.

Then, when the internal state changes to a state of a point d (humidity rd) where the load G (the sum of the sensible heat load Gt and the latent heat load Gx) and the output H (= H3) of the cooling means balance, The decrease in the humidity r stops, and equilibrium is reached in the state of the cooling line d-p4 (apparatus dew point temperature tp4 (= tss)).

However, in any of the above forms (a) and (b), the cooling line gradient is rapidly reduced as the internal humidity r decreases, and the dehumidifying efficiency Δx / Δh in the accompanying dehumidifying function of the cooling means is increased. Significant decrease (Δx1 / Δ in Fig. 6)
h1 to Δx2 / Δh2, and in FIG. 7, Δx3 / Δh3 to Δx
4 / Δh4), there is a problem that the efficiency of lowering the internal humidity r is low.

An object of the present invention is to efficiently reduce the internal humidity by adjusting and maintaining the internal temperature to the target temperature by the accompanying dehumidifying function of the cooling means.

[0013]

A first characteristic configuration of an air conditioner according to the present invention is that the return air from the air conditioning target area is cooled by a cooling means, and the cooling air is supplied to the air conditioning target area as supply air. In the configuration including a circulation means and a control means for adjusting the output of the cooling means and the supply air amount based on the temperature detection so that the temperature in the zone becomes a target temperature, the control means is configured to reduce the humidity in the zone to be detected. Calculation means for determining the target device dew point temperature according to the humidity in the detection area in the form of lowering the target device dew point temperature, and cooling so that the temperature in the detection area becomes the target temperature when the device dew point temperature becomes the target device dew point temperature. It is provided with adjusting means for adjusting the output of the means and the supply air amount, and the operation and effect thereof are as follows.

[0014]

In other words, in the above-mentioned conventional configuration of (a) shown in FIG. 6, the device dew point temperature tp is lowered due to the device characteristics because the proportional adjustment relationship between the cooling means output H and the supply air amount Q is determined. Since the limit point is determined to be the specific point p2 with respect to the load condition in the target area, and in the conventional form of (b) shown in FIG. 7, the cooling means is maintained so as to maintain the supply air temperature ts at the constant value tss. In the characteristics of the apparatus by adjusting the output H of the device, the lower limit point of the apparatus dew point temperature tp is determined to be the specific point p4. Therefore, in any form, the cooling line gradient decreases with the decrease of the internal humidity r, and However, the accompanying reduction in dehumidification efficiency of the associated dehumidification function is significant.

On the other hand, according to the first characteristic configuration of the present invention (see FIG. 5), the humidity r in the detection area decreases (r1-r2-
r3 ...), the target device dew point temperature tpm is lowered (tp
m1-tpm2-tpm3 ...), the target device dew point temperature tpm is determined according to the detection region humidity r, and the device dew point temperature tp becomes the target device dew point temperature tpm at each decrease in the region humidity r. Since the output H and the supply air amount Q of the cooling means are adjusted so that the temperature ti becomes the target temperature tii, the lowering limit of the device dew point temperature tp with respect to the lowering of the in-zone humidity r is eliminated as compared with the conventional modes ( pm1-pm2-pm3 ...), and by selecting an appropriate relationship for the determination relationship of the target device dew point temperature tpm with respect to the humidity r in the detection area, the cooling line gradient can be made smaller than that in the conventional form with respect to the decrease in the humidity r in the area. Can also be maintained at a high level, and the dehumidifying efficiency Δxm / Δhm in the accompanying dehumidifying function of the cooling means can be maintained at a high level.

[0016]

As described above, according to the first characteristic configuration of the present invention, it is possible to efficiently reduce the internal humidity by the accompanying dehumidifying function of the cooling means while maintaining the internal temperature at the target temperature. As a result, the humidity in the area can be made comfortable in a short period of time, and the humidity in the area can be adjusted to a lower humidity than in the past.

[Second Characteristic Configuration of the Present Invention] In a second characteristic configuration of the air conditioner according to the present invention, the arithmetic means calculates the temperature of the contact point at the tangent line drawn from the in-zone state point to the saturation line in the psychrometric chart. The target device dew point temperature is given.

That is, the gradient of the tangent line drawn from the in-zone state point to the saturation line in the air diagram becomes the maximum gradient in the straight line group drawn from the in-zone state point to each point on the saturation line.

Therefore, if the above-mentioned first characteristic construction is carried out in such a manner that the temperature of the contact point at such a tangent line is given as the target device dew point temperature at each point in time when the internal humidity gradually decreases, cooling with the maximum gradient is made at each point. It is possible to obtain the highest accompanying dehumidifying effect by displaying a line, which makes it possible to reduce the internal humidity more efficiently and to obtain a higher operating efficiency in terms of the energy consumption of the cooling means against the humidity reduction rate. it can.

