JPH0642793A - Heating and dehumidifying air conditioning apparatus - Google Patents

Abstract

PURPOSE:To prevent the condensation of moisture in air in an area of window glass by controlling operation of a dehumidifying means with reasonable control form. CONSTITUTION:The setting of an objective humidity condition (rb') is changed automatically to low humidity side when a detecting outside air temperature (to) of an outside air temperature detecting means 19 is reduced so that the setting condition that the absolute humidity in an area in the objective humidity condition (rb') becomes lower than the absolute humidity of saturated air at the detecting outside temperature (to). In this case, the objective humidity condition (rb') in the objective area P is controlled by the control of operation of a dehumidifying means 6c through a dehumidifying control means 15 under a setting condition that the absolute humidity in the area under the objective humidity condition (rb') becomes lower than the absolute humidity of saturated air at the outside air temperature (to). According to this method, the dew point temperature of air in the area P is kept lower than the outside temperature (to) even when the temperature of a window glass is reduced to a temperature equal to the outside temperature (to) whereby the condensation of moisture in air in the area P on the window glass can be prevented surely and comfortability in the area can be improved.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION The present invention relates to a heating means for heating a target area, a dehumidifying means for dehumidifying the target area, and an air condition detection of the target area. The present invention relates to a heating / dehumidifying air conditioner provided with a dehumidifying control means for adjusting the output of the dehumidifying means so as to bring the humidity state of 1 to the target humidity state.

[0002]

2. Description of the Related Art Conventionally, in the heating and dehumidifying air conditioner as described above, the target humidity condition (generally, the target relative humidity) is artificially set, so that the moisture intrusion into the region or the moisture generation in the region occurs. With respect to the dehumidifying load of No. 3, the target area was merely adjusted and maintained at the artificially set target humidity state by adjusting the output of the dehumidifying unit by the above dehumidifying control unit.

[0003]

However, in order to prevent the window glass, which is exposed to the outside air at a temperature lower than that in the heated area, from clouding and the condensed water drop dripping in the window, mainly in winter. If the target humidity condition (target relative humidity) is set to a considerably low humidity side in consideration of safety, the dehumidifying means will be continuously operated with a high output at all times, resulting in high operating costs, and the area is always dry. Therefore, there is a problem that the comfort in the area is greatly impaired.

An object of the present invention is to solve the above problems by controlling the operation of the dehumidifying means in a rational control mode, and to surely prevent the dew condensation phenomenon of moisture in the air in the region such as fog on the window glass or drizzling. While preventing it, it is to reduce operating costs and improve comfort in the area.

[0005]

A first characteristic configuration of a heating and dehumidifying air conditioner according to the present invention is heating means for heating a target area,
Based on the dehumidifying means for dehumidifying the target area, and the air condition detection of the target area, the output of the dehumidifying means is adjusted so that the humidity state of the target area becomes the target humidity state in the heating state by the heating means. In the configuration provided with the dehumidification control means, the outside air temperature detection means for detecting the outside air temperature, and the setting such that the absolute humidity in the region in the target humidity state is equal to or less than the absolute humidity of the saturated air at the detected outside air temperature based on the detected outside air temperature. In order to maintain the state, there is provided the setting change means for automatically changing the target humidity state to the low humidity side as the detected outside air temperature decreases, and the action and effect are as follows.

[0006]

That is, when the internal humidity is adjusted to the target humidity state by the operation control of the dehumidifying means by the dehumidifying control means in a setting state in which the absolute humidity in the area in the target humidity state is equal to or less than the absolute humidity of saturated air at the outside air temperature, Even if the temperature of the window glass drops to a temperature equal to the outside air temperature, the absolute humidity of the inside air is equal to or lower than the absolute humidity of the saturated air at the outside air temperature, that is, the dew point temperature of the inside air is equal to or lower than the outside air temperature. Condensation of moisture in the air on the window glass is reliably prevented.

With respect to the change in the outside air temperature, the target humidity condition is automatically changed to the low humidity side as the outside air temperature lowers, so that the dehumidification is performed even though the outside air temperature is relatively high and dew condensation hardly occurs. Unnecessarily high output operation of the means to adjust the area to a low humidity condition (dry condition) lower than necessary
On the contrary, it is possible to prevent the setting of the target humidity state on the high humidity side, which is insufficient for the purpose of preventing dew condensation, even if the outside air temperature is considerably low and dew condensation is likely to occur.

[0008]

Therefore, according to the first characteristic configuration of the present invention, the dew condensation phenomenon of the moisture in the air in the region such as fogging and drop in the window glass can be surely prevented, and a certain target artificially set in the region can be set. Compared with the conventional air conditioner that only adjusts to the humidity condition, unnecessary high output operation of the dehumidifying means can be effectively avoided, operating cost can be saved, and it is possible to avoid keeping the area dry more than necessary. You can improve the comfort in the area.

[Second Characteristic Configuration of the Present Invention] In a second characteristic configuration of the heating and dehumidifying air conditioner according to the present invention, the dehumidifying means is a dehumidifying means for the perimeter zone, with the perimeter zone as the target area. The heat source means for supplying the dehumidifying heat source to the dehumidifying means and the interior zone dehumidifying means is provided, and the supply of the dehumidifying heat source to the perimeter zone dehumidifying means in the heating state is performed by the dehumidifying heat source to the interior zone dehumidifying means. This is because the distribution control means having priority over the supply is provided.

That is, the dew condensation phenomenon such as fogging and drop of water on the window glass in the heated state is naturally more likely to occur in the perimeter zone in contact with the outdoors than in the interior zone.

Therefore, if the above-mentioned second characteristic structure is adopted, even in a situation where the capacity of the common heat source means for distributing and supplying the heat source for dehumidification to the dehumidifying means for the perimeter zone and the dehumidifying means for the interior zone is limited. In addition, while selecting a small capacity as the heat source means, the dehumidifying effect on the perimeter zone can be enhanced by preferentially supplying the dehumidifying heat source to the dehumidifying means for the perimeter zone in response to a considerable decrease in outside air temperature. , It is possible to reliably prevent the occurrence of dew condensation in the perimeter zone.

