JP2667318B2 - Outside air introduction type 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 an outside air introduction type air conditioner, and more particularly to a method of controlling the temperature of outside air to a set temperature by means of temperature control means, and distributing and supplying the temperature-controlled outside air to a plurality of air-conditioned rooms. In addition, the entire outside air operation in the temperature control mode in which the air supply amount of the temperature-controlled outside air to each of the air-conditioned rooms is adjusted by the variable air volume device according to the air-conditioning load of each room to be air-conditioned, and the operation of the temperature control means are stopped. The present invention also relates to an external air introduction type air conditioner that selectively performs non-temperature-controlled external air to all air-conditioned rooms in a non-temperature-controlled mode in which the air is distributed to a plurality of air-conditioned rooms.

[0002]

2. Description of the Related Art Conventionally, as an outside air introduction type air conditioner,
As shown in Japanese Patent Publication No. 62-2225, when the enthalpy of the outside air becomes smaller than the indoor enthalpy of the room to be air-conditioned, the return air from the room to be air-conditioned is re-cooled by the cooling coil and supplied to the room to be air-conditioned. In place of the circulation operation, an all-outside air operation for supplying outside air to the room to be air-conditioned as air-conditioning air is performed, and in this all-outside air operation, when the room temperature of the room to be air-conditioned becomes higher than the allowable upper limit temperature with respect to the target room temperature,
By operating the cooling coil and supplying the outside air of which the cooling temperature is controlled by the cooling coil to the room to be air-conditioned, the entire outside air operation in the temperature control mode corresponding to the cooling load is performed. When the room temperature falls below the target room temperature, the cooling load is reduced only by supplying non-temperature-regulated outside air to the room to be air-conditioned while the cooling coil is stopped until the room temperature becomes higher than the allowable upper limit temperature for the target room temperature. There has been one that performs a full outside air operation (so-called outside air cooling) in a corresponding non-temperature control mode. ... (Conventional example 1)

As disclosed in Japanese Patent Application Laid-Open No. Sho 59-21929, when the outside air temperature is higher than the design supply air temperature for the room to be air-conditioned, the return air from the room to be air-conditioned is re-cooled by a cooling coil. When the outside air temperature is lower than the design supply air temperature for the room to be air-conditioned, the circulation operation for supplying air to the room to be air-conditioned is performed. In some cases, the device operation is switched to a full outside air operation (outside air cooling) in a non-temperature control mode corresponding to a cooling load by supplying outside air to the room to be air-conditioned. ... (Conventional example 2)

[0004]

However, as in the above-mentioned prior art 1, the temperature control mode is changed from the full outside air operation to the non-temperature based on the temperature relationship between the room temperature of the room to be air-conditioned and the target room temperature of the room to be air-conditioned. The mode in which the mode is switched to the all-outdoor operation is not applicable when there are a plurality of air-conditioned rooms and the load conditions of these target rooms are different. If the mode switching from the temperature control mode full outside air operation to the non-temperature control mode full outside air operation is performed based on the temperature relationship between the room temperature of the representative room and the target room temperature, the non-temperature control mode full outside air operation is performed. Mode switching is inappropriate for other air-conditioned rooms, and there is a problem in that other air-conditioned rooms may have insufficient air-conditioning output such as insufficient cooling or insufficient heating.

[0005] Further, as in the above-mentioned conventional example 2, simply switching to the non-temperature control mode full outside air operation based on the result of comparison between the outside air temperature and the design supply air temperature for the room to be air-conditioned is as follows. For example, in the case of cooling, since the target room temperature of the room to be air-conditioned is a set value higher than the design air supply temperature, even if the outside air temperature is slightly higher than the design air supply temperature, if the cooling load of the room to be air-conditioned at that time is small. In addition, if a sufficient supply air volume can be ensured, there is actually a situation in which only the uncooled (non-temperature controlled) outside air supply can sufficiently cope with the cooling load. Since the operation is continued, there is a problem that the energy saving effect is low.

