JP2007024363A - Room pressure control device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To inhibit variation of room pressures of a plurality of rooms connected with one air conditioner by simple control. <P>SOLUTION: This room pressure control device 10 for controlling room pressures of the rooms connected with the air conditioner through air supply passages to a target value, comprises an air conditioner control portion 14 for determining air volume controlled variable of the air conditioner from a first deviation value of a measured value of static pressure of the air supply passage measured by a first pressure meter 51 mounted in the air supply passage and a target value of static pressure of the air supply passage on the basis of quadratic function characteristics, and an exhaust damper control portion 16 for determining opening controlled variable of an exhaust damper 41 discharging the air in the room from a secondary deviation value of a measured value of the room pressure of the room measured by a second pressure meter 52 mounted in the room and a target value of the room pressure of the room on the basis of the quadratic function characteristics. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention relates to a room pressure control device, and more particularly to a room pressure control device suitable for keeping constant the room pressure of a plurality of rooms connected to one air conditioner.

  In facilities such as clean rooms for pharmaceutical manufacturing and aseptic animal breeding rooms, it is necessary to keep the rooms clean and prevent the entry of bacteria from outside. The barrier is formed higher than the pressure. Moreover, in such a facility, when changing the production line or changing the experiment contents, the room is sealed and the inside of the room is disinfected by formalin fumigation.

In an air conditioner used in such a facility, a pressure adjustment exhaust damper is controlled by PID control, or a pressure adjustment exhaust damper is controlled by fuzzy control (see Patent Document 1). ).
JP-A-5-224760

  However, the method of controlling the pressure adjusting exhaust damper by PID control has a problem that the room pressure fluctuates greatly when the door of the room is opened and closed. Further, in the method of controlling the exhaust damper for pressure adjustment by fuzzy control, there is a problem that it is necessary to perform fuzzy inference calculation and the control becomes complicated.

  The objective of this invention is providing the room pressure control apparatus which can suppress the fluctuation | variation of the room pressure of the several room connected to one air conditioner by simple control.

A room pressure control apparatus according to the present invention is a room pressure control apparatus for controlling a room pressure of a room connected to an air conditioner through an air supply passage to a target value, and is provided in the air supply passage. The air volume control of the air conditioner based on the quadratic function characteristic from the first deviation value between the measured value of the static pressure of the supply passage measured by the pressure gauge of 1 and the target value of the static pressure of the supply passage. 2 from the second deviation value between the measured value of the room pressure of the room and the target value of the room pressure of the room measured by the second pressure gauge provided in the room. And an exhaust damper control unit that obtains an opening degree control amount of the exhaust damper for exhausting the air in the room based on a second-order function characteristic.
Here, a first filter that performs an averaging filter process on the output signal of the first pressure gauge, and a second filter that performs an averaging filter process on the output signal of the second pressure gauge The air conditioner control unit further includes a first value of a measured value of the static pressure of the supply passage and a target value of the static pressure of the supply passage that has been subjected to the averaging filter process by the first filter. The air volume control amount of the air conditioner is obtained from the deviation value of 3 based on a quadratic function characteristic, and the exhaust damper control unit measures the room pressure of the room subjected to the averaging filter process by the second filter. The opening control amount of the exhaust damper may be obtained from a fourth deviation value between the value and the target value of the room pressure of the room.
The air conditioner control unit performs a correction dead zone process for setting a correction dead zone for both the first or third deviation value and time, obtains an air volume control amount of the air conditioner, and the exhaust damper control unit A correction dead zone process for setting a correction dead zone for both the second or fourth deviation value and time may be performed to obtain the opening degree control amount of the exhaust damper.
A measured value of the static pressure of the exhaust passage measured by another pressure gauge provided in an exhaust passage between the exhaust fan for exhausting air from the room and the room, and a target value of the static pressure of the exhaust passage. An exhaust fan control unit that obtains the air volume control amount of the exhaust fan based on a quadratic function characteristic from the fifth deviation value may be further provided.
The filter further includes another filter that performs an averaging filter process on the output signal of the other pressure gauge, and the exhaust fan control unit performs static filtering on the exhaust passage that has been subjected to the averaging filter process by the other filter. The air flow control amount of the exhaust fan may be obtained based on a quadratic function characteristic from a sixth deviation value between the measured pressure value and the static pressure target value of the exhaust passage.
The exhaust fan control unit may perform a correction dead zone process for setting a correction dead zone for both the fifth or sixth deviation value and time to obtain the air flow control amount of the exhaust fan.
When the local exhaust switch provided in the room is turned on, the other room measured by another pressure gauge provided in the other room whose room pressure is controlled by the room pressure control device. Based on the quadratic function characteristic, the air in the other room is exhausted from the deviation value between the measured value of the room pressure and the target value changed by subtracting a predetermined value from the target value of the room pressure in the other room. For this purpose, another exhaust damper control unit for obtaining an opening control amount of another exhaust damper may be further provided.

The room pressure control device of the present invention has the following effects.
(1) By adopting the secondary deviation control method, the parameters can be simplified compared to the PID control method, so that fluctuations in the chamber pressure can be suppressed by simple control, and compared to the PID control method. Since the followability and stability can be improved, the chamber pressure can be stably controlled.
(2) Since stable and flexible control is possible compared to variable air volume control by chamber pressure and constant air volume ratio control of supply and exhaust, local exhaust system when opening / closing doors, starting air conditioner, changing ventilation frequency A stable room pressure (air flow) can be ensured at all times during the operation of.
(3) Since the control is performed in the state of the optimum device, the motor damper is not operated as much as possible except when the local exhaust device is operated or when the room pressure is corrected, so that the life of the device can be drastically improved.
(4) Since airflow can be ensured even during a momentary power failure (power failure), the room pressure can be controlled without stopping the system during a power failure.
(5) By adopting an open network such as a programmable logic controller (PLC), it is possible to improve the replaceability from the existing system and the expandability of the future system.
(6) A total air conditioning system can be constructed by applying to temperature control, humidity control, and heat source control.