[0020]

EXAMPLES Next, examples will be described.

In FIG. 1, reference numeral 1 denotes a package type air conditioner, in which a return air RA introduced from an air conditioning target area 2 into a return air path 3 is temperature-controlled by a heat-conditioning heat exchanger 4, and its temperature-controlled air is supplied. Is supplied as the supply air SA to the target area 2 through the supply air passage 5, and in parallel with this, the outside air OA guided from the outside to the inside by the outside air passage 6 is passed to the heat source heat exchanger 7, The configuration is such that the passing air is discarded outdoors via the exhaust passage 8.

Reference numeral 9 denotes an outside air flow passage for mixing a part of the outside air OA with the return air RA to be passed to the temperature control heat exchanger 4, and 10 is return air RA to the outside air OA to be passed to the heat source heat exchanger 7.
It is a return mood flow path that mixes a part of.

The heat exchanger 4 for temperature control and the heat exchanger 7 for heat source constitute a heat pump together with the compressor 11 and the expansion valve 12, and the heat exchanger 4 for temperature control is evaporated in cooling by switching the refrigerant circulation mode. As the heat source heat exchanger 7 and the heat source heat exchanger 7 as the condenser, while in heating, the temperature control heat exchanger 4 functions as the condenser, and the heat source heat exchanger 7 as the evaporator. Make it work.

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

Reference numeral 15 denotes a sensor for detecting the supply air temperature ts, 1
6 is the temperature of the return air RA (that is, the temperature t in the target area 2).
i), 17 is a sensor that detects the humidity of the return air RA (that is, the internal humidity r of the target area 2), and 18 is a sensor that detects the surface temperature tp of the temperature control heat exchanger 4, Is an air conditioner controller that controls the operation of the air conditioner 1 based on the information detected by these sensors.

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

Reference numeral 22 denotes a supply to each room 2a so as to maintain the room temperature ti of each room 2a in the target area 2 at the target temperature tii in accordance with the deviation Δti between the room temperature ti detected by the room temperature sensor 23 and the target temperature tii. It is a variable air volume device that adjusts the air volume q.

Next, the operation control mode in cooling will be described with reference to FIGS. 2 and 3.

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 operates the compressor 11 at the maximum output in the cooling medium circulation mode. Maximum output Hma for heat exchanger 4 for temperature control
Start the start-up operation with the cooling function at x.

The air flow rate control device 22 is in the fully open state because each room 2a is in the cooling stopped state and the detected room temperature ti is higher than the target temperature tii (state point s in the air diagram of FIG. 3), and the air conditioning is performed. Air supply amount Q (=
Σq) is the maximum.

By this start-up operation in the maximum supply amount state, the temperature ti (room temperature) in the target area 2 gradually decreases,
In addition, the accompanying absolute dehumidifying function of the temperature control heat exchanger 4 causes the absolute humidity in the region to gradually decrease.

When the internal temperature ti (room temperature) is lowered to the target temperature tii (state point a), the air flow rate changer 22 adjusts the air supply amount q to each chamber 2a so as to maintain the internal temperature ti at the target temperature tii. Adjust the throttle to adjust the total air supply Q to the lower side.

On the other hand, the air conditioner controller 19 completes the start-up operation and starts the dehumidifying operation based on the detected return air temperature ti falling to the target temperature tii.

In this dehumidifying operation, the air conditioner controller 19 sequentially determines the target device dew point temperature tpm according to the detected return air humidity r in the calculation unit 19a, and the target device dew point temperature tpm and the temperature control heat exchanger 4 are also set. The surface temperature tp of the temperature control heat exchanger 4 (that is, the temperature corresponding to the device dew point temperature) is adjusted to the target device dew point according to the deviation Δtp from the detected surface temperature tp under the control of the air supply amount Q by the air flow rate device 22. The output H of the temperature adjustment heat exchanger 4 is adjusted by adjusting the output of the compressor 11 so that the temperature becomes tpm.

The calculation unit 19a determines the target corresponding to the detected return air humidity r based on the setting relationship (tpm = F (r)) between the return air humidity r (in-zone humidity) and the target device dew point temperature tpm as shown in FIG. The device dew point temperature tpm is determined,
As the above setting relationship (tpm = F (r)), the temperature of the contact point p at the tangent line drawn from the saturation state L to the saturation line L at the temperature ti on the air diagram is the target device dew point temperature. Determined to be given as tpm (however, for humidity r that exceeds the upper limit of the normal change range, tpm = tp
humidity (constant), or humidity r below the lower limit of the normal change range
Is set to tpm = tpmu (constant)).

