JP2013113452A - Air conditioning method of building - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide an air conditioning method of a building suppressing air conditioning energy loss and indoor environment deterioration by a draft or the like by correcting a collapsed air balance between a vertical space and each interior of each room in the building by carrying out a corrective action so as to make a differential pressure or an amount of air movement between the vertical space and the inside of each room zero by means of the existing air conditioners.SOLUTION: A vertical space 1 penetrating an interior of a building B and a room R1 are connected to each other by gaps or the like. A part of a returned air of the room R1 is mixed with an outside air introduced from an outside air introducing port 5b by an air returning fan 12 of an air conditioner 11 and supplied to the room R1 as an air conditioned air after carrying out a temperature regulation by a heating coil 11b and a cooling coil 11c, and a part of the remainder of the returned air is exhausted from exhaust ports 5a, 5c. A differential pressure between the room R1 and the vertical space 1 is measured by a first measuring device 31, and a rotating speed of the air returning fan 12 or an opening of an exhaust damper 13 is controlled by a control device C so as to make the differential pressure zero.

Description

  The present invention relates to an air conditioning method for buildings, and particularly relates to an air conditioning suitable for buildings such as buildings.

  Normally, air conditioning in a building is designed and adjusted by taking an air balance so that the balance between the sum of outside air introduction amounts (OA) and the sum of exhaust air amounts (EA) on each floor is zero. However, when the air balance is lost, the gap wind corresponding to EA-OA (difference between EA and OA) passes vertically through the building such as the staircase, elevator shaft, pipe shaft (hereinafter referred to as “vertical space”). ) Flows into the room through the gap between the room and the partition wall. For this reason, for example, air flows from a floor with excessive OA to a floor with excessive EA through a vertical space, and the entire building is conditioned and humidity-controlled to exhaust a lot of conditioned air, or introduce excessive outside air. As a result, the air conditioning energy is wasted. The causes of the collapse of the air balance include the following.

[Chimney effect]
In a high-rise building, when the temperature difference between the air-conditioning temperature and the outside air widens, a phenomenon (chimney effect) in which the pressure difference between the room and the outside changes in the height direction occurs. When this chimney effect occurs, on the floor where “indoor pressure <outdoor air pressure” (for example, the underground floor in winter), the outside air OA ′ that flows in from the sum of OA and the opening to the outside (the access path to the underground passage, etc.) Becomes larger than the total sum of EA, and excess air flows out from the room into the vertical space through the gaps in the walls of the vertical space. On the other hand, on floors where “indoor pressure> outdoor air pressure” (for example, higher floors in winter), the sum of EA and the sum of indoor air EA ′ flowing out of the opening to the outside is larger than the sum of OA. Therefore, the shortage flows from the vertical space into the room through the gaps in the walls of the vertical space.

[Air balance of variable air volume air conditioner is poor]
When the rotation speed of the supply / exhaust fan or the opening of the damper changes due to control where the control target is not room pressure, such as indoor temperature control or CO ₂ concentration control, the room pressure changes as a result of the control. The air volume of the gap changes, affecting the balance of OA and EA.

[Incomplete air balance of air conditioners on the floor]
When there are air supply by multiple air conditioners and exhaust of constant air volume (CAV) on the floor, adjusting the air balance when operating all air conditioners reduces the total OA when a part of the air conditioners is stopped For this reason, the draft air flows into the room from the vertical space so as to compensate for the shortage.

  For example, there are the following to suppress the circulation of air inside and outside such a building. First, in the so-called double door system, a windbreak room is constructed, the air that has entered the windbreak room from the inside is returned to the indoor, and the air that has entered the windshield room from the outside is returned to the outside, so that There is one that prevents air flow and reduces loss of air conditioning energy (Patent Document 1). In addition, when the outside air pressure is high, by closing the damper that leads to the outside and preventing the outside air from flowing into the room, the amount of outside air inflow is increased more than usual, preventing loss of air conditioning energy. (Patent Document 2).

Japanese Patent No. 4515173 Japanese Examined Patent Publication No. 7-107460

  The technique described in Patent Document 1 is applied to a general chamber because a windbreak booth is separately provided and the flow of air inside and outside is suppressed by controlling an exhaust fan provided in the windbreak chamber. In such a case, it is necessary to provide such a windbreak booth in each room. In the technique described in Patent Document 2, it is necessary to install a dedicated air duct and a damper. Therefore, none of these conventional techniques can prevent the above-described collapse of the air balance by using the existing air conditioning equipment as it is.