Embodiments of a room pressure control apparatus according to the present invention will be described below with reference to the drawings.
As shown in FIG. 1, the room pressure control apparatus 10 according to the first embodiment of the present invention sets the room pressures of the first and second rooms to +30 Pa (target value) by using a return type (forward ring type) air conditioning system. ) And +20 Pa (target value), respectively. In the following, the target value is represented by a deviation value from 1 atmosphere (1013 hPa).

  As shown in FIG. 2, the room pressure control device 10 includes first to third filters 11 to 13, an air conditioner control unit 14, a constant air volume device control unit 15, and first and second exhaust damper controls. Units 16 and 17 and a control unit 18.

  The 1st thru | or 3rd filters 11-13 are for performing the averaging filter process as shown in FIG. 3 with respect to the output signal (measurement value) of the 1st thru | or 3rd pressure gauges 51-53. . That is, the first filter 11 filters and averages the output signal of the first pressure gauge 51 provided in the air supply passage 61 from the air conditioner 20 to the first and second rooms shown in FIG. The second and third filters 12 and 13 filter the output signals of the second and third pressure gauges 52 and 53 provided in the first and second chambers, respectively. It is for averaging.

  By performing the averaging filter process on the output signals in the first to third pressure gauges 51 to 53, the control can be stabilized as compared with a normal monitor that is controlled without performing the averaging filter process. . Here, the control by performing such an averaging filter process is referred to as an “averaging monitor”.

  Note that the first to third filters 11 to 13 are controlled by the filter processing control signal input from the control unit 18 to perform the averaging filter processing.

  The air conditioner control unit 14 is configured by, for example, a programmable logic controller (hereinafter referred to as “PLC”), and calculates the air volume control amount of the air conditioner 20 based on the output signal of the first filter 11. Then, the frequency of the input signal of the air conditioner inverter 21 (see FIG. 1) for controlling the rotation speed of the air supply fan of the air conditioner 20 is changed according to the calculated air volume control amount.

  The constant air volume device control unit 15 is configured by, for example, a PLC, and based on a control signal input from the control unit 18, first and second constant air volume devices (CAV) 31 provided in the air supply passage 61. , 32 output an air flow signal and an operation / stop command.

  The first exhaust damper control unit 16 is composed of, for example, a PLC, calculates the opening control amount of the first exhaust damper 41 based on the output signal of the second filter 12, and calculates the calculated opening control amount. Is output to the first exhaust damper 42.

  The second exhaust damper control unit 17 is configured by, for example, a PLC, calculates the opening control amount of the second exhaust damper 42 based on the output signal of the third filter 13, and calculates the calculated opening control amount. Is output to the second exhaust damper 42.

  Here, the air conditioner control unit 14, the first exhaust damper control unit 16, and the second exhaust damper control unit 17 are controlled by the secondary deviation control method, which is a feature of the room pressure control device of the present invention, of the air conditioner 20. An air flow control amount, an opening control amount of the first exhaust damper 41, and an opening control amount of the second exhaust damper 42 are calculated.

As shown in an example in FIG. 4, the secondary deviation control method is based on a quadratic function characteristic (control amount = K _p × (deviation value) ² ) from a deviation value between a measured value and a target value (set value). The control amount (industrial value) is obtained. Such a secondary deviation control method has the following characteristics as compared with the PID control method.

(1) Good followability.
In the secondary deviation control method, as shown by the quadratic function characteristic B in FIG. 5A, when the deviation value is larger than the PID characteristic A, the control is determined with a large manipulated variable (however, limited by the maximum manipulated variable). .) Further, when the deviation amount is small, the control is determined by a small manipulated variable, so that overshoot does not occur as shown by the curve A in FIGS. 5B and 5C, and the followability is good.
On the other hand, in the PID method indicated by the PID characteristic A in FIG. 5A, it is necessary to reduce the P component (proportional component) or increase the D component (differential component) in order to improve followability, and FIG. ) And (c), as shown by curve A, overshoot occurs. As a result, when the PID control method is adopted in the room pressure control in which overshoot is not allowed, it is necessary to increase the P component (proportional component) or the I component (integral component), as shown by the PID characteristic A in FIG. Therefore, it takes time to follow.

(2) Good stability.
In the secondary deviation control method, as shown by the quadratic function characteristic B in FIG. 6A, when the deviation value is in the stable region (stable zone), the control amount for the deviation value is small. As a result, the slope characteristic of the control amount (correction amount) becomes small as shown by the curve B in FIGS. 6B and 6C, so that stable control is possible.
On the other hand, in the PID control method indicated by the PID characteristic A in FIG. 6A, it takes time to reach the stable point b as shown by the curve A in FIGS. 6B and 6C. If the P component (proportional component) and the I component (integral component) are increased for the purpose of improvement, it becomes difficult to follow from disturbance to disturbance.

(3) No time axis is required.
In the secondary deviation control method, the control amount (correction amount and manipulated variable) is always determined by the deviation value with respect to the target value (set value), so that no time axis is required.
On the other hand, in the PID control method, an offset (residual deviation) occurs only with the P component (proportional component), so that the deviation is eliminated by time components such as the I component (integral component) and the D component (differential component). . As a result, since a time component is required, it becomes difficult to deal with disturbance from stable time.

(4) In the secondary deviation control method, as shown in FIG. 7, one quadratic function characteristic B includes all of the P component (proportional component), I component (integral component), and D component (differential component).