In view of the above circumstances, an object of the present invention is to adopt a rational air-conditioning system and a mode switching system in the whole outside air operation, and to reduce the temperature control mode full outside air operation when there are a plurality of air-conditioned rooms. The point is that the mode switching to the non-temperature control mode all outside air operation is appropriately performed at a timing that does not cause an air conditioning output shortage in each of the air-conditioned rooms and at a timing that can ensure a high energy saving effect. .

[0007]

The outside air introduction type air conditioner according to the present invention is characterized in that the outside air is temperature-controlled to a set temperature by a temperature control means, and the temperature-controlled outside air is distributed and supplied to a plurality of air-conditioned rooms. In the total outside air operation in the temperature control mode in which the supply amount of the temperature-controlled outside air to each of the air-conditioned rooms is adjusted by the variable air volume device according to the air-conditioning load of each of the air-conditioned rooms, When the total air supply amount of the temperature-regulated outside air with respect to the temperature decreases to the set lower limit, the apparatus operation is changed from the total outside air operation in the temperature control mode to the temperature control means based on the determination of the decrease in the total air supply amount. Is stopped and the non-temperature-controlled outside air is distributed and supplied to the air-conditioned rooms, and the air supply amount of the non-temperature-controlled outside air to each of the air-conditioned rooms is air-conditioned by the variable air volume device in each of the air-conditioned rooms. All outside in non-temperature control mode that adjusts according to load In that is provided with a mode switching control means for switching the operation.

[0008]

In the above-mentioned characteristic configuration, in the whole outside air operation in the temperature control mode, the variable air volume device supplies the temperature-controlled outside air (outside air whose temperature is adjusted to the set temperature by the temperature control means) to each of the plurality of air-conditioned rooms. By adjusting the air volume in accordance with the air conditioning load of each room to be air-conditioned, the lower the overall air conditioning load of the plurality of room to be air-conditioned, the smaller the total supply of temperature-controlled outside air to the plurality of room to be air-conditioned.

When the total supply amount of the temperature-controlled outside air decreases to the set lower limit in the decrease of the total supply amount due to the decrease of the total air-conditioning load, based on the determination of the decrease of the total supply amount, The mode switching control means switches the operation of the apparatus to the non-temperature control mode full outside air operation in which the operation of the temperature control means is stopped. In the full outside air operation in the non-temperature control mode, as in the case of the temperature control mode, a plurality of air conditioning The air supply amount of the non-temperature controlled outside air to each of the target areas is adjusted according to the air-conditioning load of each air-conditioning target room by the variable air volume device, so that each of these air-conditioning target rooms is adjusted and maintained in the respective desired air-conditioning state. It

[0010]

That is, according to the present invention, the total supply amount of the temperature-controlled outside air that accurately reflects the entire air conditioning load under the adjustment of the supply amount of the temperature-controlled outside air by the variable air volume device is used as an index. When the supply air amount decreases to the set lower limit, the device operation is switched from the temperature control mode full outside air operation to the non-temperature control mode full outside air operation based on the decrease determination. In the all-outside-air operation mode, the supply amount of non-temperature-controlled outside air to each of the plurality of air-conditioning target areas is adjusted by the variable air volume device according to the air-conditioning load of each air-conditioning target room. Insufficient air conditioning output such as insufficient cooling and insufficient heating can be reliably prevented, and in a state where each of a plurality of air-conditioned rooms is kept in a good air-conditioning state, the temperature control mode is changed from the total outside air operation to the non-temperature control mode. All outside air driving It is possible to perform de switched appropriately.

In addition, in the case of cooling, the outside air temperature is still slightly higher than the set temperature of the temperature-controlled outside air to be distributed to each room to be air-conditioned. Even if the temperature is still somewhat lower, when the total supply amount of the temperature-controlled outside air decreases to the set lower limit value (that is, when the total air-conditioning load becomes sufficiently small), the temperature control mode full outside air operation is performed. Is switched to the non-temperature-control mode all-outside air operation, so that the system is switched to the non-temperature-control mode all-outside air operation simply based on the comparison between the outside air temperature and the design air supply temperature, as in Conventional Example 2 described above. As compared with the above, wasteful operation of the temperature control means can be prevented, and a higher energy saving effect can be obtained.