Depending on the area load condition and the air supply amount adjustment state by the air flow rate changer 22, the output H of the temperature adjustment heat exchanger 4 should be adjusted so that the surface temperature tp becomes the target device dew point temperature tpm. In the above, the output H of the temperature adjustment heat exchanger 4 may be maintained at the maximum output Hmax following the start-up operation.

In the above dehumidifying operation, the internal temperature ti
Is the target temperature ti due to the adjustment of the air supply amount by the air flow amount device 22.
While being adjusted and maintained at i, the internal humidity r decreases due to the accompanying dehumidifying function of the temperature control heat exchanger 4.
(R1-r2-r3 ...), the target device dew point temperature tpm is also gradually decreased ((tpm1-tpm2b).
-Tpm3 ...), and the exit point p of the heat exchanger 4 for temperature control is
m gradually shifts to the low humidity side (in absolute humidity), whereby the slope of the cooling line showing the air cooling process in the temperature control heat exchanger 4 is maintained largely regardless of the decrease in the internal humidity r, and the accompanying dehumidification. Dehumidification efficiency of the function is kept high.

In this dehumidifying operation, the detected return air humidity r becomes equal to or lower than the target humidity rm, or the variable air volume device 22 reaches the throttling limit or the load in the region is rapidly reduced. And the detected return air temperature ti is set lower limit temperature tiu (tiu <tii, for example, tiu = tii-2 ° C.
When it becomes deg) or less, the air conditioner controller 19 completes the dehumidification operation and switches the operation state to the normal cooling operation.

In this normal cooling operation, the air conditioner controller 19
Is the deviation Δt between the detected supply air temperature ts and the target supply air temperature tss.
Adjust the air supply temperature ts to the target air supply temperature tss according to s
The output H of the temperature control heat exchanger 4 is adjusted by adjusting the output of the compressor 11 so as to maintain the temperature H in the region by adjusting the supply air amount by the air flow rate changing device 22 as in other operating states. Room temperature) at the target temperature tii.

The equilibrium state when the above normal cooling operation is continued is shown by a broken line in FIG. 3. When the dehumidifying operation is switched to the normal cooling operation, the in-zone state is the state point e or e at the time of switching from the dehumidifying operation. ', The humidity gradually increases toward the state point d in the equilibrium state indicated by the broken line. On the other hand, in the normal operation, the detected return air temperature ti is around the target temperature tii in the normal operation. Within the allowable temperature range (tii-Δt <ti <tii + Δ
In the state of t), the humidity r in the detection range is the set upper limit humidity ro.
In the above case, the operating state is switched from the normal cooling operation to the dehumidifying operation again, and thereafter, the normal cooling operation and the dehumidifying operation are alternately repeated until the operation stop command is given.

In each of the switching from the dehumidifying operation to the normal cooling operation and the switching from the normal cooling operation to the dehumidifying operation, even if the following switching condition is satisfied for a predetermined time ΔT after the switching, The switching is restrained so that the hunting-like switching of the operating state is prevented.

[Other Embodiments] Next, other embodiments will be listed.

In the above-described embodiment, in the dehumidification operation, the surface temperature tp (that is, the surface temperature tp of the temperature control heat exchanger 4 is adjusted while the air supply amount Q is adjusted by the air flow rate changing device 22 so as to maintain the in-zone temperature ti at the target temperature tii. , Device dew point temperature) is set to the target device dew point temperature tpm so that the output H of the temperature control heat exchanger 4 is adjusted. However, instead of this, in the dehumidifying operation, the in-zone temperature ti and the target temperature tii Deviation Δti
Based on the above, while adjusting the output H of the temperature control heat exchanger 4 so that the in-zone temperature ti becomes the target temperature tii, the temperature control heat exchanger 4 is controlled by the intervention control of the air supply fan 13 and the air flow rate control device 22. Surface temperature tp is the target device dew point temperature tpm
A configuration for adjusting the supply air amount Q may be adopted.

In the above-described embodiment, when the internal humidity r is reduced to the target humidity rm by the dehumidifying operation, the operation is switched to the normal cooling operation of the operation mode in which the device dew point temperature tp becomes higher than the target device dew point temperature tpm at that time. However, instead of this, when the internal humidity r decreases to the target humidity rm by the dehumidifying operation, the output H of the cooling means (the temperature control heat exchanger 4) and the supply air amount Q are changed to the internal humidity r. Is maintained at the target humidity rm, and the internal temperature ti is the target temperature ti.
A configuration may be adopted in which the value is adjusted to reach equilibrium while being maintained at i.