(5) Parameters can be simplified.
In the secondary deviation control method, the calculation block diagram is as shown in FIG. 8, and the following calculation formula is obtained. SV is a target value (set value), PV _fn is a measured value (current value) after averaging filter processing, EV _n is a deviation value, MV _a is a control amount (correction amount), K _P is a gain coefficient, MV _n represents the operation amount, and MV _n-1 represents the previous operation amount.
EV _n = PV _fn − SV
MV _a = K _P (EV _n ) ²
MV _n = MV _n-1 + MV _a (in normal operation, when the deviation value is positive)
MV _n = MV _n-1 -MV _a (in the case of positive operation and the deviation value is negative)
MV _n = MV _n-1 -MV _a (in reverse operation, when the deviation value is positive)
MV _n = MV _n-1 + MV _a (when the deviation value is negative in reverse operation)
Accordingly, there are only two items to be set as parameters, the gain coefficient K _P and the target value (set value) SV, so that the parameters can be simplified.
Note that the quadratic function characteristics shown in FIG. 4 are those for the gain coefficient K _P = 1/5, the gain coefficient K _P = 1, and the gain coefficient K _P = 3. When the value range is 0 to 4000, the maximum operation amount is about 2.5% (operation amount = 100).

  The air conditioner control unit 14, the first exhaust damper control unit 16, and the second exhaust damper control unit 17 also perform the correction dead zone processing when a dead zone processing control signal for performing the correction dead zone processing is input from the control unit 18. This is performed to suppress the sensitive reaction (operation) of the air conditioner 20 and the first and second exhaust dampers 41 and 42.

  The correction dead zone process is performed by setting a correction dead zone for both the deviation value and the time. That is, as shown in FIG. 9, if the deviation value is within a predetermined range with respect to the target value (a value between deviation value + P1 and deviation value -P1), the air conditioner control unit 14 and the first exhaust The damper control unit 16 and the second exhaust damper control unit 17 do not calculate control amounts (air volume control amount and opening degree control amount). Further, even if the deviation value is outside the predetermined range with respect to the target value, if the period is within the predetermined time T, the air conditioner control unit 14, the first exhaust damper control unit 16, and the second exhaust The damper control unit 17 does not calculate control amounts (air volume control amount and opening degree control amount).

  The control unit 18 controls the first to third filters 11 to 13, the air conditioner control unit 14, the constant air flow device control unit 15, and the first and second exhaust dampers 16 and 17.

  Next, the operation of the room pressure control device 10 when the air conditioner 20 is started from a stopped state will be described. It is assumed that the opening degrees of the first and second exhaust dampers 41 and 42 are 50% and 60%, respectively.

  When the air conditioner 20 is activated, the control unit 18 of the room pressure control device 10 controls the air conditioner control unit 14 so that the frequency of the input signal of the air conditioner inverter 21 is fixed to a predetermined frequency and output. . As a result, air is supplied from the air conditioner 20 to the air supply passage 61 with a constant air volume.

  The first and second constant air volume devices 31, 32 enter the throttle when the static pressure in the supply passage 61 increases, and conversely, when the static pressure in the supply passage 61 decreases, the dampers open to open the damper. When the first and second constant air volume devices 31, 32 are operated in the process of increasing the static pressure of the air passage 61 to +400 Pa (target value), the operations of the first and second constant air volume devices 31, 32 are performed. And the operation of the air conditioner inverter 21 may be hunting. Therefore, in order to prevent the first and second constant air volume devices 31 and 32 from operating, the control unit 18 determines a control signal for stopping the control operation of the first and second constant air volume devices 31 and 32. Output to the air volume device control unit 15.

  When 20 seconds have passed since the air conditioner 20 was started, the control unit 18 outputs a filter processing control signal for performing the averaging filter processing shown in FIG. 3 to the first filter 11 and also shown in FIG. After outputting the dead zone processing control signal for performing the corrected dead zone processing to the air conditioner control unit 14, the air volume control amount of the air conditioner 20 is calculated by the secondary deviation control method based on the output signal of the first filter 11. The air conditioner control unit 14 is controlled. Thereby, in the air conditioner control unit 14, the air flow control amount is calculated by the secondary deviation control method based on the output signal (measured value) of the first pressure gauge 51 subjected to the averaging filter processing by the first filter 11. After that, the frequency of the input signal of the air conditioner inverter 21 is changed according to the calculated air volume control amount. As a result, the air volume of the air conditioner 20 is controlled so that the static pressure of the air supply passage 61 becomes +400 Pa (target value) while suppressing the sensitive reaction (operation) of the air conditioner 20.

  Thereafter, when the static pressure of the supply passage 61 enters a stable region (that is, when the static pressure of the supply passage 61 enters the range of +390 Pa to +410 Pa for 20 seconds or more), the control unit 18 performs the first and second constants. A control signal for starting the control operation of the air volume devices 31 and 32 is output to the constant air volume device controller 14. Thereby, the 1st and 2nd constant air volume apparatus 31 and 32 operate | moves so that air may be sent to the 1st and 2nd room with fixed air volume.

  Thereafter, the room pressures of the first and second rooms do not fall within the stable range (that is, the room pressure of the first room does not fall within the range of +20 Pa to +40 Pa for 20 seconds or more, and the room pressure of the second room is +10 Pa. The control unit 18 outputs a filter processing control signal for performing the averaging filter processing to the second and third filters 12 and 13 when 3 minutes or more have passed, within 20 seconds or more in the range of ~ 30 Pa). After the dead zone processing control signal for performing the corrected dead zone processing is output to the first and second exhaust damper control units 41 and 42, the secondary deviation control is performed based on the output signals of the second and third filters 12 and 13. The first and second exhaust damper control units 16 and 17 are controlled so as to calculate the opening control amounts of the first and second exhaust dampers 41 and 42 by the method.