  As described above, the collapse of the air balance is caused by the movement of air through the vertical space. The present invention corrects the collapse of the air balance by using the existing air-conditioning equipment so that the differential pressure between the vertical space and the room or the amount of air movement becomes zero. The purpose is to suppress the loss of air conditioning energy and the deterioration of the indoor environment.

  In order to achieve the above object, the present invention provides a method for air conditioning a vertical space penetrating the interior of a building and a room communicated by a gap, an opening, or a duct. A part of the mixture is mixed with the outside air introduced from the outside air introduction port, heat-exchanged by a heat exchanger to adjust the temperature, and then supplied to the chamber as conditioned air, and the remaining part of the return air is exhausted from the exhaust port. In the air conditioning method, the conditioned air after temperature adjustment is supplied to the chamber by a variable air volume method that is independent of the pressure in the room, and the differential pressure in the chamber and the vertical space is measured and the difference is measured. The rotational speed of the return air fan is controlled so that the pressure becomes zero.

For example, when the chamber pressure is higher than the atmospheric pressure in the vertical space, the differential pressure (chamber pressure−vertical space pressure) is a positive value. If the number of rotations of the return air fan is increased at this time, the amount of return air flowing from the room increases, but the temperature and humidity are adjusted via a heat exchanger such as a coil and then returned to the room. Due to the resistance, the amount of air returned to the room is reduced. That is, the amount of air returned to the room is less than the amount of return air. Further, when the rotational speed of the return air fan is increased, the amount of air flowing out of the room and the amount of air flowing into the heat exchanger through the exhaust port damper and the like increase. At this time, all of the air passing through the heat exchanger is supplied to the room by the variable air volume method. However, the variable air volume method determines the air volume regardless of the room pressure control, for example, according to the indoor temperature. Since the rotational speed of the fan is determined, by increasing the rotational speed of the return air fan, air exceeding the required air volume of the variable air volume system flows to the variable air volume unit. Then, the variable air volume unit performs control to lower the rotational speed of the air supply fan that supplies air into the room, for example. Therefore, when the rotation speed of the return air fan is increased, the rotation speed of the supply air fan is decreased and the chamber pressure is decreased (the amount of air passing through the variable air volume unit and the heat exchanger is not changed at this time). As a result, the chamber pressure decreases, so that the differential pressure (chamber pressure−longitudinal space pressure) changes to zero.
Conversely, when the chamber pressure is lower than the atmospheric pressure in the vertical space, the differential pressure (chamber pressure−vertical space pressure) is a negative value. In this case, the chamber pressure rises by lowering the rotational speed of the return air fan, so that the differential pressure (chamber pressure-vertical space pressure) changes to become zero.

  When the rotational speed of the return air fan is controlled, a certain amount of time passes after the rotational speed of the return air fan reaches a predetermined minimum or maximum value, and then the damper of the exhaust port is closed by a certain amount or constant. An opening operation may be performed, and then the rotational speed of the return air fan may be controlled so that the differential pressure becomes zero.

  When the rotational speed of the return air fan is controlled, if the differential pressure does not become 0 even after a predetermined time has elapsed after the rotational speed of the return air fan reaches a predetermined minimum value or maximum value, You may make it control so that the said differential pressure | pressure may be set to 0 by adjusting the opening degree of the damper of the said exhaust port.

  When the opening degree of the damper of the exhaust port is further controlled, if the differential pressure does not become 0 even after a certain time has elapsed after the damper of the exhaust port is fully opened or fully closed, a part of the return air is When mixing with the outside air introduced from the outside air inlet, when the amount of the return air flow to be mixed can be adjusted by the opening degree of the return air damper provided in the return air and outside air mixing flow path, May be controlled so that the differential pressure becomes zero.

  A parameter that determines the responsiveness of the control for adjusting the rotational speed of the return air fan may be changed based on the differential pressure between the outdoors and the room.

  A parameter that determines the responsiveness of the control for adjusting the rotation speed of the return air fan may be changed based on the temperature difference between the room temperature and the outside air temperature and the height of the room.

  Instead of the differential pressure, an output value of a device that outputs a physical quantity (for example, voltage or current) proportional to the differential pressure may be used.

  In place of the differential pressure, a physical quantity (for example, voltage or current) that is provided in an opening formed in a wall that separates the chamber and the vertical space and is proportional to the air volume, the wind speed, or the air volume that passes through the opening is output. You may make it use the output value of an apparatus.

  According to the present invention, the existing air conditioner is controlled, and the return air fan is adjusted so that the differential pressure between the vertical space and the room or the amount of air movement becomes zero. It is possible to suppress the loss of air-conditioning energy and the deterioration of the indoor environment due to drafts and the like.