[0012]

【Example】

 [First Embodiment] Next, a first embodiment will be described.

FIG. 1 shows air conditioning equipment for an interior zone I and a perimeter zone P in an intelligent building or the like, where 1a is a first air conditioning unit for the interior zone, 1b is a second air conditioning unit for the perimeter zone,
1c is a heat source unit common to both air conditioning units 1a and 1b.

Reference numeral 2 is a return air duct that joins the return air R from both zones I and P and returns it to each of the first and second air conditioning units 1a and 1b. The first air conditioning unit 1a includes the return air duct 2 The mixed air of the return air R from the outside air and the introduced outside air O from the outside air duct 3 is adjusted in temperature and humidity by the upstream side heat exchanger 4c, the downstream side heat exchanger 4h, and the humidifier 4m, and this adjusted air is Air supply duct 5 to interior zone I by air supply fan Fa as air supply Sa to interior zone I
Send to a.

Similarly, in the second air conditioning unit 1b, the return air R from the return air duct 2 is installed in the upstream heat exchanger 6c,
The temperature and humidity are adjusted by the downstream heat exchanger 6h and the humidifier 6m, and this adjusted air is sent to the air supply duct 5b to the perimeter zone P as the air supply Sb for the perimeter zone P by the air supply fan Fb.

In each of the zones I and P, 7a and 7a
Reference numeral b is a variable air volume device that adjusts the zone temperatures tra and trb, and deviations Δtra and Δtrb between the detected zone temperatures tra and trb by the zone temperature sensors 8a and 8b and the target zone temperatures tra ′ and trb ′ by the setters 9a and 9b. In accordance with the above, the controllers 10a and 10b adjust the supply air amounts qa and qb to the zones I and P by adjusting the opening degrees of the dampers 11a and 11b, respectively, and the zone temperatures tra and trb of the zones I and P are adjusted.
Is adjusted and maintained at the target zone temperatures tra 'and trb'.

Reference numerals 12a and 12b denote air flow rate changing devices 7a and 7a.
Each air supply duct 5 detected by the airway pressure sensors 13a, 13b in response to the adjustment of the air supply air amounts qa, qb by 7b.
Based on the internal static pressures pa, pb of a, 5b, the respective internal static pressures pa, pb of the air supply ducts 5a, 5b are adjusted and maintained at the respective target static pressures pa ', pb'. It is a fan controller that adjusts the output of Fa and Fb.

The heat source unit 1c includes a heat source heat exchanger 1
4. Outside air O to be absorbed and radiated with respect to the heat exchanger 14 for heat source
Equipped with a fan Fc that ventilates, a compressor C, and a valve mechanism V, this heat source unit 1c and each air conditioning unit 1a, 1
By connecting b through the refrigerant pipe u, an air heat source heat pump in which the refrigerant is circulated by the compressor C over the heat exchangers 4c, 4h, 6c, 6h, 14 is configured.

In this heat pump, the following refrigerant circulation patterns (a) to (f) can be selected by switching each valve in the valve mechanism V.

(B) Heating / Heating pattern As shown in FIG. 2, the high pressure refrigerant gas discharged from the compressor C (indicated by a thick black line in the figure) is divided into two streams to make the first switching valve. The downstream heat exchanger 4h in the first air conditioning unit 1a and the downstream heat exchanger 6h in the second air conditioning unit 1b are distributed and supplied via v1 and the third switching valve v3, and these downstream heat exchangers 4h, 6h are provided. To function as an air heating condenser.

Condensed refrigerant liquid delivered from each of the downstream side heat exchangers 4h and 6h (indicated by hatched thick lines in the figure).
Are combined by way of a first expansion valve ex1 and a third expansion valve ex3 which respectively function as simple flow rate adjusting valves, and the combined refrigerant liquid is passed through a fifth expansion valve ex5 and the heat source heat exchanger 14
The heat source heat exchanger 14 functions as an evaporator to cause the outside air O to absorb heat.

Then, the low-pressure refrigerant gas (shown by the white thick line in the figure) sent from the heat source heat exchanger 14 is sucked into the compressor C via the sixth switching valve v6 and the accumulator Ac.

That is, in each of the air conditioning units 1a and 1b, the warm air Sa heated by the downstream heat exchangers 4h and 6h,
By supplying Sb to each zone I, P, each zone I,
Heat P.

(B) Heating dehumidification pattern As shown in FIG. 3, the high pressure refrigerant gas (thick black line) discharged from the compressor C is divided into two streams as in the heating / heating mode of (a) above. The first switching valve v1 and the third switching valve v
3 to the downstream side heat exchanger 4h in the first air conditioning unit 1a and the downstream side heat exchanger 6h in the second air conditioning unit 1b, and these downstream side heat exchangers 4h, 6h are supplied.
To function as an air heating condenser.

The condensed refrigerant liquids (thick lines with hatching) sent from the respective downstream side heat exchangers 4h, 6h are first expansion valves ex1, which function as simple flow rate adjusting valves, respectively.
The combined refrigerant liquid is split into two streams, one of which is supplied to the heat source heat exchanger 14 through the fifth expansion valve ex5, and the other of which is the fourth expansion valve ex3. ex4
To the upstream heat exchanger 6c in the second air conditioning unit 1b, whereby the heat source heat exchanger 14 functions as an evaporator to absorb heat from the outside air O, and the second air conditioning unit 1b to the perimeter zone P is supplied. The upstream side heat exchanger 6c is used as an evaporator to perform an air cooling function.

Then, the heat exchanger 14 for the heat source and the second
The low-pressure refrigerant gas (white thick line) sent from the upstream heat exchanger 6c of the air conditioning unit 1b is caused to join via the sixth switching valve v6 and the fourth switching valve v4, and the combined refrigerant gas is passed through the accumulator Ac. Let the compressor C inhale.