  Thereby, in the first and second exhaust damper control units 16 and 17, the second and third pressure gauges 52, the opening degree control amounts of which are subjected to the averaging filter processing by the second and third filters 12 and 13. After being calculated by the secondary deviation control method based on the output signal (measured value) 53, the opening degree of the first and second exhaust dampers 41 and 42 is changed according to the calculated opening degree control amount. As a result, the chamber pressures in the first and second chambers become +30 Pa (target value) and +20 Pa (target value) while suppressing the sensitive reaction (operation) of the first and second exhaust dampers 41 and 42. In addition, the opening degrees of the first and second exhaust dampers 41 and 42 are respectively controlled.

  Thereafter, when the room pressures in the first and second rooms enter the stable range, the control unit 18 air-conditions the air supply passage 61 so as to keep the static pressure in the supply passage 61 at +400 Pa (target value) with respect to the air conditioner control unit 14. The air volume of the machine 20 is controlled, and the first and second exhaust damper control sections 16 and 17 are kept at +30 Pa (target value) and +20 Pa (target value) with respect to the first and second chambers. Then, the opening degree of the first and second exhaust dampers 41 and 42 is controlled.

Next, the operation of the room pressure control device 10 when the mode is shifted from the normal operation to the energy saving operation will be described.
At the time of mode transition, since it is necessary to change the static pressure of the air supply passage 61 while maintaining the chamber pressures of the first and second rooms, the averaging filter process and the correction dead band process are not performed. And it is better to increase the control operation speed. Therefore, the control unit 18 of the room pressure control device 10 outputs a filter process control signal that does not perform the averaging filter process to the first to third filters 11 to 13 and performs a correction dead band process that does not perform the correction dead band process. the control signal and the air conditioner control unit 14 outputs to the first and second exhaust damper control units 16 and 17, the air volume control in accordance with the secondary deviation control scheme using a quadratic function characteristic with a larger gain factor K _p The air conditioner controller 14 and the first and second exhaust damper controllers 16 and 17 are controlled so as to calculate the amount and the opening control amount.

  When the mode of the air conditioner 20 is shifted from the normal operation to the energy saving operation, the control unit 18 of the room pressure control device 10 changes the target value of the static pressure of the air supply passage 61 from +400 Pa to +200 Pa, and the first Based on the output signal of the filter 11, the air conditioner control unit 14 is controlled so as to calculate the air volume control amount of the air conditioner 20 by the secondary deviation control method. As a result, the frequency of the input signal of the air conditioner inverter 21 is lowered according to the calculated air flow control amount, so that the air pressure of the air conditioner 20 is adjusted so that the static pressure of the air supply passage 61 becomes +200 Pa, which is the target value after the change. The air volume is controlled.

  Further, the control unit 18 sends a control signal for stopping the control operation of the first and second constant air volume devices 31 and 32 so as not to operate the first and second constant air volume devices 31 and 32. To the unit 15.

  Thereafter, when the static pressure of the supply passage 61 enters a stable region (that is, when the static pressure of the supply passage 61 enters the range of +190 Pa to +210 Pa for 20 seconds or more), the control unit 18 performs the first and second constants. In order to send air from the air volume devices 31 and 32 to the first and second rooms with a constant air volume and utilize it as an energy saving mode, a control signal for starting the control operation of the first and second constant air volume devices 31 and 32 is generated. Output to the constant air volume device control unit 14.

  Thereafter, the control unit 18 calculates the opening control amounts of the first and second exhaust dampers 41 and 42 by the secondary deviation control method based on the output signals of the second and third filters 12 and 13. The first and second exhaust damper control units 16 and 17 are controlled. As a result, the opening pressure of the first exhaust damper 41 is changed in accordance with the opening degree control amount calculated by the first exhaust damper control unit 16, so that the chamber pressure in the first room is maintained at +30 Pa (target value). At the same time, the opening degree of the second exhaust damper 42 is changed according to the opening degree control amount calculated by the second exhaust damper control unit 17, so that the chamber pressure in the second chamber becomes +20 Pa (target value). Kept.

  Thereafter, the static pressure of the supply passage 61 enters the stable region, the chamber pressure of the first room enters the stable region (+25 Pa to +35 Pa), and the chamber pressure of the second chamber enters the stable region (+15 Pa to +25 Pa). If the operation state continues for 5 minutes or more, the control unit 18 controls the air conditioner control unit 14 and the first and second exhaust dampers so as to end the operation at the time of the mode transition from the normal operation to the energy saving operation. The units 16 and 17 are controlled.

  Next, the operation of the room pressure control apparatus 10 when the mode is shifted from the energy saving operation to the normal operation will be described.

  When the mode of the air conditioner 20 is shifted from the energy saving operation to the normal operation, the control unit 18 of the room pressure control device 10 changes the target value of the static pressure of the air supply passage 61 from +200 Pa to +400 Pa to change the first Based on the output signal of the filter 11, the air conditioner control unit 14 is controlled so as to calculate the air volume control amount of the air conditioner 20 by the secondary deviation control method. As a result, the frequency of the input signal of the air conditioner inverter 21 is increased according to the calculated air volume control amount, and therefore the air volume of the air conditioner 20 so that the static pressure of the air supply passage 61 becomes +400 Pa, which is the target value after the change. Is controlled.

  In contrast to the mode transition from the normal operation to the energy operation described above, the control unit 18 supplies the air from the first and second constant air volume devices 31 and 32 to the first and second rooms with a constant air volume. Therefore, a control signal for starting the control operation of the first and second constant air volume devices 31 and 32 is output to the constant air volume device controller 15.