It is explanatory drawing which showed typically the outline of the structure of the air conditioning system for enforcing the air conditioning method concerning embodiment. It is explanatory drawing which showed the mode for changing the responsiveness of control by operation of a return air fan and an exhaust damper. It is explanatory drawing which shows the relationship between the strength of the chimney effect in a building, and the pressure of vertical space. It is explanatory drawing which showed the mode for changing the responsiveness of control by operation of a return air damper. It is explanatory drawing which showed typically the outline of the structure of the apparatus which outputs the physical quantity proportional to the air volume. It is explanatory drawing which showed typically the outline of the structure of the other apparatus which outputs the physical quantity proportional to an air volume.

  Hereinafter, an embodiment will be described. FIG. 1 is a diagram schematically showing a schematic configuration of an air conditioning system for carrying out an air conditioning method according to the embodiment. In this example, a building having a plurality of floors is shown. The example applied to B is shown. The rooms R1 and R2 on each floor of the building B all have the same configuration and the same air conditioning system is adopted, so the following description will be given taking the room R1 as an example.

  The room R1 is adjacent to a room RE (for example, a toilet or a hot water room) with exhaust, which is located through a vertical space 1 such as an elevator shaft and a wall 2, for example. The machine room 4 is adjacent to the room R1 through the wall 3. The machine room 4 is provided with an air conditioner 11 that performs air conditioning of the room R1.

  The air conditioner 11 has a return air fan 12 and an air supply fan 16 in a chamber 11a. The return air fan 12 introduces the indoor atmosphere (return air) taken from the return air port 3a provided in the wall 3 into the chamber 11a. A part of the return air introduced into the chamber 11a is exhausted from an exhaust port 5a provided in the outer wall 5 of the building B through an exhaust damper 13 as exhaust.

  The remaining part of the return air taken into the chamber 11 a is mixed with the outside air via the return air damper 14. That is, after the outside air introduced into the chamber 11a from the outside air inlet 5b provided in the outer wall 5 of the building via the outside air damper 15 and a part of the return air are mixed, the heating coil 11b, the cooling coil 11c, The temperature and humidity are adjusted by the humidifier 11d. After the temperature and humidity are adjusted, the air supply fan 16 supplies a plurality of VAV units 21 installed in the ceiling space of the room R1 and supplies the air into the room R1 from the air supply ports 22a provided in the ceiling 22. The

  Exhaust air from the room RE with the previous exhaust located between the room R1 and the vertical space 1 is exhausted from the exhaust port 22b provided in the ceiling 22 through the CAV unit 23 by the exhaust duct 24 and the like. It exhausts from the exhaust port 5c provided in the outer wall 5. FIG.

  Although the chamber R1 and the chamber RE with the exhaust, the chamber RE with the exhaust and the vertical space 1, and the chamber R1 and the machine chamber 4 are separated by a wall or the like, they are not closed in an airtight manner, And large and small openings (not shown). Therefore, the room RE, the room R1, the vertical space 1, and the machine room 4 with exhaust are also communicated.

  The return air fan 12 of the air conditioner 11 includes the measurement result of the first measuring device 31 provided on the wall 2 that separates the exhausted room RE and the vertical space 1, and the second result provided on the outer wall 5. The control device C performs inverter control based on each measurement result of the measurement device 32. Similarly, the opening degree of the exhaust damper 13 can be controlled by the control device C based on the measurement results of the first measurement device 31 and the measurement results of the second measurement device 32. In this example, the first measuring device 31 is a differential pressure gauge that measures the differential pressure between the chamber RE with exhaust and the vertical space 1, and the second measuring device 32 includes the machine room 4 and the outdoors. It is a differential pressure gauge that measures the differential pressure between.

  The air conditioning system according to the embodiment has the above-described configuration. Next, an example of the operation will be described. First, during normal times, the exhaust damper 13 and the return air damper 14 are controlled so that the exhaust amount and the outside air intake amount are equal to the outside air intake amount by the outside air damper 15 control from the outside air introduction port 5b. The Further, the rotation speed of the air supply fan 16 is controlled for indoor air conditioning (for example, the rotation speed is controlled according to the room temperature of the room R1 to adjust the supply air volume), and the rotation speed of the return air fan 12 is controlled. Is controlled in accordance with the rotational speed of the air supply fan 16, and the amount of air supply / exhaust in the room is matched (control during normal time).