[0012]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS In FIG. 1, reference numeral 1 denotes an air-conditioning target area which is a set of a plurality of air-conditioning target rooms 1a, and 2 denotes an air conditioner.

The air conditioner 2 has a heat pump H in which a supply-side heat exchanger 3, an exhaust-side heat exchanger 4, a compressor 5, and an expansion valve 6 are used as main devices and connected by a refrigerant circuit 7.
By switching the refrigerant flow direction, in the cooling operation, the supply-side heat exchanger 3 functions as an evaporator, and the exhaust-side heat exchanger 4 functions as a condenser.
Conversely, in the heating operation, the supply-side heat exchanger 3 functions as a condenser, and the exhaust-side heat exchanger 4 functions as an evaporator.

On the other hand, with respect to the air path configuration, basically,
A part of the return air RA returning from each of the target rooms 1a to the air conditioner 2 via the return air passage 8 is divided by the first damper D1 and the second damper D2 so as to be diverted to the second damper D2 side. The combined air-fuel mixture of the diverted return air RA ′ and the outside air OA introduced into the air conditioner 2 through the outside air passage 9 is used as an object for radiating condensed heat in cooling, and as an object for absorbing vaporized heat in heating, and is used as an exhaust heat. After passing through the exchanger 4, the air is discarded outside the system by the exhaust fan 11 through the exhaust air passage 10, and in parallel with this, the outside air OA is taken in upstream of the junction of the return air RA ′.
Is partially adjusted by the third damper D3 and the fourth damper D4 to divide the flow toward the fourth damper D4 (the divided air RA ′).
And the diverted outside air OA '
Is joined to the return air RA downstream of the branch point of the branch air return air RA ′, and the combined air-fuel mixture of the branch air OA ′ and the return air RA is temperature-controlled by the air supply side heat exchanger 3. The supply air is distributed and supplied to each target room 1a by the air supply fan 13 through the air supply air passage 12 as the air supply SA.

That is, a part of the return air RA is discarded outside the system, and a part of the outside air OA is mixed in the supply air SA to each target room 1a, thereby cooling or heating each target room 1a. They are ventilated in parallel.

Further, in the above-described air path configuration, by operating the first to fourth dampers D1 to D4, the entire amount of the return air RA is exhausted through the exhaust air path 10, and the entire amount of the supply air SA is reduced to the outside air O.
A ′, that is, so-called all-outside air operation can be performed.

A branch supply air passage 12a for each target chamber 1a
Are the room temperature ti detected by the room temperature sensor 14.
And the target room temperature tii set by the setting device 15 (for example, tii = 27 ° C. for cooling and tii = 25 for heating)
° C) and the room temperature ti is calculated based on the deviation dti from the target room temperature ti.
A variable air flow device 16 is provided to adjust the air supply amount q to the target room 1a so that the target room temperature tii is higher in the detected room temperature ti than the target room temperature tii (ti). > Tii), the larger the deviation dti is, the larger the air supply amount q to the target chamber 1a is, and the more the deviation dti is.
Is smaller, the air supply amount q to the target room 1a is reduced to adjust the room temperature ti to the target room temperature tii, and conversely, the detected room temperature ti is lower in temperature than the target room temperature tii (ti <tii). ), The larger the deviation dti is, the larger the air supply amount q to the target chamber 1a is, and the more the deviation dti is.
As the air conditioner 2 is smaller, the air supply amount q to the target room 1a is decreased, and the room temperature ti is adjusted to the target room temperature tii.

Reference numeral 17 denotes a controller of the air conditioner 2. The controller 17 controls the operation of the air conditioner 2 in the cooling operation according to the control flow shown in FIG.