That is, the interior zone I is heated by supplying the warm air Sa heated by the downstream heat exchanger 4h of the first air conditioning unit 1a.
For the perimeter zone P, the second air conditioning unit 1b
In the above, the air-cooled dehumidification in the upstream heat exchanger 6c and the subsequent reheating in the downstream heat exchanger 6h cause dehumidified hot air Sb.
Is generated and the dehumidified hot air Sb is supplied to dehumidify the perimeter zone P along with heating.
In the perimeter zone P, the phenomenon of dew condensation of moisture in the air in the zone, such as fogging of the window glass w facing the outdoors and drop of condensed water, is prevented.

In the refrigerant circulation pattern, the interior zone I and the perimeter zone P are communicated with each other and the return air R from the zones I and P in the return air duct 2 merges into the interior zone I. It also gives some dehumidifying effect at the same time.

(C) Cooling / Heating Pattern As shown in FIG. 4, the high-pressure refrigerant gas (black thick line) discharged from the compressor C is passed through the third switching valve v3 to the downstream heat of the second air conditioning unit 1b. The heat is supplied to the exchanger 6h to cause the downstream heat exchanger 6h of the second air conditioning unit 1b to function as an air heater as a condenser.

The heat exchanger 6 on the downstream side of the second air conditioning unit 1b
The condensed refrigerant liquid (thick line with hatching) sent from h is a third expansion valve e that functions as a mere flow rate adjusting valve.
x3 and split into two streams, one is supplied to the heat source heat exchanger 14 through the fifth expansion valve ex5, and the other is upstream heat exchange in the first air conditioning unit 1a through the second expansion valve ex2. The heat source heat exchanger 14
Is used as an evaporator to absorb heat from the outside air O, and
The upstream heat exchanger 4c of the first air conditioning unit 1a for the interior zone I functions as an evaporator to perform an air cooling function.

Then, the heat exchanger 14 for the heat source and the first
The low-pressure refrigerant gas (white thick line) sent from the upstream heat exchanger 4c of the air conditioning unit 1a is merged through the sixth switching valve v6 and the second switching valve v2, and the combined refrigerant gas is passed through the accumulator Ac. Let the compressor C inhale.

That is, the interior zone I is cooled, and the perimeter zone P is heated.

(D) Heating / cooling pattern As shown in FIG. 5, the high-pressure refrigerant gas (black thick line) discharged from the compressor C is passed through the first switching valve v1 to the downstream heat of the first air conditioning unit 1a. The heat is supplied to the exchanger 4h to cause the downstream heat exchanger 4h of the first air conditioning unit 1a to function as an air heater as a condenser.

Downstream heat exchanger 4 of the first air conditioning unit 1a
The condensed refrigerant liquid (thick line with hatching) delivered from h is a first expansion valve e that functions as a mere flow rate adjusting valve.
x1 to split into two streams, one is supplied to the heat source heat exchanger 14 via the fifth expansion valve ex5, and the other is upstream heat exchange in the second air conditioning unit 1b via the fourth expansion valve ex4. The heat exchanger 14 for the heat source.
Is used as an evaporator to absorb heat from the outside air O, and
The upstream heat exchanger 6c of the second air conditioning unit 1b with respect to the perimeter zone P is made to function as an evaporator with an air cooling function.

Then, the heat exchanger 14 for the heat source and the second
The low-pressure refrigerant gas (white thick line) sent from the upstream heat exchanger 6c of the air conditioning unit 1b is caused to join via the sixth switching valve v6 and the fourth switching valve v4, and the combined refrigerant gas is passed through the accumulator Ac. Let the compressor C inhale.

That is, contrary to the cooling / heating pattern of (c), the interior zone I is heated and the perimeter zone P is cooled.

(E) Cooling / cooling pattern As shown in FIG. 6, the high-pressure refrigerant gas (black thick line) discharged from the compressor C is supplied to the heat source heat exchanger 14 through the fifth switching valve v5. , The heat source heat exchanger 14 is used as a condenser to radiate heat to the outside air O.

The condensed refrigerant liquid (thick line with hatching) sent from the heat source heat exchanger 14 is split into two streams via the fifth expansion valve ex5 which functions as a simple flow rate adjusting valve,
One is supplied to the upstream heat exchanger 4c of the first air conditioning unit 1a via the second expansion valve ex2, and the other is supplied to the fourth expansion valve e.
x4 through the upstream side heat exchanger 6c of the second air conditioning unit 1b
To the upstream heat exchangers 4c, 6
The air cooling function of c is used as an evaporator.

Then, the low-pressure refrigerant gas delivered from each of the upstream heat exchangers 4c and 6c is merged through the second switching valve v2 and the fourth switching valve v4, and the combined refrigerant liquid is compressed through the accumulator Ac. Let C inhale.

That is, in each of the air conditioning units 1a and 1b, the cold air Sa cooled by the upstream heat exchangers 4c and 6c,
By supplying Sb to each zone I, P, each zone I,
Cool P.

(V) Cooling / dehumidifying pattern As shown in FIG. 7, the high-pressure refrigerant gas (black thick line) discharged from the compressor C is divided into three streams, and the first switching valve v
1, the third switching valve v3, the fifth switching valve v5, the downstream heat exchanger 4h of the first air conditioning unit 1a, the second air conditioning unit 1
It is distributed and supplied to the downstream side heat exchanger 6h of b, and the heat source heat exchanger 14, thereby making the downstream side heat exchangers 4h and 6h of each air conditioning unit 1a, 1b function as an air heating condenser. The heat exchanger 14 for heat source is made to radiate heat to the outside air O.

The condensed refrigerant liquids (thick hatched lines) sent from the downstream side heat exchangers 4h and 6h and the heat source heat exchanger 14 respectively function as first flow rate adjusting valves ex1. , The third expansion valve ex3 and the fifth expansion valve ex5 are combined, and the combined refrigerant liquid is divided into two streams, one of which is through the second expansion valve ex2 and the upstream heat exchanger of the first air conditioning unit 1a. 4c, and the other is supplied to the upstream heat exchanger 6c of the second air conditioning unit 1b via the fourth expansion valve ex4, whereby the upstream heat exchanger 4c of each of the air conditioning units 1a, 1b is supplied. , 6c function as an evaporator for air cooling.