  First, when the chamber pressure in the chamber R1 is higher than the pressure in the vertical space 1, the differential pressure (chamber pressure−vertical space pressure) measured by the first measuring device 31 is a positive value. At this time, the control output of the rotational speed of the return air fan 12 is controlled to be positive (in the direction of increasing the rotational speed). When the number of rotations of the return air fan 12 increases, the chamber pressure decreases, so that the differential pressure (chamber pressure−vertical space pressure) measured by the first measuring device 31 changes in a direction that becomes zero. Conversely, when the chamber pressure is lower than the longitudinal space pressure, the differential pressure (chamber pressure−vertical space pressure) measured by the first measuring device 31 is a negative value. At this time, the control output of the rotational speed of the return air fan 12 is controlled to be negative (in the direction of decreasing the rotational speed). When the rotational speed of the return air fan 12 decreases, the chamber pressure increases, so that the differential pressure (chamber pressure-vertical space pressure) changes to zero.

  Here, when the rotational speed of the return air fan 12 reaches a preset upper limit value or lower limit value, and the differential pressure still does not become zero even after a certain time (for example, about 10 seconds in consideration of chattering). The exhaust damper 13 is separated from the other control, that is, the normal control described above, and the opening degree control is performed based on the differential pressure (room pressure−vertical space pressure) measured by the first measuring device 31. Do. That is, when the differential pressure (chamber pressure−vertical space pressure) is a positive value, the exhaust damper 13 is controlled to open. When the exhaust damper 13 is opened, a portion of the return air introduced into the chamber 11a is released to the outside as exhaust gas, so that the chamber pressure decreases and the differential pressure (room pressure−vertical space pressure) becomes zero. Change direction.

  On the contrary, when the differential pressure (chamber pressure-vertical space pressure) measured by the first measuring device 31 is a negative value, the exhaust damper 13 is controlled to be closed (the direction in which the opening is reduced). When the opening degree of the exhaust damper 13 decreases, the ventilation amount returned to the chamber R1 as the return air increases and the chamber pressure increases, so that the differential pressure (chamber pressure-vertical space pressure) changes to zero. At this time, the return air damper 14 maintains the opening degree until then. When the differential pressure becomes zero, the control of the exhaust damper 13 is returned to the normal control, and the control based on the differential pressure is only the rotational speed control of the return air fan 12.

  Furthermore, even if the rotational speed of the return air fan 12 reaches a preset upper limit value or lower limit value, and the opening degree of the exhaust damper 13 reaches a preset maximum opening degree or minimum opening degree, the differential pressure When (room pressure-vertical space pressure) does not become zero, the return air damper 14 is controlled separately from the normal control. That is, when the differential pressure (chamber pressure-vertical space pressure) is a positive value, the return air damper 14 is controlled to close. When the opening degree of the return air damper 14 is reduced, the amount of return air returned to the chamber R1 is reduced and the chamber pressure is lowered, so that the differential pressure (chamber pressure-vertical space pressure) is changed to zero. Conversely, when the differential pressure (chamber pressure-vertical space pressure) is a negative value, the opening degree of the return air damper 14 is controlled to increase.

  In addition, when the control by the return air damper 14 is added in this way and the differential pressure becomes zero, the control of the exhaust damper 13 and the return air damper 14 is returned to the normal control, and the differential pressure by the control device C is returned. The control to set to 0 is returned only to the rotational speed control of the return air fan 12.

  According to the above example, the existing air conditioner 11 is used as it is, and the return air fan 12, the exhaust damper 13, and further the return air damper 14 are controlled, so that the differential pressure between the chamber R1 and the vertical space 1 is reduced. It is possible to approach 0, thereby correcting the collapse of the air balance between the room R1 and the vertical space 1 in the building B, and suppressing the loss of air-conditioning energy and the deterioration of the indoor environment due to a draft or the like. .

  By the way, when the differential pressure between the indoor and the outdoor is large or small (that is, when the absolute value of the differential pressure with reference to the differential pressure 0 is large or small), the rotational speed of the return air fan 12 or the opening of the exhaust damper 13 is increased. Even if the degree is the same, the amount of air movement will change. That is, when the differential pressure outside the room increases due to the chimney effect (the indoor pressure increases on higher floors, etc.), the amount of exhaust movement (exhaust from the CAV unit 23 and the exhaust port 5a (not limited to one)). The total amount of exhaust air from the air conditioner is greater than the desired amount. Therefore, if the differential pressure between the indoor and outdoor is increased, it is preferable to reduce the amount of change in the rotational speed of the return air fan 12 and the opening degree of the exhaust damper 13 so as to obtain a desired exhaust amount.

  That is, when the pressure difference between the indoor pressure and the outdoor pressure is large, the degree of change in the rotation speed of the return air fan 12 and the opening degree of the exhaust damper 13 according to the differential pressure between the pressure in the chamber R1 and the pressure in the vertical space 1 To reduce responsiveness. Conversely, when the value of the indoor pressure-outdoor pressure is small, the degree of change in the rotational speed of the return air fan 12 and the opening degree of the exhaust damper 13 according to the differential pressure between the pressure in the chamber R1 and the pressure in the vertical space 1 is set. It is preferable to increase the responsiveness.