  Further, the control unit 18 calculates the opening control amounts of the first and second exhaust dampers 41 and 42 by the secondary deviation control method based on the output signals of the second and third filters 12 and 13. The first and second exhaust damper control units 16 and 17 are controlled. As a result, the opening pressure of the first exhaust damper 41 is changed in accordance with the opening degree control amount calculated by the first exhaust damper control unit 16, so that the chamber pressure in the first room is maintained at +30 Pa (target value). At the same time, the opening degree of the second exhaust damper 42 is changed according to the opening degree control amount calculated by the second exhaust damper control unit 17, so that the chamber pressure in the second chamber becomes +20 Pa (target value). Kept.

  Thereafter, the static pressure of the air supply passage 61 enters a stable region (+390 Pa to +410 Pa), the chamber pressure of the first room enters the stable region (+25 Pa to +35 Pa), and the chamber pressure of the second chamber reaches a stable region (+15 Pa). ~ + 25 Pa), when the state that continues is 5 minutes or more, the control unit 18 and the air conditioner control unit 14 and the first and second so as to end the operation at the time of mode transition from the energy saving operation to the normal operation. The exhaust damper control units 16 and 17 are controlled.

Next, a room pressure control apparatus 110 according to a second embodiment of the present invention will be described with reference to FIGS.
As shown in FIG. 10, the room pressure control device 110 according to the present embodiment increases the room pressures of the first and second rooms to +30 Pa (with an all fresh type air conditioning system) equipped with an exhaust fan 70 (+30 Pa). Target value) and +20 Pa (target value), respectively.

  As shown in FIG. 11, the room pressure control device 110 is different from the room pressure control device 10 according to the first embodiment shown in FIG. 2 in that it includes a fourth filter 81 and an exhaust fan control unit 82. .

  The fourth filter 81 is a graph with respect to the output signal (measured value) of the fourth pressure gauge 72 provided in the exhaust passage 62 between the first and second exhaust dampers 41 and 42 and the exhaust fan 70. This is for performing the averaging filter processing as shown in FIG. Note that the fourth filter 81 is controlled by the filter processing control signal input from the control unit 18 to perform the averaging filter processing.

  The exhaust fan control unit 82 calculates the air volume control amount of the exhaust fan 70 by the secondary deviation control method based on the output signal of the fourth filter 81, and controls the rotational speed of the exhaust fan 70 according to the calculated air volume control amount. The frequency of the input signal of the exhaust fan inverter 71 is changed. Note that the exhaust fan control unit 82 is controlled by the dead zone processing control signal input from the control unit 18 to perform the correction dead zone processing.

  Next, the operation of the room pressure control device 110 when the air conditioner 20 is started from a stopped state will be described. It is assumed that the opening degrees of the first and second exhaust dampers 41 and 42 are 50% and 60%, respectively.

  When the air conditioner 20 is activated, the control unit 18 of the room pressure control device 110 controls the air conditioner control unit 14 so that the frequency of the input signal of the air conditioner inverter 21 is fixed to a predetermined frequency and output. At the same time, the exhaust fan controller 82 is controlled so that the frequency of the input signal of the exhaust fan inverter 71 is fixed to a predetermined frequency and output. Thus, air is supplied from the air conditioner 20 to the air supply passage 61 with a constant air volume, and air is discharged from the exhaust passage 62 with a constant air volume by the exhaust fan 70.

  At this time, in order not to operate the first and second constant air volume devices 31 and 32, the control unit 18 outputs a control signal for stopping the control operation of the first and second constant air volume devices 31 and 32. It outputs to the constant air quantity device control unit 15.

  When 20 seconds elapse after the air conditioner 20 is activated, the control unit 18 outputs a filter processing control signal for performing the averaging filter processing shown in FIG. 3 to the first and fourth filters 11 and 81, and After outputting the dead zone processing control signal for performing the corrected dead zone processing shown in FIG. 9 to the air conditioner control unit 14 and the exhaust fan control unit 82, the second order based on the output signals of the first and fourth filters 11 and 81. The air conditioner control unit 14 and the exhaust fan control unit 82 are controlled so as to calculate the air volume control amounts of the air conditioner 20 and the exhaust fan 70 by the deviation control method.

  Thereby, in the air conditioner control unit 14, the air flow control amount is calculated by the secondary deviation control method based on the output signal (measured value) of the first pressure gauge 51 subjected to the averaging filter processing by the first filter 11. The frequency of the input signal of the air conditioner inverter 21 is changed in accordance with the calculated air volume control amount. As a result, the air volume of the air conditioner 20 is controlled so that the static pressure of the air supply passage 61 becomes +400 Pa (target value) while suppressing the sensitive reaction (operation) of the air conditioner 20. Further, in the exhaust fan control unit 82, the air volume control amount is calculated by the secondary deviation control method based on the output signal (measured value) of the fourth pressure gauge 72 subjected to the averaging filter process by the fourth filter 81, The frequency of the input signal of the exhaust fan inverter 71 is changed according to the calculated air volume control amount. As a result, the air volume of the exhaust fan 70 is controlled so that the static pressure of the exhaust passage 62 becomes +400 Pa (target value) while suppressing the sensitive reaction (operation) of the exhaust fan 70.

  Thereafter, when the static pressure of the supply passage 61 enters a stable region (that is, when the static pressure of the supply passage 61 enters the range of +390 Pa to +410 Pa for 20 seconds or more), the control unit 18 performs the first and second constants. A control signal for starting the control operation of the air volume devices 31 and 32 is output to the constant air volume device controller 14. As a result, the first and second constant air volume devices 31 and 32 operate to send air to the first and second rooms with a constant air volume.