(A) First, the hr / vr value (k
cal / m ³ ) and the ho / vo value of the outside air OA (kc
al / m ³ ) are calculated from the temperature tr and humidity rr of the return air RA detected by the return air state detector 18 and the temperature to and humidity ro of the outside air OA detected by the outside air state detector 19, respectively. It is calculated based on the following approximate expression.

H / v = (K ₀ · t ² + K ₁ · t + K ₂ ) K ₀ = (0.006r ² + 0.423r + 19.028) / 10 ⁴ K ₁ = (− 0.162r ² + 33.79r + 2308.05) ) / 10 ⁴ K ₂ = (0.976 r ² + 203.338r + 345.44) / 10 ⁴ where h; specific enthalpy (hr, ho) (kcal / kg (DA)) v; specific volume (vr, vo) ( m ³ / kg (DA)) t; dry-bulb temperature (tr, to) (° C.) r; relative humidity (rr, ro) (%) The subscript r indicates return air, and the subscript o indicates outside air.

Then, in # 1, the first determination unit 17a
Is calculated as hr / vr value of return air RA and ho of outside air OA.
/ Hr value, and when hr / vr ≦ ho / vo, the mixture of return air RA and branch air OA ′ is supplied to the air supply SA.
"Circulation operation" is selected, and hr / vr> ho
In the case of / vo, “all outside air operation” in which the whole amount of the supply air SA is outside air OA ′ is selected.

(B) If "circulation operation" is selected in # 1, the fan control unit 17b controls the air passage static pressure ps of the air supply passage 12 detected by the air pressure sensor 20 to the set pressure pss. Adjusts the rotation speed Fn of the air supply fan 13. ...... (Fan control)

The supply air temperature ts detected by the supply air temperature sensor 21 is equal to the set temperature tss (for example, tss = 12).
° C), the temperature control controller 17c adjusts the rotation speed Cn of the compressor 5 to adjust the temperature control output (cooling output) of the air supply side heat exchanger 3. ...... (Temperature control)

Subsequently, the damper control unit 17d operates the opening degrees d2, d3, d of the second, third, and fourth dampers D2, D3, D4.
4 are respectively set to the opening degrees da2, da3, d for circulation operation.
a4 (for example, da2 = 25% opening degree, da3 = 100%
Opening, da4 = 15.4% opening)
The adjustment of the air supply amount q to the target room 1a by each of the variable air volume devices 16 and the adjustment of the fan rotation speed Fn by the corresponding fan control unit 17a make the total air supply amount Qsa to the air-conditioning target area 1 in FIG. As shown in the drawing, the fan Q is changed in accordance with the change in the total air conditioning load W (total cooling load) in the air conditioning target area 1 so that the amount Qoa of the outside air OA ′ in the total air supply amount Qsa is maintained at a predetermined amount. The opening degree d1 of the first damper D1 is adjusted according to the setting function da1 = f (Fn) using the rotation speed Fn as a variable. ...... (Damper control)

Then, the process returns to (start) after a predetermined standby time.

(C) On the other hand, in # 1, “all outside air operation”
Is selected, the damper control unit 17d sets the first and third
The opening degrees d1 and d3 of the dampers D1 and D3 are each set to 0% (fully closed), and the opening degrees d2 and d4 of the second and fourth dampers D2 and D4 are respectively set and opened for full outside air operation. Degree db
2, db4 (for example, db2 = 66% opening, db4 = 1
(00% opening).

Subsequently, in # 2, the fan control unit 17b performs the same (fan control) as in the case of "circulation operation", and in # 3, the second determination unit 17e determines that the fan speed Fn as a result of the fan control is It is determined whether the rotation speed is equal to or higher than a set lower limit rotation speed Fnmin (for example, 20% rotation speed of the maximum rotation speed).

(D) When the determination in # 3 is Fn <Fnmin, the fan control unit 17b adjusts and fixes the fan rotation speed Fn to the set lower limit rotation speed Fnmin (that is, until the next (fan control), The rotation speed Fn is maintained at the set lower limit rotation speed Fnmin).