  FIG. 2 explains this, and in the figure, the “operation amount” is the operation amount for the return air fan 12 and the exhaust damper 13, and in the figure, the point K is in the chamber R 1. The amount of normal operation of the return air fan 12 and the exhaust damper 13 when the pressure-pressure difference in the vertical space 1 is zero is shown. When the differential pressure is positive, control for increasing the rotational speed of the return air fan 12 and control for increasing the opening of the exhaust damper 13 are performed, and control for increasing the operation amount from the K point to the upper side in the figure. Is done. When the differential pressure is negative, control is performed to reduce the rotational speed of the return air fan 12, and control to reduce the opening of the exhaust damper 13, and control to decrease the operation amount from the K point downward in the figure. Is done.

  And the change of the operation amount shown by the solid line in FIG. 2 shows the case where the pressure difference between the room pressure and the outdoor pressure is not taken into consideration, and the pressure is based on the pressure difference between the pressure in the chamber R1 and the pressure in the vertical space 1, The change in the manipulated variable indicated by the alternate long and short dash line indicates the change in the manipulated variable for improving the response when the pressure difference between the indoor pressure and the outdoor pressure is small. The change of the manipulated variable for weakening the responsiveness when the pressure difference between the pressure and the outdoor pressure is large is shown. Note that FIG. 2 shows the change in responsiveness using proportional control as an example. However, since offset (residual deviation) may appear only with proportional control, integral control may be used as necessary. Good.

  As described above, the degree of change in the operation amount is changed depending on the magnitude of the pressure difference between the indoor pressure and the outdoor pressure, and the parameter for determining the control response is changed, so that the pressure difference according to the indoor / outdoor pressure is changed. Control can be performed at an appropriate response speed. In the air conditioning system shown in FIG. 1, since the second measuring device 32 is installed, it is possible to detect the pressure difference between the indoor pressure and the outdoor pressure and change the parameter that determines the responsiveness of the control described above. It is.

  Moreover, if the indoor-outdoor temperature difference is the same in a certain building, a similar pressure distribution can be obtained. Therefore, if the indoor-outdoor temperature difference is known, the magnitude of the indoor-outdoor differential pressure with respect to the height (number of floors) of the room in the building can be obtained.

  That is, according to the knowledge of the inventors, as shown in FIG. 3, when the indoor-outdoor temperature difference is large, the chimney effect is increased, and as a result, the degree of increase in the indoor pressure with respect to the room height is increased. (Solid line in FIG. 3). Conversely, when the indoor-outdoor temperature difference is small, the chimney effect is small, and as a result, the degree of increase in the indoor pressure with respect to the room height is small (broken line in FIG. 3).

By utilizing this, by calculating the predicted value of the indoor pressure-outdoor pressure at the height of the chamber R1, the parameter for determining the control responsiveness as shown in FIG. As a result, it is possible to perform control at an appropriate response speed according to the magnitude of the pressure difference inside and outside the room. For example, the predicted value of the indoor pressure and the outdoor pressure can be calculated as follows. That is, the density ρ of air can be expressed by the following equation, where t is the temperature (° C.).
ρ = 1.293 / (1 + 0.00367 × t) [kg / m ³ ]
Here, if there is a passage where the vertical space and outside air are always connected to B1F and 1F of the target building, the chimney effect of the upper floor is 1F as the reference (ΔP = 0), and the height difference from 1F is h In proportion to the pressure difference ΔP (indoor pressure−outdoor pressure) increases. Therefore, when the indoor density is ρ ₁ and the outdoor density is ρ ₂ , the differential pressure ΔP is
It can be calculated as ΔP = (ρ ₂ −ρ ₁ ) × g × h. (G is gravitational acceleration)
And by predicting the indoor pressure-outdoor pressure in this way, such a parameter can be changed by the indoor-outdoor temperature difference by the thermometer without using an expensive differential pressure gauge.

  Also, the outside air temperature varies greatly depending on the time (for example, season, time zone, etc.), but the room temperature is controlled by the air conditioner, and the change due to the time is small compared to the outside air temperature. An approximate magnitude of the indoor-outdoor differential pressure relative to the room height can be determined. Therefore, the above-mentioned “when the temperature difference is large” and “when the temperature difference is small” may be regarded as “when the outside air temperature is low” and “when the outside air temperature is high”, respectively.