  Further, after the static pressure of the exhaust passage 62 enters the stable region (that is, the static pressure of the exhaust passage 62 enters the range of +390 Pa to +410 Pa for 20 seconds or more), the chamber pressures of the first and second rooms are stable. (That is, the room pressure of the first room does not enter the range of +20 Pa to +40 Pa for 20 seconds or more and the room pressure of the second room does not enter the range of +10 Pa to +30 Pa for 20 seconds or more) or 3 minutes When the time has elapsed, the control unit 18 outputs the filter processing control signal for performing the averaging filter processing to the second and third filters 12 and 13, and the first and second dead zone processing control signals for performing the correction dead zone processing. After output to the second exhaust damper control units 41 and 42, the first and second exhaust dampers 4 are output by the second order deviation control method based on the output signals of the second and third filters 12 and 13. Controls the first and second exhaust damper control units 16 and 17 to calculate the opening control amount of 42.

  Thereby, in the first exhaust damper control unit 16, the secondary deviation control is performed based on the output signal (measured value) of the second pressure gauge 52 in which the opening degree control amount is subjected to the averaging filter process by the second filter 12. The calculated opening degree control amount is output to the first exhaust damper 41 by the method. As a result, the opening degree of the first exhaust damper 41 can be changed so as to keep the chamber pressure in the first chamber at +30 Pa (target value) while suppressing the sensitive reaction (operation) of the first exhaust damper 41. . Similarly, in the second exhaust damper control unit 17, the secondary deviation control is performed based on the output signal (measured value) of the third pressure gauge 53 in which the opening degree control amount is subjected to the averaging filter process by the third filter 13. The opening degree control amount calculated by the method is output to the second exhaust damper 43. As a result, the opening degree of the second exhaust damper 42 can be changed so as to keep the chamber pressure in the second chamber at +20 Pa (target value) while suppressing the sensitive reaction (operation) of the second exhaust damper 42. .

  Thereafter, when the room pressures in the first and second rooms enter the stable range, the control unit 18 air-conditions the air conditioner control unit 14 so as to keep the static pressure in the supply passage 61 at +400 Pa (target value). The air volume of the machine 20 is controlled so that the first and second exhaust damper controllers 16 and 17 maintain the chamber pressures in the first and second rooms at +30 Pa (target value) and +20 Pa (target value). The opening degree of the first and second exhaust dampers 41 and 42 is controlled, and the air volume of the exhaust fan 70 is controlled so that the exhaust fan control unit 82 maintains the static pressure of the exhaust passage 62 at +400 Pa (target value). Let

Next, the operation of the room pressure control device 110 when the mode is shifted from the normal operation to the energy saving operation will be described.
At the time of mode transition, the control unit 18 outputs a filter process control signal that does not perform the averaging filter process to the first to fourth filters 11 to 13 and 81, and the correction dead band process that does not perform the correction dead band process. with a control signal and the air conditioner control unit 14 and the first and second exhaust damper control units 16 and 17 and outputs the exhaust fan control unit 82, a secondary deviation using a quadratic function characteristic with a larger gain factor K _p The air conditioner control unit 14, the first and second exhaust damper control units 16, 17 and the exhaust fan control unit 82 are controlled so as to calculate the air volume control amount and the opening degree control amount according to the control method.

  When the mode of the air conditioner 20 and the exhaust fan 70 is shifted from the normal operation to the energy saving operation, the control unit 18 changes the target value of the static pressure of the air supply passage 61 from +400 Pa to +200 Pa, and the first filter 11. The air conditioner control unit 14 is controlled so as to calculate the air volume control amount of the air conditioner 20 by the secondary deviation control method based on the output signal. As a result, the frequency of the input signal of the air conditioner inverter 21 is lowered in accordance with the calculated air flow control amount, so that the static pressure of the air supply passage 61 becomes +200 Pa (target value after change). The air volume is controlled. Further, the control unit 18 changes the target value of the static pressure of the exhaust passage 62 from +380 Pa to +180 Pa, and sets the air volume control amount of the exhaust fan 70 based on the output signal of the fourth filter 81 by the secondary deviation control method. The exhaust fan control unit 82 is controlled to calculate. As a result, the frequency of the input signal of the exhaust fan inverter 71 is lowered according to the calculated air flow control amount, and therefore the air flow of the exhaust fan 70 so that the static pressure of the exhaust passage 62 becomes +180 Pa (target value after change). Is controlled.

  At this time, the control unit 18 sends a control signal for stopping the control operation of the first and second constant air volume devices 31 and 32 so as not to operate the first and second constant air volume devices 31 and 32. Output to the control unit 15.

  Thereafter, when the static pressure of the supply passage 61 enters a stable region (that is, when the static pressure of the supply passage 61 enters the range of +190 Pa to +210 Pa for 20 seconds or more), the control unit 18 performs the first and second constants. In order to send air from the air volume devices 31 and 32 to the first and second rooms with a constant air volume and utilize it as an energy saving mode, a control signal for starting the control operation of the first and second constant air volume devices 31 and 32 is generated. Output to the constant air volume device control unit 14.

  Thereafter, the control unit 18 calculates the opening control amounts of the first and second exhaust dampers 41 and 42 by the secondary deviation control method based on the output signals of the second and third filters 12 and 13. The first and second exhaust damper control units 16 and 17 are controlled. As a result, the opening pressure of the first exhaust damper 41 is changed in accordance with the opening degree control amount calculated by the first exhaust damper control unit 16, so that the chamber pressure in the first room is maintained at +30 Pa (target value). At the same time, the opening degree of the second exhaust damper 42 is changed according to the opening degree control amount calculated by the second exhaust damper control unit 17, so that the chamber pressure in the second chamber becomes +20 Pa (target value). Kept.