Then, the low-pressure refrigerant gas (white thick line) sent from the upstream heat exchangers 4c, 6c of each air conditioning unit 1a, 1b is merged via the second switching valve v2 and the fourth switching valve v4. , The combined refrigerant gas to accumulator Ac
To be sucked into the compressor C via.

That is, in each of the air conditioning units 1a and 1b, dehumidifying cold air Sa and Sb is generated by the air cooling and dehumidifying in the upstream heat exchangers 4c and 6c and the subsequent reheating in the downstream heat exchangers 4h and 6h. To generate these dehumidified cold air S
By supplying a and Sb to each of the zones I and P, the interior zone I and the perimeter zone P are dehumidified by cooling.

As for heating in patterns other than the heating and dehumidifying pattern described in (b) above, the humidifier 4 may be used as necessary.
Drive m, 6m.

Reference numeral 15 denotes a controller for controlling the operation of the heat pump. This controller 15 is one of the refrigerant circulation patterns (a) to (f) according to a specified operation mode.
One or a plurality of them are sequentially selected and used to display the desired air-conditioning state. Next, regarding the operation control mode when [heating dehumidification mode] is specified among various operation modes I will explain in detail.

When the [heating / dehumidifying mode] is specified in the operation mode specification, the controller 15 controls the operation mode as shown in FIG.
First, the (heating start-up operation) in the heating / heating pattern (FIG. 2) described above (a) is performed under the adjustment of the supply air volume by the air flow rate changing devices 7a and 7b, and the zone temperature is set in this (heating start-up operation). When the zone temperatures tra and trb of the respective zones I and P detected by the sensors 8a and 8b rise to the target zone temperatures tra 'and trb', respectively, the (heating start-up operation) shifts to the (heating temperature control operation). .

In the (heating temperature control operation), the heating / heating pattern of (a) (FIG. 2) is continuously adopted, and the air supply air temperature sensors 16a, 16b are adjusted under the air supply air volume adjustment by the air flow rate changing devices 7a, 7b. The supply air temperatures tsa and tsb for the respective zones I and P detected by
After adjusting to sb ′, stabilization of each zone temperature tra, trb is waited for a predetermined time Ta (for example, 10 minutes), and thereafter, (dehumidification temperature control operation) is started.

Incidentally, this is one of the other operation modes [heating /
In the case where the "heating mode" is specified, the above-described (heating temperature control operation) is continued until the end of the operation after similarly performing (heating start-up operation).

In the (dehumidifying / temperature controlling operation), the heating / dehumidifying pattern (FIG. 3) described above (b) is adopted, and the air flow rate changing devices 7a, 7b are used.
The supply air temperature tsa, tsb for each zone I, P is adjusted to their respective set values tsa ', tsb' under the supply air volume adjustment by
The dehumidification of the perimeter zone P is started while adjusting and maintaining the above, and the relative humidity rb of the perimeter zone P is reduced to the target relative humidity rb ′.

When the relative humidity rb detected by the humidity sensor 17b of the perimeter zone P in the (dehumidifying and temperature controlling operation) decreases to the target relative humidity rb ', the (dehumidifying and temperature controlling operation) to the (temperature and humidity controlling operation). ).

In the (temperature control / humidity control operation), the heating / dehumidification pattern (FIG. 3) is adopted in the same manner as in the (dehumidification / temperature control operation), and each zone is adjusted while the supply air volume is adjusted by the air flow rate changing devices 7a and 7b. The relative humidity rb of the perimeter zone P is adjusted by adjusting the dehumidification output to the perimeter zone P while adjusting / maintaining the supply air temperatures tsa and tsb for I and P to the respective set values tsa ′ and tsb ′. Keep it
This (temperature control / humidity control) is continued until the operation end command is given.

Each operation in the above basic control flow will be further described. Regarding (heating start-up operation), in the heating / heating pattern (FIG. 2) under the supply air volume adjustment by the air flow rate changing devices 7a and 7b, As shown in FIG. 9, the following cycles # 1, # 2, and # 3 are repeated.

(# 1) Based on the detection information from the pressure / temperature sensor at the inlet of the compressor C, the superheat degree sh of the compressor suction refrigerant is adjusted to a set value sh '(for example, 8 ° C.) by adjusting the fifth expansion valve ex5. adjust.

(# 2) The downstream heat exchanger 4h in the first air conditioning unit 1a is adjusted by adjusting the compressor output fc based on the information detected by the air temperature sensor 16a on the interior zone side.
Of the interior zone I by adjusting the heating output ha of the interior zone I.
Adjust to a '.

(# 3) The first expansion valve ex as a flow rate adjusting valve based on the detection information of both the air supply temperature sensors 16a and 16b on the interior zone side and the perimeter zone side.
By adjusting the opening degrees of 1 and the third expansion valve ex3 in a contradictory manner, the heating outputs ha and hb of the downstream heat exchangers 4h and 6h in the first and second air conditioning units 1a and 1b are adjusted, The air supply temperature tsb for the perimeter zone P is made to match the air supply temperature tsa on the interior zone side detected by the air supply temperature sensor 16a on the interior zone side.

It should be noted that in the antithetic adjustment, the sum of the refrigerant flow rate of the first expansion valve ex1 and the refrigerant flow rate of the third expansion valve ex3 (that is, the refrigerant flow rate of the fifth expansion valve ex5) is not changed. , The first expansion valve e for changing and adjusting the flow rate ratio
While maintaining the total opening (α1 + α3) of the opening α1 of x1 and the opening α3 of the third expansion valve ex3 at a predetermined constant value, the opening ratio (in other words, the third expansion at the constant total opening) An adjustment mode in which the opening ratio α3 / (α1 + α3) of the valve ex3 is changed is adopted.

Regarding (heating / heating control operation) subsequent to (heating start-up operation), FIG. 10 shows the heating / heating pattern (FIG. 2) under the adjustment of the supply air volume by the air flow rate changing devices 7a and 7b. As shown, the following cycles # 4 and # 5 are repeated.

(# 4) Similar to (# 2) above, the first air conditioning unit 1a is adjusted by adjusting the compressor output fc based on the detection information of the air temperature sensor 16a on the interior zone side.
The heating output ha of the downstream side heat exchanger 4h is adjusted to adjust the supply air temperature tsa for the interior zone I to the set value tsa ′.