Also, in the "all outside air operation", as the transition control to the "non-temperature regulation mode" (in the case of cooling, so-called outside air cooling) in which the temperature regulation of the air supply SA is stopped, the temperature regulation control unit 1 in # 4.
7c stops the operation of the compressor 5.

Then, the process returns to (start) after a predetermined standby time.

(E) When the determination in # 3 is Fn ≧ Fnmin, the total supply amount Qsa is determined based on the fan speed Fn.
Is calculated, and the maximum outside air cooling output Gmax and the total air conditioning load (entire cooling load) W that can be obtained in the “non-temperature adjustment mode” in which the temperature adjustment of the supply air SA is stopped are calculated by the following equations.

Gmax = (hr / vr−ho / vo) · Qsmax (kcal / H) W = (hr / vr−hs / vs) · Qsa (kcal / H) where Qsmax: maximum total air supply (rated) Value) (m ³ / H) hs; specific enthalpy of supply air SA (kcal / kg (DA)) vs. specific volume of supply air SA (m ³ / kg (DA))

The hs / vs value of the supply air SA is determined by the supply air temperature ts (° C.) detected by the supply air temperature sensor 21 and the humidity rs of the supply air SA detected by the supply air humidity sensor 22.
(%), The ho / vo value of the outside air OA and the hr / vr value of the return air RA are calculated by an approximate expression in the same manner as described above.

Then, in # 5, the third determination unit 17f
However, the calculated maximum outside air cooling output Gmax and the total air conditioning load W are compared in magnitude, and when Gmax <W, a transition to the “temperature control mode” in which the temperature of the air supply SA is performed even during “all outside air operation”. As control, the temperature control controller 17c operates the compressor 5 in # 6, performs the same (temperature control) as in the case of "circulation operation", and returns to (start) after a predetermined standby time.

When Gmax ≧ W, the process returns to step # 2 as continuous control of the "non-temperature control mode".

That is, by the above control, h of the outside air OA
o / vo value is larger than hr / vr value of return air RA (h
o / vo ≧ hr / vr), return air RA and outside air O
By performing cooling in “circulation operation” in which the air-fuel mixture with A ′ (diverted outside air) is supplied as air SA, energy saving is achieved while ensuring ventilation.

In the "circulation operation", the total supply amount Q is controlled so that the supply temperature ts is maintained at the set temperature tss.
According to the change of sa and the change of the state of the outside air OA,
While adjusting the temperature control output of the air supply side heat exchanger 3 by adjusting the compressor rotation speed Cn, the target room 1
adjustment of air supply amount q to a and air supply fan 1
3, the total air supply amount Qsa is changed according to the overall air conditioning load (entire cooling load) W of the air conditioning target area 1 as shown in FIG. ) And the total air conditioning load (entire cooling load) W of the air conditioning target area 1 is balanced.

On the other hand, the ho / vo value of the outside air OA is equal to the return air RA.
Is smaller than the hr / vr value of (ho / vo <hr / v
r) In the case of "circulation operation" in which the air-fuel mixture of return air RA and outside air OA 'is used as air supply SA, "total outside air operation" in which the entire amount of supply air SA is outside air OA' is more energy-saving. Cooling with "all outside air operation" is performed because it is more advantageous.

As an embodiment of the cooling in the “all outside air operation”, the rotation speed Cn of the compressor 5 is adjusted so that the supply air temperature ts is maintained at the set temperature tss, and the air supply side heat exchange is performed. While the temperature control output of the heater 3 is being adjusted,
It is determined that the fan rotation speed Fn is equal to or higher than the set lower limit rotation speed Fnmin (Fn ≧ Fnmin), and the maximum outdoor air cooling output Gmax is smaller than the total air conditioning load (entire cooling load) W (Gmax) in the subsequent step # 5. <W) (in other words, the entire amount of the supply air SA is
It is determined that the temperature control (cooling) of the supply air SA is necessary to balance the total air conditioning output (entire cooling output) with the total air conditioning load (entire cooling load) W in the “all outside air operation” A ′. In this case, the operation is continued in the cycles # 6- # 2- # 3- # 5- # 6 including (temperature control control) in # 6 and (fan control) in # 2.