  Furthermore, as described with reference to FIG. 2, the control of the return air damper 14 is also performed by changing the degree of change in the manipulated variable according to the pressure difference between the indoor pressure and the outdoor pressure. It is possible to perform control at an appropriate response speed according to the magnitude of the pressure difference between the inside and outside of the room by changing the parameter that determines the responsiveness.

  That is, in FIG. 4, the “operation amount” is an operation amount for the return air damper 14, and in the drawing, point L is when the pressure difference between the pressure in the chamber R 1 and the pressure in the vertical space 1 is zero. The amount of operation of the return air damper 14 during normal operation is shown. When the differential pressure is positive, the opening degree of the return air damper 14 is reduced, and when the differential pressure is negative, the opening degree of the return air damper 14 is increased. In FIG. 4, the change in the operation amount indicated by the solid line shows a case based on the pressure difference between the pressure in the chamber R1 and the pressure in the vertical space 1 without considering the pressure difference between the indoor pressure and the outdoor pressure. The change in the operation amount indicated by the alternate long and short dash line indicates the change in the operation amount of the return air damper 14 for enhancing the responsiveness when the pressure difference between the indoor pressure and the outdoor pressure is small, and the operation amount indicated by the broken line This change indicates a change in the operation amount of the return air damper 14 for weakening the responsiveness when the pressure difference between the indoor pressure and the outdoor pressure is large.

  Taking into account the magnitude of the pressure difference between the indoor pressure and the outdoor pressure, the degree of change in the operation amount of the return air damper 14 is changed, and the parameter that determines the control responsiveness is changed. It is possible to control at an appropriate response speed according to the magnitude of the differential pressure. Of course, in this case, as described with reference to FIG. 3, the parameter may be changed based on the indoor-outdoor temperature difference instead of the pressure difference between the indoor pressure and the outdoor pressure.

  In the above-described embodiment, the rotational pressure control of the return air fan 12 is first given priority so that the differential pressure becomes zero. However, the opening degree control of the exhaust damper 13 may be preferentially controlled. Good. In such a case, when the opening degree of the exhaust damper 13 is controlled, if the differential pressure does not become zero even after a certain time has elapsed after reaching full open or full close, the rotational speed of the return air fan 12 is further increased. Control may be performed so that the differential pressure becomes zero. When the rotational speed of the return air fan 12 is further controlled as described above, even if a certain time elapses after the rotational speed of the return air fan 12 reaches a predetermined minimum value or maximum value, the differential pressure becomes zero. If this is not the case, when the part of the return air is mixed with the outside air introduced from the outside air inlet, the opening of the return air damper 14 may be controlled so that the differential pressure becomes zero. .

  Even if the rotational speed of the return air fan 12 reaches a preset upper limit value or lower limit value and a certain time (for example, about 10 seconds in consideration of chattering) elapses, the differential pressure (room pressure-longitudinal space pressure) still remains. When the value does not become 0, the opening degree of the exhaust damper 13 may be further increased by a predetermined amount from the previous opening degree or may be decreased by a predetermined amount.

  That is, when the differential pressure (chamber pressure−vertical space pressure) is positive and the rotational speed of the return air fan 12 reaches the upper limit value, the opening degree of the exhaust damper 13 is further determined in advance from the previous opening degree. The opening degree is increased by a predetermined amount (for example, approximately 5 when fully open is 100 and fully closed is 0). When the opening degree of the exhaust damper 13 increases, the amount of the return air introduced into the chamber 11a that is released to the outside as exhaust increases, so the room pressure decreases. When the differential pressure (room pressure-vertical space pressure) reaches a predetermined negative value, the rotational speed of the return air fan 12 is lowered from the upper limit value so that the differential pressure (room pressure-vertical space pressure) is reduced. Control is returned to zero. At this time, the exhaust damper 13 maintains the opening degree as it is.

  On the contrary, when the rotational pressure of the return air fan 12 reaches the lower limit with the differential pressure (chamber pressure−vertical space pressure) being negative, the opening degree of the exhaust damper 13 is determined in advance from the opening degree so far. Decrease by a predetermined amount. When the opening degree of the exhaust damper 13 decreases, the ventilation amount returned to the chamber R1 as return air increases and the chamber pressure increases. Then, when the differential pressure (room pressure−vertical space pressure) reaches a predetermined value of positive pressure, the rotational speed of the return air fan 12 is increased from the lower limit value, and the differential pressure (room pressure−vertical space pressure) is increased. Return to control to zero.