(# 5) In the above (# 3), adjustment is performed so that the supply air temperature tsb for the perimeter zone P matches the supply air temperature tsa on the interior zone side detected by the supply air temperature sensor 16a on the interior zone side. However,
In (# 5), the perimeter is adjusted in a reciprocal manner by adjusting the opening degree of each of the first expansion valve ex1 and the third expansion valve ex3 as flow rate adjusting valves in the same adjustment form as the valve adjustment form in (# 3). Supply air temperature tsb for zone P
To the set value tsb ′ on the perimeter zone side.

In some cases, the set value tsa 'on the interior zone side and the set value tsb' on the perimeter zone side are the same for each of the supply air temperatures tsa and tsb.

Regarding (dehumidifying and temperature controlling operation), as shown in FIG. 11, in the heating dehumidifying pattern (FIG. 3) under the adjustment of the supply air volume by the air flow rate changing devices 7a and 7b, the following # 6 to # are performed.
Repeat 10 cycles.

(# 6) The compressor output fc is increased by a predetermined value Δfc.

(# 7) Based on the information detected by the pressure / temperature sensor at the inlet of the compressor C, the opening α4 of the fourth expansion valve ex4 is adjusted without changing the opening α5 of the fifth expansion valve ex5. By adjusting the total opening (α4 + α5) of the fifth expansion valve ex5 and the fourth expansion valve ex4, the superheat degree sh of the compressor suction refrigerant is adjusted to the set value sh ′.

(# 8) By opening the first expansion valve ex1 and the third expansion valve ex3, which are flow rate adjusting valves, on the basis of the information detected by the air temperature sensor 16a on the interior zone side, the opening degrees are adjusted in a contradictory manner. The heating output ha of the downstream heat exchanger 4h in the first air conditioning unit 1a is adjusted to set the supply air temperature tsa for the interior zone I to the set value ts.
Adjust to a '.

Incidentally, in this antithetic opening adjustment, the above (#
Similar to 3), the sum of the refrigerant flow rate of the first expansion valve ex1 and the refrigerant flow rate of the third expansion valve ex3 (that is, the fourth expansion valve ex4
And the fifth expansion valve ex5), the first expansion valve ex5 is used in order to change and adjust the flow ratio without changing the total refrigerant flow rate.
While maintaining the total opening degree (α1 + α3) of the opening degree α1 of 1 and the opening degree α3 of the third expansion valve ex3 at a predetermined constant value, the opening ratio (in other words, the first expansion at the constant total opening degree). An adjustment mode in which the opening ratio α1 / (α1 + α3) of the valve ex1 is changed is adopted.

(# 9) The total opening (α4 + α5) of the fifth expansion valve ex5 and the fourth expansion valve ex4 is set to (#
In the state where the total opening in 7) is maintained, the fourth expansion valve ex and the fifth expansion valve ex
Opening ratio with the expansion valve ex5 (in other words, the opening ratio α4 / (α4 + α of the fourth expansion valve ex4 at a constant total opening)
5)) by adjusting the cooling output cb of the upstream heat exchanger 6c in the second air conditioning unit 1b,
The supply air temperature tsb for the perimeter zone P is set to the set value t
Adjust to sb '.

(# 10) Based on the coil surface temperature detection of the upstream heat exchanger 6c in the second air conditioning unit 1b, the detected coil surface temperature tpb (that is, the device dew point temperature) is taken into consideration in dehumidification efficiency. The determined setting value tp
It is determined whether or not the compressor output fc has reached the maximum output fcmax, and the determination coil surface temperature tp is obtained as the determination result.
When b is less than or equal to the set value tpb 'or the compressor output fc reaches the maximum output fcmax, the process proceeds to the determination of the completion of humidity decrease in (# 11) and (# 12) (FIG. 8). , The detection coil surface temperature tp
When b is higher than the set value tpb 'and the compressor output fc is still less than the maximum output fcmax, the process returns to (# 6).

After lowering the relative humidity rb of the perimeter zone P to the target relative humidity rb '(temperature control / humidity control operation)
As for the above, as shown in FIG. 12, the following cycles # 13 to # 16 are repeated in the heating / dehumidifying pattern (FIG. 3) under the adjustment of the supply air volume by the air flow rate changing devices 7a and 7b.

(# 13) Pressure at the inlet of compressor C
Based on the detection information of the temperature sensor, the opening degree α4 of the fourth expansion valve ex4 and the opening degree α5 of the fifth expansion valve ex5 are increased / decreased while maintaining their opening ratios, and the compressor suction refrigerant The superheat degree sh of is adjusted to the set value sh '.

(# 14) Similar to (# 8) above, based on the detection information of the air temperature sensor 16a on the interior zone side, the sum of the first expansion valve ex1 and the third expansion valve ex3 as flow rate adjusting valves, respectively. While maintaining the opening (α1 + α3) at a predetermined constant value, the first and third expansion valves ex1, e
The opening ratio of x3 (in other words, the first opening at a fixed total opening)
By adjusting the opening ratio α1 / (α1 + α3)) of the expansion valve ex1, the heating output ha of the downstream heat exchanger 4h in the first air conditioning unit 1a is adjusted to set the supply temperature tsa for the interior zone I. Adjust to the value tsa '.

(# 15) Similar to (# 9) above, the total opening (α4 + α5) of the fifth expansion valve ex5 and the fourth expansion valve ex4 is set based on the information detected by the air temperature sensor 16b on the perimeter zone side. The opening ratio of the fourth expansion valve ex and the fifth expansion valve ex5 (in other words, the fourth expansion valve ex4 at a constant total opening is maintained at the total opening of (# 13)).
By adjusting the opening degree ratio α4 / (α4 + α5)) to adjust the cooling output cb of the upstream heat exchanger 6c in the second air conditioning unit 1b, the supply air temperature tsb to the perimeter zone P is set to a set value tsb '. Adjust to.