That is, even in the "all outside air operation" in which the whole amount of the supply air SA is the outside air OA ', the change of the total supply amount Qsa (in other words, the change of the total supply amount Qsa so as to maintain the supply air temperature ts at the set temperature tss). Changes in the air conditioning load W) and the outside air OA
In accordance with the state change, while adjusting the temperature control output of the air supply side heat exchanger 3 by adjusting the compressor rotation speed Cn, the air supply amount q to the target chamber 1a by each variable air volume device 16 is adjusted, and By adjusting the rotation speed Fn of the air supply fan 13 in accordance therewith, the total air supply amount Qsa is changed according to the change in the overall air conditioning load (entire cooling load) W of the air conditioning target area 1 as shown by the line A in FIG. The cooling is continuously performed in the “temperature control mode” in which the total air conditioning output (entire cooling output) and the total air conditioning load (entire cooling load) W of the air conditioning target area 1 are balanced.

On the other hand, in the cooling operation state in the above-mentioned "temperature control mode all outside air operation", the fan rotation speed Fn (decrease in the total supply amount Qsa) due to the decrease in the total air conditioning load W causes # 3. , The fan speed Fn is equal to the set lower limit speed F
When it is determined that Fn is smaller than nmin (Fn <Fnmin) (in other words, the total air-conditioning output (entire cooling output) in the “entire outside air operation” is the total air-conditioning load (entire cooling load).
If it is determined that the temperature control (cooling) of the supply air SA is not necessary to balance with W), the operation of the compressor 5 is stopped (stop the temperature control of the supply air SA) in # 4, The mode shifts to the “non-temperature control mode” in which the outside air OA ′ is supplied to the air-conditioning target area 1 as the air supply SA without being temperature-controlled.

As a result of stopping the temperature control of the air supply SA in this mode transition, the fan rotation speed Fn increases (the total air supply amount Qsa increases) and the determination in # 3 becomes (Fn ≧ Fnmin). In the following # 5, the maximum outdoor air cooling output Gmax
Is equal to or greater than the total air conditioning load (entire cooling load) W (Gmax ≧
W) (in other words, in order to balance the total air-conditioning output (entire cooling output) with the total air-conditioning load (entire cooling load) W in the “all outside air operation”, the temperature control (cooling) of the air supply SA. As long as it is determined that is unnecessary, the operation is continued in the cycle of # 5- # 2- # 3- # 5 including only (fan control) in # 2.

That is, even in the “all outside air operation” in which the entire amount of the supply air SA is the outside air OA ′, the supply of air to the target room 1 a by each of the variable air flow amount devices 16 is performed with the temperature control of the supply air SA stopped. By adjusting the amount q and the fan speed Fn associated therewith, the total air supply amount Qsa is changed as shown by the line B in FIG. 4 according to the change in the overall air-conditioning load W and the change in the state of the outside air OA. By changing, the cooling is continuously performed in the “non-temperature control mode” in which the total air conditioning output (entire cooling output) and the total air conditioning load (entire cooling load) W of the air conditioning target area 1 are balanced.

The line B in FIG. 4 illustrates a case where the state of the outside air OA is constant.

In the cooling execution state in the above-mentioned "non-temperature control mode all outside air operation", in # 5 due to an increase in the total air conditioning load (entire cooling load) W in the air conditioning target area 1 and an increase in the specific enthalpy ho of the outside air OA. When it is determined that (Gmax <W), the operation of the compressor 5 is restarted in # 6, and the operation returns to the cooling in the “temperature control mode all outside air operation”.