  Furthermore, even if a predetermined time elapses after the opening degree of the exhaust damper 13 is increased or decreased by a predetermined amount, the differential pressure (chamber pressure−vertical space pressure) does not become a predetermined value of negative pressure or positive pressure. In this case, the opening degree of the exhaust damper 13 is further increased or decreased by a predetermined amount. That is, when the differential pressure (chamber pressure−vertical space pressure) is a positive value and the rotational speed of the return air fan 12 reaches the upper limit value and the exhaust damper 13 opening degree is increased by a predetermined amount, the negative pressure does not become a predetermined value. The exhaust damper 13 is further increased by a predetermined amount. Conversely, when the differential pressure (chamber pressure-vertical space pressure) is a negative value and the rotational speed of the return air fan 12 reaches the lower limit value, the positive pressure does not become the predetermined value even if the opening degree of the exhaust damper 13 is reduced by a predetermined amount. For this, the opening degree of the exhaust damper 13 is further reduced by a predetermined amount.

  Further, even if the rotational speed of the return air fan 12 reaches a preset upper limit value or lower limit value, and the opening degree of the exhaust damper 13 reaches a preset maximum opening degree or minimum opening degree, the differential pressure ( When the chamber pressure-vertical space pressure does not reach a predetermined value of negative pressure or positive pressure, the return air damper 14 may be controlled separately from the normal control.

  That is, even if the differential pressure (chamber pressure-vertical space pressure) is a positive value, the return air fan 12 rotation speed reaches the upper limit value, and the opening degree of the exhaust damper 13 does not reach the predetermined value of the negative pressure. In such a case, control is performed so that the return air damper 14 is closed. When the opening degree of the return air damper 14 is reduced, the amount of return air returned to the chamber R1 is reduced. As a result, the chamber pressure is lowered, so that the differential pressure (room pressure−vertical space pressure) is changed to zero. Conversely, when the differential pressure (chamber pressure−vertical space pressure) is a negative value, the return air fan 12 rotation speed reaches the lower limit value and the exhaust damper 13 does not reach the predetermined value even if the opening degree reaches the minimum opening degree. First, the opening degree of the return air damper 14 is controlled to be increased.

  Since the adjustment of the amount of air movement can be performed more finely by performing the rotation speed control of the return air fan 12 than by performing the opening degree control of the exhaust damper 13, the adjustment of the exhaust damper 13 is performed as described above. If the opening degree is increased or decreased by a predetermined amount step by step, and the amount of air movement is adjusted by continuously controlling the rotational speed of the return air fan 12, the chamber pressure is reduced. It becomes possible to adjust.

  In the air conditioning system shown in FIG. 1, the first measuring device 31 and the second measuring device 32 both use a differential pressure gauge. However, the present invention is not limited to this, and a physical quantity proportional to the differential pressure (for example, voltage Or an output value of a device that outputs a current), or an opening (not shown) formed in the wall 2 separating the chamber R1 and the vertical space 1 is proportional to the air volume, the wind speed, or the air volume passing through the opening. The output value of the device that outputs the physical quantity (for example, voltage or current) may be used.

  FIG. 5 shows an example of a measuring device 51 that outputs an object quantity proportional to the air volume. The measuring device 51 has an interior of a chamber 52 divided into two flow paths 52a and 52b. Is provided with a hot-wire anemometer 53, and two electrodes 54 and 55 are provided in the other channel 52b. The electrode 54 has high rigidity, and the electrode 55 has a structure that is flexibly deformed by receiving wind. These two electrodes 54 and 55 are arranged side by side along the flow path of the wind, and when the wind is not flowing through the flow path, they are in contact with each other.

  If the wind flows from the opening 56 toward the opening 57, the electrode 55 is deformed toward the opening 57, so that the contact state of the two electrodes is released and the contact is opened (the contact is opened). Cut). Conversely, when wind flows from the opening 57 toward the opening 56, the electrode 55 tends to be deformed toward the electrode 54, so that the contact remains closed (the contact remains connected). Thus, the direction of wind flow can be detected in the open / closed state of the electrode 54 and the electrode 55, and the wind intensity can be measured by the hot wire anemometer 53. The output from the hot wire anemometer 53 is converted by the converter 58 and output from the output line 59 to, for example, the control device C.

  FIG. 6 shows an example of another measuring device 61 that outputs a quantity proportional to the air volume. The main body 62 of the measuring device 61 is filled with a liquid, and the pendulum 63 is immersed in the liquid. . The pendulum 63 has a central portion 63a supported by a fulcrum 64 provided in the liquid, and underwater resistors 63b and 63c that also serve as weights are provided at both ends.

  A wind receiving body 63d is provided above the central portion 63a of the pendulum 63 and protrudes from the water surface. And the wind which flows through the flow paths 65 and 66 of the wind provided facing the upper part of the main body 62 can be received. The position of the wind receiving body 63d is measured by a laser distance meter 67, and it is possible to measure the wind direction and the wind speed from the difference between the distance when there is no wind and the measured distance. Since the pendulum 63 is immersed in the liquid, the viscosity of the liquid can prevent self-excited vibration of the wind receiving body 63d and sudden movement due to sudden wind.