(# 16) Based on the relative humidity detected by the humidity sensor 17b in the perimeter zone P, the detected relative humidity r
b and the target relative humidity rb 'by increasing or decreasing the compressor output fc according to the deviation Δrb between the perimeter zone P and the target relative humidity rb'.
The relative humidity rb of is adjusted and maintained at the target relative humidity rb ′.

In the [heating and dehumidifying mode], the target relative humidity rb 'is intended to reduce the relative humidity rb in the perimeter zone P (dehumidifying temperature control operation), so that the relative humidity rb in the perimeter zone P is maintained. The target condition for shifting to (temperature control / humidity control) is the target relative humidity rb ', but the humidity setting change unit 18 in the controller 15 (# 11) sets the target relative humidity rb' to the outside air temperature to and the target relative humidity. A predetermined functional expression rb ′ that gives a relationship with the humidity rb ′
Based on = F (to), the target relative humidity rb 'is automatically set according to the outside air temperature to detected by the outside air temperature sensor 19.

Then, the solid line graph in FIG.
For each outside air temperature to (horizontal axis), a graph giving the relative humidity rx (vertical axis) of the air whose temperature is at the target zone temperature trb ′ of the perimeter zone P at an absolute humidity equal to the absolute humidity of the saturated air at the outside air temperature tox ( In other words, the relative humidity r (vertical axis) of the temperature trb ′ and the dew point temperature td.
p (horizontal axis) is a graph that gives the relationship with
In the above functional expression rb ′ = F (to) indicated by the broken line graph, for each outside air temperature to, the target zone temperature trb ′ of the perimeter zone P is the absolute humidity equal to the absolute humidity of the saturated air at the outside air temperature tox. Relative humidity value (r
x-Δr) as the target relative humidity rb ′ (in other words, for each outside air temperature to, the temperature t of the air whose dew point temperature is lower than the outside air temperature tox by a predetermined value Δt).
An equation which gives the relative humidity value at rb ′ as the target relative humidity rb ′ is selected.

That is, in [heating and dehumidifying mode], the target relative humidity rb 'is automatically changed according to the outside air temperature to as described above, so that the outside air temperature to is relatively high and the window glass w in the perimeter zone P is relatively high. Although the dew condensation phenomenon such as cloudy weather and drizzling of condensed water is unlikely to occur, the perimeter zone P is unnecessarily high-power dehumidified and the perimeter zone P is set to a low humidity state (dry state) lower than necessary. The target relative humidity rb ′ is not sufficiently set in order to prevent the dew condensation, even though the dew phenomenon is likely to occur in the perimeter zone P because the outside air temperature to is considerably low because the outside air temperature to is considerably low. Avoid being on a high humidity side.

Further, in contrast to the dew condensation phenomenon in the heating state occurring in the perimeter zone P in contact with the outside, in the above [heating / dehumidifying mode], the upstream side of the first air conditioning unit 1a side which is the dehumidifying means for the interior zone I. Heat exchanger 4c
To the dehumidifying means for the perimeter zone P, that is, the upstream heat exchanger 6c on the second air conditioning unit 1b side by preferentially supplying the condensed refrigerant liquid (hatched thick line) as a heat source for dehumidification to the dehumidifying means. By this, the compressor C
The dehumidifying ability of the perimeter zone P is ensured as much as possible while the dehumidifying ability of the perimeter zone P is ensured to be as large as possible while the performance of the perimeter zone P is limited.

[Second Embodiment] Next, a second embodiment will be described.

FIG. 14 shows a first air conditioning unit 1a for the interior zone I, a second air conditioning unit 1b for the perimeter zone P, and a common heat source unit 1c for the air conditioning units 1a, 1b, as in the first embodiment. However, the air-conditioning equipment of the type in which the air flow rate changing devices 7a and 7b for the respective zones I and P are omitted is shown.
In the second embodiment, the same devices as those described in the first embodiment are designated by the same reference numerals as those used in the first embodiment, and the description thereof will be omitted.

In this air conditioner, the interior zone I is heated and the perimeter zone P is heated and dehumidified [heating dehumidification mode] in the same manner as in the first embodiment according to the basic control flow shown in FIG. The basic control flow (heating start-up operation),
Each of the (heating temperature control operation), (dehumidification temperature control operation), and (temperature control / humidity control operation) is configured as follows.

Regarding (heating start-up operation),
In the heating pattern (FIG. 2), as shown in FIG. 15, the following cycles # 1 ′, # 2 ′ and # 3 ′ are repeated.

(# 1 ') Pressure at the inlet of the compressor C
Based on the information detected by the temperature sensor, the superheat degree sh of the compressor suction refrigerant is adjusted to the set value sh'by adjusting the fifth expansion valve ex5 (the same as (# 1) in the first embodiment).

(# 2 ') Compressor output fc is maximum output fc
Adjust to max.

(# 3 ') Based on the detection information of both the zone temperature sensors 8a and 8b on the interior zone side and the perimeter zone side, the first expansion valve ex as a flow rate adjusting valve, respectively.
By adjusting the opening degrees of 1 and the third expansion valve ex3 in a contradictory manner, the heating outputs ha and hb of the downstream heat exchangers 4h and 6h in the first and second air conditioning units 1a and 1b are adjusted, The zone temperature trb of the perimeter zone P is matched with the zone temperature tra of the interior zone detected by the zone temperature sensor 8a of the interior zone.

Incidentally, in the antithetic opening adjustment, the sum of the refrigerant flow rate of the first expansion valve ex1 and the refrigerant flow rate of the third expansion valve ex3 (that is, the refrigerant flow rate of the fifth expansion valve ex5) is not changed. , The first expansion valve e for changing and adjusting the flow rate ratio
While maintaining the total opening (α1 + α3) of the opening α1 of x1 and the opening α3 of the third expansion valve ex3 at a predetermined constant value, the opening ratio (in other words, the third expansion at the constant total opening) An adjustment mode in which the opening ratio α3 / (α1 + α3) of the valve ex3 is changed is adopted.

Regarding (heating / heating control operation) subsequent to (heating start-up operation), as shown in FIG. 16 in the heating / heating pattern (FIG. 2), the following # 4 ', # 5' are similarly set.
Repeat the cycle.