  Thereafter, the static pressure of the air supply passage 61 enters the stable region, the static pressure of the exhaust passage 62 enters the stable region (that is, the static pressure of the exhaust passage 62 enters the range of +170 Pa to +190 Pa), and When the state in which the room pressure is in the stable region (+25 Pa to +35 Pa) and the room pressure in the second room is in the stable region (+15 Pa to +25 Pa) continues for 5 minutes or more, the control unit 18 starts from the normal operation described above. The air conditioner control unit 14, the first and second exhaust damper control units 16 and 17, and the exhaust fan control unit 82 are controlled so as to end the operation at the time of mode transition to the energy saving operation.

  Next, the operation of the room pressure control device 110 when the mode is shifted from the energy saving operation to the normal operation will be described.

  When the mode of the air conditioner 20 and the exhaust fan 70 is shifted from the energy-saving operation to the normal operation, the control unit 18 changes the target value of the static pressure of the air supply passage 61 from +200 Pa to +400 Pa to change the first filter 11. The air conditioner control unit 14 is controlled so as to calculate the air volume control amount of the air conditioner 20 by the secondary deviation control method based on the output signal. As a result, the frequency of the input signal of the air conditioner inverter 21 is increased according to the calculated air volume control amount, and therefore the air volume of the air conditioner 20 so that the static pressure of the air supply passage 61 becomes +400 Pa (target value after change). Is controlled. Further, the control unit 18 changes the target value of the static pressure of the exhaust passage 62 from +180 Pa to +380 Pa, and sets the air volume control amount of the exhaust fan 70 based on the output signal of the fourth filter 81 by the secondary deviation control method. The exhaust fan control unit 82 is controlled to calculate. As a result, the frequency of the input signal of the exhaust fan inverter 71 is increased according to the calculated air flow control amount, so that the air flow of the exhaust fan 70 is adjusted so that the static pressure of the exhaust passage 62 becomes +380 Pa (target value after change). Be controlled.

  At this time, contrary to the above-described mode transition from the normal operation to the energy operation, the control unit 18 supplies the first and second air from the first and second constant air volume devices 31 and 32 with a constant air volume. In order to send to the room, a control signal for starting the control operation of the first and second constant air volume devices 31 and 32 is output to the constant air volume device controller 15.

  Further, the control unit 18 calculates the opening control amounts of the first and second exhaust dampers 41 and 42 by the secondary deviation control method based on the output signals of the second and third filters 12 and 13. The first and second exhaust damper control units 16 and 17 are controlled. As a result, the opening pressure of the first exhaust damper 41 is changed in accordance with the opening degree control amount calculated by the first exhaust damper control unit 16, so that the chamber pressure in the first room is maintained at +30 Pa (target value). At the same time, the opening degree of the second exhaust damper 42 is changed according to the opening degree control amount calculated by the second exhaust damper control unit 17, so that the chamber pressure in the second chamber becomes +20 Pa (target value). Kept.

  Thereafter, the static pressure of the supply passage 61 enters a stable region (+390 Pa to +410 Pa), the static pressure of the exhaust passage 62 enters a stable region (+370 Pa to +390 Pa), and the room pressure of the first room is stable (+25 Pa to +25 Pa). +35 Pa) and the state in which the chamber pressure in the second room is in the stable range (+15 Pa to +25 Pa) continues for more than 5 minutes, the control unit 18 performs the operation at the time of mode transition from the energy saving operation to the normal operation. The air conditioner control unit 14, the first and second exhaust damper control units 16 and 17, and the exhaust fan control unit 82 are controlled so as to end.

Next, a room pressure control apparatus 210 according to a third embodiment of the present invention will be described with reference to FIG.
As shown in FIG. 12, the room pressure control device 210 according to the present embodiment has a local exhaust switch 93 turned on in the return type air conditioning facility shown in FIG. This is used when controlling the difference between the chamber pressures of the first and second rooms to 10 Pa (30 Pa-20 Pa) when the first chamber is exhausted by the exhaust device 90.

  The room pressure control apparatus 210 according to this embodiment is different from the room pressure control apparatus 10 according to the first embodiment shown in FIG. 2 in that the output signal of the switch 93 is input to the control unit 18.

  When the local exhaust switch 93 provided in the first room is turned on, the exhaust fan 91 of the local exhaust device 90 starts operating and the local exhaust damper 92 is fully opened. The room pressure in the room drops. Therefore, the control unit 18 outputs a filter processing control signal that does not perform the averaging filter processing to the first to fourth filters 11 to 13 and 81 and does not perform the correction dead zone processing in order to improve followability. The corrected dead zone processing control signal is output to the air conditioner control unit 14, the first and second exhaust damper control units 16, 17, and the exhaust fan control unit 82, and then the second order deviation based on the output signal of the second filter 12. The opening control amount of the first exhaust damper 41 is output by the control method. Further, according to the output signal of the switch 93, the control unit 18 changes the target value of the room pressure of the second room from +20 Pa, and the difference between the room pressure of the first room and the room pressure of the second room becomes 10 Pa. The second target value is obtained by subtracting the value and calculating the opening control amount of the second exhaust damper 42 by the secondary deviation control method based on the output signal of the second filter 12. The exhaust damper control unit 17 is controlled.

  After that, when 60 seconds elapse, the control unit 18 returns the target value of the second chamber pressure from the new target value to +20 Pa before the change, and based on the output signal of the third filter 13, the second order. The second exhaust damper control unit 17 is controlled so as to calculate the opening degree control amount of the second exhaust damper 42 by the deviation control method.

  After that, when the switch 93 is turned off, the exhaust fan 91 of the local exhaust device 90 stops operating and the local exhaust damper 92 is closed, so that the chamber pressure in the first room increases. Therefore, the control unit 18 controls the first exhaust damper control unit 16 to open the opening degree of the first damper 41 according to the output signal of the switch 93, and sets the target value of the chamber pressure in the second room. Based on the output signal of the second filter 12, the value is changed from +20 Pa to a new target value obtained by subtracting the value at which the difference between the room pressure in the first room and the room pressure in the second room is 10 Pa. Then, the second exhaust damper control unit 17 is controlled so as to calculate the opening degree control amount of the second exhaust damper 42 by the secondary deviation control method.