Although the above shows an example in which the present invention is applied to a system that controls the supply air volume of conditioned air into the room according to the indoor temperature, for example, the supply of air into the room by the concentration of indoor CO ₂ The present invention can also be applied to a system for controlling the air volume. Thus, for example a system of the CO ₂ concentration sensor is installed in a room, by adjusting the degree of opening of the exhaust damper 13 and the return air damper 14 based on the numerical value indicated by the CO ₂ concentration sensor, to control the outside air intake amount into the room In the same manner as described above, the opening degree of the exhaust damper 13 and the return air damper 14 may be controlled so that the “room pressure−vertical space pressure” becomes zero.

  For example, when the return air damper 14 is fully closed, all the air discharged from the chambers R1 and R2 through the return air port 3a by the return air fan 12 is exhausted to the outside. However, the discharged air is the return air in the present invention. Of course, when the return air damper 14 is fully closed, the return air fan 12 substantially functions as an exhaust fan, but is still a return air fan in the present invention.

  The present invention is useful for air conditioning of relatively high-rise buildings such as buildings.

DESCRIPTION OF SYMBOLS 1 Vertical space 2, 3 Wall 3a Return air port 4 Machine room 5 Outer wall 5a, 5c Exhaust port 5b Outside air introduction port 11 Air conditioner 11a Chamber 11b Heating coil 11c Cooling coil 11d Humidifier 12 Return air fan 13 Exhaust damper 14 Return air damper 15 Outside air damper 16 Supply fan 21 VAV unit 22 Ceiling 22a Supply port 22b Exhaust port 23 CAV unit 24 Exhaust duct 31 First measurement device 32 Second measurement device B Building C Control device R1, R2 Chamber RE Exhaust Room

Claims (8)

A method of air-conditioning a vertical space penetrating through the interior of a building and a room connected by a gap, an opening, or a duct,
A part of the return air in the room is mixed with the outside air introduced from the outside air introduction port by the return air fan, the heat is exchanged by the heat exchanger and the temperature is adjusted, and then supplied to the room as conditioned air, and the remaining return air Part of the air-conditioning method of exhausting from the exhaust port,
The chamber is supplied with conditioned air after temperature adjustment by a variable air volume method independent of the pressure in the room,
A building air-conditioning method, wherein the pressure difference between the chamber and the vertical space is measured, and the rotational speed of the return air fan is controlled so that the differential pressure becomes zero. When the rotational speed of the return air fan is controlled, a certain amount of time passes after the rotational speed of the return air fan reaches a predetermined minimum or maximum value, and then the damper of the exhaust port is closed by a certain amount or constant. 2. The building air conditioning method according to claim 1, wherein the number of rotations of the return air fan is controlled so that the differential pressure becomes zero after performing an opening operation. When the rotational speed of the return air fan is controlled, if the differential pressure does not become 0 even after a predetermined time has elapsed after the rotational speed of the return air fan reaches a predetermined minimum value or maximum value, The building air conditioning method according to claim 1, wherein the differential pressure is controlled to be zero by adjusting an opening degree of the damper of the exhaust port. When controlling the opening degree of the exhaust outlet damper, if the differential pressure does not become 0 even after a certain period of time has elapsed after the exhaust opening damper has fully opened or fully closed,
When mixing a part of the return air with the outside air introduced from the outside air inlet, when the return air volume to be mixed can be adjusted by the opening of the return air damper provided in the return air and outside air mixing flow path 4. The building air conditioning method according to claim 2 or 3, wherein the opening of the return air damper is controlled so that the differential pressure becomes zero. The parameter which determines the responsiveness of the control which adjusts the rotation speed of the said return air fan based on the differential pressure | voltage between the outdoors and the said room is changed, The any one of Claims 1-4 characterized by the above-mentioned. How to air-condition buildings. Based on the temperature difference between the room temperature and the outside air temperature and the height of the room, a parameter for determining the responsiveness of the control for adjusting the rotation speed of the return air fan is changed. The building air conditioning method according to claim 1. The building air conditioning method according to claim 1, wherein an output value of a device that outputs a physical quantity proportional to the differential pressure is used instead of the differential pressure. Instead of the differential pressure, an output value of a device that is provided in an opening formed in a wall that separates the chamber and the vertical space and outputs a volume of air passing through the opening, a wind speed, or a physical quantity proportional to the volume of air is used. The building air-conditioning method according to claim 1, wherein

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