(# 4 ') The downstream heat exchanger 4 in the first air conditioning unit 1a is adjusted by adjusting the compressor output fc based on the information detected by the zone temperature sensor 8a on the interior zone side.
By adjusting the heating output ha of h, the zone temperature tra of the interior zone I is adjusted to the target zone temperature tra 'on the interior zone side.

(# 5 ') In the above (# 3'), adjustment is performed so that the zone temperature trb of the perimeter zone P matches the zone temperature tra of the interior zone detected by the zone temperature sensor 8a of the interior zone. However, in (# 5 ′), the opening degree of each of the first expansion valve ex1 and the third expansion valve ex3, which are flow rate adjusting valves, is adjusted in the same manner as the valve adjustment method in (# 3 ′). By setting the zone temperature t of the perimeter zone P
rb is adjusted to the target zone temperature trb ′ on the perimeter zone side.

The target zone temperatures tra 'and trb' on the interior zone side and the perimeter zone side may be the same.

Regarding the (dehumidification / temperature control operation), as shown in FIG. 17 in the heating / dehumidification pattern (FIG. 3), the following #
Repeat the cycle from 6'to # 10 '.

(# 6 ') Compressor output fc is set to a predetermined value Δfc
Only (the same as (# 6) in the first embodiment).

(# 7 ') Pressure at the inlet of the compressor C
Based on the information detected by the temperature sensor, the opening α5 of the fourth expansion valve ex4 is adjusted without changing the opening α5 of the fifth expansion valve ex5, and the sum of the fifth expansion valve ex5 and the fourth expansion valve ex4 is adjusted. By adjusting the opening degree (α4 + α5), the superheat degree sh of the compressor suction refrigerant is adjusted to the set value sh ′ (the same as (# 7) in the first embodiment).

(# 8 ') Based on the information detected by the zone temperature sensor 8a on the interior zone side, the opening degrees of the first expansion valve ex1 and the third expansion valve ex3, which are flow rate adjusting valves, are adjusted in a contradictory manner. The heating output ha of the downstream heat exchanger 4h in the first air conditioning unit 1a is adjusted to adjust the zone temperature tra of the interior zone I to the target zone temperature tra 'on the interior zone side.

Incidentally, in this antithetic opening adjustment, the above (#
3 '), the sum of the refrigerant flow rate of the first expansion valve ex1 and the refrigerant flow rate of the third expansion valve ex3 (that is, the fourth expansion valve ex3).
4 and the fifth expansion valve ex5), the first expansion valve ex5 is used to change and adjust the flow ratio without changing the total refrigerant flow rate.
While maintaining the total opening degree (α1 + α3) of the opening degree α1 of 1 and the opening degree α3 of the third expansion valve ex3 at a predetermined constant value, the opening ratio (in other words, the first expansion at the constant total opening degree). An adjustment mode in which the opening ratio α1 / (α1 + α3) of the valve ex1 is changed is adopted.

(# 9 ') The fifth expansion valve ex5 is based on the information detected by the zone temperature sensor 8b on the perimeter zone side.
And the fourth opening of the fourth expansion valve ex4 (α4 + α5) (#
7 ′), the opening ratio of the fourth expansion valve ex5 and the fifth expansion valve ex5 (in other words, the opening ratio α4 / of the fourth expansion valve ex4 at a constant total opening). (Α4 + α
5)) by adjusting the cooling output cb of the upstream heat exchanger 6c in the second air conditioning unit 1b,
The zone temperature trb of the perimeter zone P is adjusted to the target zone temperature trb ′ on the perimeter zone side.

(# 10 ') Based on the coil surface temperature detection of the upstream heat exchanger 6c in the second air conditioning unit 1b,
The detection coil surface temperature tpb (that is, equivalent to the device dew point temperature) is a set value t determined in consideration of dehumidification efficiency.
It is determined whether or not the compressor output fc has reached the maximum output fcmax, and the determination coil surface temperature tp is obtained as the determination result.
When b is equal to or less than the set value tpb 'or the compressor output fc reaches the maximum output fcmax, the humidity reduction completion in (# 11) and (# 12) in the basic control flow shown in FIG. 8 is completed. If the detection coil surface temperature tpb is higher than the set value tpb ′ and the compressor output fc is still less than the maximum output fcmax (#
6 ') (the same as (# 10) in the first embodiment).

After lowering the relative humidity rb of the perimeter zone P to the target relative humidity rb '(temperature control / humidity control operation)
18 in the heating dehumidification pattern (FIG. 3).
As shown in, the following cycles # 13 'to # 16' are repeated.

(# 13 ') Based on the detection information of the pressure / temperature sensor at the inlet of the compressor C, the opening α4 of the fourth expansion valve ex4 and the opening α5 of the fifth expansion valve ex5 are opened. The superheat degree sh of the compressor suction refrigerant is adjusted to a set value sh'by increasing or decreasing while maintaining the temperature ratio.

(# 14 ') Similar to the above (# 8'),
Based on the detection information of the zone temperature sensor 8a on the interior zone side, the first expansion valve ex1 as a flow rate adjusting valve, respectively.
While maintaining the total opening (α1 + α3) of the first and third expansion valves ex3 at a predetermined constant value.
1, ex3 opening ratio (in other words, opening ratio α1 / (α1 + α3) of the first expansion valve ex1 at a constant total opening)
Is adjusted to adjust the heating output ha of the downstream heat exchanger 4h in the first air conditioning unit 1a to adjust the zone temperature tra of the interior zone I to the target zone temperature tra 'on the interior zone side.

(# 15 ') Similar to the above (# 9'),
Based on the detection information by the zone temperature sensor 8b on the perimeter zone side, the total opening (α4 + α5) of the fifth expansion valve ex5 and the fourth expansion valve ex4 is maintained at the total opening of (# 13 ′). Opening ratio of the fourth expansion valve ex and the fifth expansion valve ex5 (in other words, the fourth expansion valve e at a constant total opening)
By adjusting the opening ratio α4 / (α4 + α5) of x4 to adjust the cooling output cb of the upstream heat exchanger 6c in the second air conditioning unit 1b, the zone temperature trb of the perimeter zone P is adjusted to the perimeter zone side. Adjust to the target zone temperature trb '.