  After that, when 60 seconds elapse, the control unit 18 returns the target value of the second chamber pressure from the new target value to +20 Pa before the change, and based on the output signal of the third filter 13, the second order. The second exhaust damper control unit 17 is controlled so as to calculate the opening degree control amount of the second exhaust damper 42 by the deviation control method.

  Note that the above-described control method during operation of the local exhaust device can also be applied to the all fresh air conditioning equipment shown in FIG.

  In the above description, the case where the chamber pressures of the two rooms (first and second rooms) are maintained at the target values (set values) has been described. However, the room pressure control device according to the present invention can be used for three or more rooms. The present invention can also be applied to the case where the chamber pressure is kept at a target value (set value).

It is a figure for demonstrating the return type air conditioner using the room pressure control apparatus by the 1st Example of this invention. It is a block diagram which shows the structure of the room pressure control apparatus by 1st Example of this invention. It is a figure for demonstrating the averaging filter process. It is a figure which shows an example of the quadratic function characteristic used in a secondary deviation control system. It is a figure which shows the comparison with the secondary deviation control system and PID control system regarding followability. It is a figure which shows the comparison with the secondary deviation control system regarding a stability, and a PID control system. It is a figure which shows the characteristic of the quadratic function characteristic used in a secondary deviation control system. It is a figure which shows the calculation block diagram of a secondary deviation control system. It is a figure for demonstrating a correction dead zone process. It is a figure for demonstrating the all fresh type air-conditioning installation using the room pressure control apparatus by the 2nd Example of this invention. It is a block diagram which shows the structure of the room pressure control apparatus by the 2nd Example of this invention. It is a figure for demonstrating the return type | formula air conditioner using the room pressure control apparatus by the 3rd Example of this invention.

Explanation of symbols

10, 110, 210 Room pressure control devices 11-13 First to third filters 14 Air conditioner control unit 15 Constant air volume device control units 16, 17 First and second exhaust damper control units 18 Control unit 20 Air conditioner 21 Air conditioner inverters 31 and 32 First and second constant air volume devices 41 and 42 First and second exhaust dampers 51 to 53 First to third pressure gauges 61 Air supply passage 62 Exhaust passage 70 Exhaust fan 71 Exhaust Inverter for fan 72 Fourth pressure gauge 81 Fourth filter 82 Exhaust fan controller 90 Local exhaust device 91 Exhaust fan 92 Local exhaust damper 93 Switch

Claims (7)

A room pressure control device for controlling a room pressure of a room connected to an air conditioner through a supply passage to a target value,
A quadratic function characteristic from a first deviation value between a measured value of the static pressure of the supply passage measured by a first pressure gauge provided in the supply passage and a target value of the static pressure of the supply passage. An air conditioner control unit for obtaining an air volume control amount of the air conditioner based on
Based on a quadratic function characteristic from a second deviation value between a measured value of the room pressure of the room measured by a second pressure gauge provided in the room and a target value of the room pressure of the room, the room An exhaust damper control unit for obtaining an opening control amount of the exhaust damper for exhausting the air inside,
A room pressure control device comprising: A first filter that performs an averaging filter process on an output signal of the first pressure gauge;
A second filter that performs an averaging filter process on the output signal of the second pressure gauge;
Further comprising
From the third deviation value between the measured value of the static pressure of the supply passage and the target value of the static pressure of the supply passage that has been subjected to the averaging filter process by the first filter. Obtain the air volume control amount of the air conditioner based on the quadratic function characteristics,
The exhaust damper control unit determines the exhaust damper from a fourth deviation value between a measured value of the room pressure of the room subjected to the averaging filter process by the second filter and a target value of the room pressure of the room. Find the opening control amount,
The room pressure control device according to claim 1, wherein: The air conditioner control unit performs a correction dead zone process for setting a correction dead zone for both the first or third deviation value and time, and obtains an air volume control amount of the air conditioner.
The exhaust damper control unit performs a correction dead zone process for setting a correction dead zone for both the second or fourth deviation value and time, and obtains an opening control amount of the exhaust damper.
The room pressure control device according to claim 1 or 2, characterized by the above.   A measured value of the static pressure of the exhaust passage measured by another pressure gauge provided in an exhaust passage between the exhaust fan for exhausting air from the room and the room, and a target value of the static pressure of the exhaust passage. The room pressure control according to any one of claims 1 to 3, further comprising an exhaust fan control unit that obtains an air flow control amount of the exhaust fan based on a quadratic function characteristic from the fifth deviation value. apparatus. Further comprising another filter that performs an averaging filter process on the output signal of the other pressure gauge;
The exhaust fan control unit obtains a quadratic function from a sixth deviation value between the measured value of the static pressure of the exhaust passage and the target value of the static pressure of the exhaust passage subjected to the averaging filter process by the other filter. Obtaining an air volume control amount of the exhaust fan based on characteristics;
The room pressure control device according to claim 4, wherein:   5. The exhaust fan control unit performs correction dead zone processing for setting a correction dead zone for both the fifth or sixth deviation value and time, and obtains an air volume control amount of the exhaust fan. Or the chamber pressure control apparatus of 5.   When the local exhaust switch provided in the room is turned on, the other room measured by another pressure gauge provided in the other room whose room pressure is controlled by the room pressure control device. Based on the quadratic function characteristic, the air in the other room is exhausted from the deviation value between the measured value of the room pressure and the target value changed by subtracting a predetermined value from the target value of the room pressure in the other room. The room pressure control device according to claim 1, further comprising another exhaust damper control unit that obtains an opening degree control amount of another exhaust damper for the purpose.

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