Further, in the cooling state in the "non-temperature control mode all outside air operation", the total air conditioning load (entire cooling load) W in the air conditioning target area 1 further decreases and the specific enthalpy ho of the outside air OA further decreases. When (Fn <Fnmin) is determined in # 3 due to the decrease in the fan rotation speed Fn due to the above, the fan rotation speed Fn is adjusted to the set lower limit rotation speed Fnmin and fixed after the determination, and FIG. "Non-temperature control mode all outside air operation" mainly for ventilation in a state where the total supply amount Qsa is constant as indicated by the line C in FIG.
I am trying to do.

As described above, the cooling operation has been described. In the heating operation, the same operation mode as described above is adopted in a state in which the heating temperature (for example, tss = 40 ° C.) is adopted as the set temperature tss of the supply air temperature ts.

In both the cooling and the heating, in the above (temperature control), the temperature control load of the air supply side heat exchanger 3 is abnormally large and the air supply temperature ts cannot be adjusted to the set temperature tss. When a limit occurs, the limit is recognized and the control flow proceeds to the next step.

In short, in this embodiment, in performing the “all outside air operation”, the outside air OA ′ is temperature-adjusted to the set temperature tss by the air supply side heat exchanger 3 as a temperature control means.
This temperature-controlled outside air is distributed and supplied to the plurality of air-conditioned rooms 1a, and the supply amount q of the temperature-controlled outside air to each of the air-conditioned rooms 1a is changed by the variable air volume device 16 according to the air-conditioning load of each of the air-conditioned rooms 1a. In the "temperature control mode all outside air operation", when the total supply amount Qsa of the temperature control outside air to the plurality of air-conditioned rooms 1a decreases to the set lower limit, based on the decrease determination of the total supply amount Qsa. The operation of the apparatus is changed from the “temperature control mode whole outside air operation” to the supply-side heat exchanger 3 as a temperature control means.
Is stopped to distribute and supply the non-temperature-controlled outside air to the air-conditioned room 1a, and the supply amount q of the non-temperature-controlled outside air to each of the air-conditioned rooms 1a is changed by the variable air volume device 16 to each of the air-conditioned rooms 1a.
To "non-temperature control mode all outside air operation" which is adjusted according to the air conditioning load of the air conditioner.

Then, the second determination section 17e, and
The temperature control section 17c constitutes a mode switching control means for switching from the "temperature control mode full outside air operation" to the "non-temperature control mode full outside air operation", and the total supply amount Qsa of temperature controlled outside air.
Is determined to have decreased to the set lower limit value, the fan speed Fn is smaller than the set lower limit speed Fnmin (Fn <Fn <
Fnmin).

Another Embodiment Next, another embodiment will be described.

Instead of the portion surrounded by the broken line in the control flow shown in FIG. 2, the flow configuration of the portion surrounded by the broken line in FIG. 5 may be adopted.

In this case, the rotation speed Cn of the compressor 5 is adjusted so that the supply air temperature ts is maintained at the set temperature tss in the “all outside air operation”, and the temperature of the air supply side heat exchanger 3 is adjusted. In a state in which the control output is being adjusted (that is, in a state in which the “temperature control mode” is performed), it is determined in # 3 that the fan rotation speed Fn is equal to or higher than the set lower limit rotation speed Fnmin (Fn ≧ Fnmin), and In the following # 7, the fan rotation speed Fn is set to the set upper limit rotation speed Fnmax (for example, 95% of the maximum rotation speed).
(Fn <Fnmax), the air supply SA is used to balance the total air-conditioning output (entire cooling output) with the total air-conditioning load (entire cooling load) W in the “entire outside air operation”. It is determined that the temperature control (cooling) is necessary. In response to this determination, the cycle of # 7- # 2- # 3- # 7 is repeated to perform the cooling in the "temperature control mode all outside air operation". continue.