(# 16 ') Based on the relative humidity detected by the humidity sensor 17b in the perimeter zone P, the compressor output fc is increased or decreased in accordance with the deviation Δrb between the detected relative humidity rb and the target relative humidity rb'. The relative humidity rb of the zone P is adjusted and maintained at the target relative humidity rb '.

Then, in the above [heating / dehumidifying mode], the target relative humidity rb 'is the same as in the first embodiment, in the basic control flow shown in FIG. 8 by the humidity setting changing unit 18 in the controller 15 (# 11). , A predetermined functional expression rb ′ that gives the relationship between the outside air temperature to and the target relative humidity rb ′
= F (to), the target relative humidity rb 'is automatically set according to the outside air temperature to detected by the outside air temperature sensor 19, and its functional expression rb' = F (t
Similarly to the first embodiment, the outside air temperature tox for each outside air temperature to, as shown by the solid line graph in FIG.
The relative humidity value (rx−Δr) lower than the relative humidity rx of the air whose temperature is at the target zone temperature trb ′ of the perimeter zone P by the predetermined humidity Δr at the absolute humidity equal to the absolute humidity of the saturated air at the target relative humidity. Expression given as rb ′ (that is, for each outside air temperature to, the relative humidity value at the temperature trb ′ of the air whose dew point temperature is lower than the outside air temperature tox by the predetermined value Δt, is the target relative humidity rb ′.
The formula given as is selected.

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

In each of the above-described embodiments, the target humidity state is given by the relative humidity value (target relative humidity rb '). Instead, however, the target humidity state is expressed by the absolute humidity value, the water vapor partial pressure, or the dew point. Various modes can be adopted as the mode for designating the target humidity condition, such as the temperature.

In the equipment of the dehumidifying means for the interior zone and the dehumidifying means for the perimeter zone, each of which can employ various dehumidification methods, the dehumidifying means for the dehumidifying means for the perimeter zone is supplied with the dehumidifying heat source for the dehumidifying means for the interior zone. When performing distribution control that has priority over the supply of heat, the excess heat source for dehumidification is supplied to the dehumidifying means for the perimeter zone in parallel with the heat source for dehumidification necessary for achieving the target humidity condition. Alternatively, the interior zone I may be directly dehumidified to some extent in a heated state.

Further, a structure in which the dehumidifying means for the interior zone I is omitted may be adopted.

The present invention is not limited to the air-conditioning equipment for which a plurality of zones are subject to air-conditioning as in the above-mentioned embodiment, but the present invention may be applied to the air-conditioning equipment for subjecting a single target area such as a dedicated perimeter zone to air conditioning. .

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

[0109]

[Brief description of drawings]

FIG. 1 is an overall view of an air conditioning facility according to a first embodiment.

FIG. 2 is a circuit diagram showing a refrigerant path of a heating / heating pattern.

FIG. 3 is a circuit diagram showing a refrigerant path of a heating dehumidification pattern.

FIG. 4 is a circuit diagram showing a refrigerant path of a cooling / heating pattern.

FIG. 5 is a circuit diagram showing a refrigerant path of a heating / cooling pattern.

FIG. 6 is a circuit diagram showing a cooling medium path of a cooling / cooling pattern.

FIG. 7 is a circuit diagram showing a refrigerant path of a cooling / dehumidifying pattern.

FIG. 8 is a flowchart showing a basic control flow of a heating dehumidification mode.

FIG. 9 is a flowchart of a heating start-up operation according to the first embodiment.

FIG. 10 is a flowchart of a heating temperature control operation in the first embodiment.

FIG. 11 is a flowchart of a dehumidifying temperature control operation in the first embodiment.

FIG. 12 is a flow chart of temperature control / humidity control operation in the first embodiment.

FIG. 13 is a graph showing the relationship between target relative humidity and outside air temperature.

FIG. 14 is an overall view of an air conditioning facility in the second embodiment.

FIG. 15 is a flowchart of a heating start-up operation according to the second embodiment.

FIG. 16 is a flowchart of a heating temperature control operation in the second embodiment.

FIG. 17 is a flowchart of the dehumidifying and temperature-controlling operation in the second embodiment.

FIG. 18 is a flowchart of temperature control / humidity control operation in the second embodiment.

[Explanation of symbols]

 4c Dehumidification means for interior zone 6h Heating means 6c Dehumidification means (dehumidification means for perimeter zone) 15 Dehumidification control means (distribution control means) 18 Setting change means 19 Outside air temperature detection means C Heat source means P Target area (perimeter zone) rb 'Target Humidity condition to outside temperature

Claims (2)

[Claims] 1. A heating means (6) for heating a target area (P).
h), dehumidifying means (6c) for dehumidifying the target area (P),
And the dehumidifying means for changing the humidity state of the target area (P) to the target humidity state (rb ′) in the heating state by the heating means (6h) based on the detection of the air state of the target area (P). A heating and dehumidifying air conditioner provided with a dehumidifying control means (15) for adjusting the output of (6c), the outside air temperature detecting means (19) for detecting an outside air temperature (to),
Based on this detected outside air temperature (to), the above-mentioned target humidity state (rb ′) is maintained so that the absolute humidity in the region is equal to or less than the absolute humidity of saturated air at the detected outside air temperature (to). A heating / dehumidifying air conditioner provided with setting changing means (18) for automatically changing the target humidity state (rb ') to a low humidity side as the detected outside air temperature (to) decreases. 2. A dehumidifying means (6c) for the perimeter zone, wherein the dehumidifying means (6c) is the dehumidifying means for the perimeter zone, and the dehumidifying means (6c) is for the perimeter zone.
A heat source means (C) for supplying a dehumidifying heat source to the dehumidifying means (4c) for the interior zone and the dehumidifying means (4c) for the interior zone are provided, and the heat source for dehumidification is supplied to the dehumidifying means (6c) for the perimeter zone in the heating state. The heating and dehumidifying air conditioner according to claim 1, further comprising a distribution control means (15) which has priority over the supply of the dehumidifying heat source to the dehumidifying means (4c).