As the cooling operation mode, the detection area temperature ti
Deviation Δ between the detected return air temperature and the target temperature tii
In which the output H of the cooling means 4 is adjusted so that the in-zone temperature ti becomes the target temperature tii according to ti, and the supply air amount Q is adjusted in accordance with the adjusted output H of the cooling means 4 in a predetermined proportional relationship. The target device dew point temperature tpm is lowered in accordance with the decrease of the humidity r in the detection area. The calculation means is provided for determining the target device dew point temperature tpm in accordance with the humidity r in the detection area. The output H of the cooling means 4 is adjusted so that the temperature ti becomes the target temperature tii, and the supply air amount Q during the cooling operation is adjusted so that the device dew point temperature tp becomes the target device dew point temperature tpm under the output adjustment. The dehumidifying operation is performed by adjusting the temperature outside the predetermined proportional relationship, or the output H of the cooling means 4 is adjusted so that the device dew point temperature tp becomes the target device dew point temperature tpm, and the in-zone temperature ti is adjusted under the output adjustment. To Dehumidifying operation mode adjusting deviates from the predetermined proportional relation during cooling operation the air supply amount Q to the target temperature tii, and operably configured to either,
A configuration may be adopted in which the cooling operation and the dehumidifying operation are switched at appropriate times according to the detected humidity r and the temperature in the detection area ti.

As a mode of adjusting the output H of the cooling means 4 and the supply air amount Q with respect to the target device dew point temperature tpm, one of the output H of the cooling means 4 and the supply air amount Q is set to the detection area temperature ti. According to the deviation Δti between the target dew point temperature iii and the target dew point temperature ii, and the other is adjusted to the target temperature tii, and the other is adjusted based on the detection information of the device dew point temperature tp. Instead of adjusting the temperature to be the target device dew point temperature tpm, the device dew point temperature tp can be calculated based on the deviation Δti between the detection range internal temperature ti and the target range internal temperature tii and the detection information of the device dew point temperature tp. The cooling device output H and the air supply amount Q that give a state in which the in-zone temperature ti is maintained at the target temperature tii while the target device dew point temperature tpm is calculated, and the cooling device output H and the air supply amount Q are calculated values thereof. It is also possible to adopt the form of adjusting to.

The target device dew point temperature tpm to be adopted for the in-zone humidity r may be determined according to the design conditions and the like, and the temperature of the contact point at the tangent line drawn from the in-zone state point to the saturation line L may be used. The configuration is not limited to the target device dew point temperature tpm.

The present invention can be applied not only to dehumidification based on cooling, but also to dehumidification for the purpose of drying or the like.

It should be noted that reference numerals are added to the claims for convenience of comparison with the drawings, but the present invention is not limited to the structures of the accompanying drawings by the entry.

[Brief description of drawings]

FIG. 1 Device configuration diagram

[Fig. 2] Control flowchart

FIG. 3 is a psychrometric chart showing state changes

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

FIG. 5 is a psychrometric chart for explaining the operation.

FIG. 6 is a psychrometric chart showing state changes in a conventional example.

FIG. 7 is a psychrometric chart showing a state change in another conventional example.

[Explanation of symbols]

 2 Air-conditioning target area 3, 5, 13 Circulation means 4 Cooling means 19 Control means 19a Calculation means H Cooling means output L Saturation line Q Supply air amount r Area humidity RA Return air SA Supply air ti Area temperature ti Target temperature tp Equipment dew point temperature tpm Target device dew point temperature

Claims (2)

[Claims] 1. A return air (RA) from an air-conditioning target area (2) is cooled by a cooling means (4), and the cooling air is supplied (S).
Circulation means (3), (5), (13) for supplying to the air-conditioning target area (2) as A) and the temperature in the area (ti)
An air conditioner having a control means (19) for adjusting the output (H) and the supply air amount (Q) of the cooling means (4) based on the temperature detection so that the temperature becomes a target temperature (tii), The control means (19) lowers the target device dew point temperature (tpm) as the humidity (r) in the detection range decreases, and the target device dew point temperature (tpm) according to the humidity (r) in the detection range.
And a device dew point temperature (t
The output (H) and the air supply amount (Q) of the cooling means (4) are adjusted so that the temperature (ti) in the detection area becomes the target temperature (tii) in the state where p) becomes the target device dew point temperature (tpm). And an adjusting device for adjusting the air conditioner. 2. The calculation means (19a) gives the temperature of the contact point at the tangent line drawn from the in-zone state point to the saturation line (L) in the air diagram as the target device dew point temperature (tpm). The air conditioner according to Item 1.