In the cooling state in the "temperature control mode all outside air operation", the fan rotation speed Fn (decrease in the total supply amount Qsa) accompanying the decrease in the total air conditioning load W causes a decrease in # 3. The fan rotation speed Fn is equal to the set lower limit rotation speed F
It is determined that the total air conditioning output (entire cooling output) is equal to the overall air conditioning load (entire cooling load) W in the “entire outside air operation” when it is determined that the total air conditioning output (entire cooling load) W is smaller than (Fn <Fnmin). It is determined that the temperature control (cooling) is unnecessary, and in response to this determination, the operation of the compressor 5 is stopped at # 4 (the temperature control of the air supply SA is stopped), whereby the “non-temperature control mode The operation shifts to cooling in "run" (that is, outside air cooling).

As a result of stopping the temperature control of the air supply SA in this mode transition, the fan rotation speed Fn increases (the total air supply amount Qsa increases) and the determination in # 3 becomes (Fn ≧ Fnmin). In the subsequent step # 7, the fan rotation speed Fn is smaller than the set upper limit rotation speed Fnmax (Fn <Fnmax).
Is determined, the total air-conditioning output (entire cooling output) is converted to the total air-conditioning load (entire cooling load) in the "all outside air operation".
It is determined that the temperature adjustment (cooling) of the supply air SA is not necessary to equilibrate with W. On the other hand, in response to this determination, # 7- # 2- # 3- # 7
By repeating this cycle, the cooling in the “non-temperature control mode all outside air operation” is continued.

In the cooling execution state in the above-mentioned "non-temperature control mode all outside air operation", in # 7 due to an increase in the total air conditioning load (total cooling load) W in the air conditioning target area 1 and an increase in the specific enthalpy ho of the outside air OA. When it is determined that the fan rotation speed Fn is equal to or higher than the set upper limit rotation speed Fnmax (Fn ≧ Fnmax), the total air conditioning output (entire cooling output) is balanced with the total air conditioning load (entire cooling load) W in “all outside air operation”. However, it is determined that the temperature control (cooling) of the supply air SA is necessary, and in response to this determination, the operation of the compressor 5 is restarted in # 6, whereby the cooling in the “temperature control mode full outside air operation” is performed. Return.

In the above-described embodiment, the case where the cooling effect is applied to each air-conditioned room 1a by the supply of the non-temperature-regulated outside air in the "non-temperature-control mode all outside air operation" has been described. In the mode "all outside air operation", the present invention can be applied to a case where a heating effect is given to each air-conditioned room 1a by the supply of non-temperature-controlled outside air.

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

[Brief description of the drawings]

FIG. 1 is an overall configuration diagram

FIG. 2 is a control flow sheet

FIG. 3 is a graph showing an air supply amount adjustment mode in circulation operation.

FIG. 4 is a graph showing an air supply amount adjustment mode in all outside air driving.

FIG. 5 is a control flow sheet showing another embodiment.

[Explanation of symbols]

 OA 'Outside air 3 Temperature control means tss Set temperature 1a Room to be air-conditioned q Air supply 16 Variable air flow device Qsa Total air supply 17e, 17c Mode switching control means

Claims (1)

(57) [Claims] The temperature of outside air is set by a temperature control means (3).
(Tss) and the temperature-controlled outside air is
Distribution and supply to the target room (1a)
(1a) The air supply amount (q) of the temperature-regulated outside air for each of
Air-conditioning load of each room (1a) to be air-conditioned by the quantity device (16)
In the total outside air operation in the temperature control mode, which is adjusted according to the temperature control mode, the entirety of the temperature controlled outside air for the plurality of air-conditioned rooms (1a)
When the air supply amount (Qsa) decreases to the set lower limit,
The apparatus is operated based on the determination of the decrease in the body supply amount (Qsa).
From the total outside air operation in the temperature control mode, the operation of the temperature control means (3) is stopped to remove the non-temperature-controlled outside air.
Distributed to and supplied to the air-conditioned room (1a).
Non-temperature controlled outside air supply to each of the target rooms (1a)
(Q) Each room to be air-conditioned by the variable air volume device (16)
(1a) In the non-temperature control mode, which adjusts according to the air conditioning load,
Mode switching control means (17e, 17e,
An outside air introduction type air conditioner provided with 17c) .