JP2006170547A - Control method and control device for air conditioning system, and air conditioning system - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To develop a control method, a control device, and an air conditioning system controlling an operation state of a pump of the air conditioning system having a high energy saving effect by a simple control means not needing any advanced hardware or software used as a control means for controlling the operation state of the pump in the air conditioning system. <P>SOLUTION: The control method and control device for the air conditioning system, and the air conditioning system has the control means for controlling a rotational frequency of the primary pump so as to provide a constant outlet temperature of a cold/hot water generator, and controlling a secondary pump so as to provide a constant outlet temperature of a heat exchanger. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to an air conditioning system control method, an air conditioning system control device, an air conditioning system controlled by the control method, and an air conditioning system including the control device.

  More specifically, an air conditioning system characterized by controlling the rotational speed of the secondary pump so that the temperature of the flowing water that has passed through the heat exchanger is kept constant according to the temperature information of the flowing water that has passed through the heat exchanger. The present invention relates to a control method, a control device for an air conditioning system, an air conditioning system controlled by the control method, and an air conditioning system having the control device.

  Further, in addition to the above control method and control device of the air conditioning system and the air conditioning system, the temperature information of the flowing water that has passed through the cold / hot water generator 1 is used to keep the temperature of the flowing water that has passed through the cold / hot water generator constant. The present invention relates to an air conditioning system control method, an air conditioning system control device, an air conditioning system controlled by the control method, and an air conditioning system having the control device.

  A circuit diagram of a very general case of a conventional air conditioning system is shown in FIG. The air conditioning system acu of FIG. 6 includes a return header CHR, two primary pumps Po11, Po12, two cold / hot water generators R1, R2, a feed header CH1, a bypass path BP1 from the feed header CH1 to the return header CHR, Secondary heat pump Po21 to which inverter Inv21 is added, secondary pump Po22 to which inverter Inv22 is added, feed header CH2, bypass passage BP2 from feed header CH2 having relief valve B to feed header CH1, and two heat exchangers F1, F2, two-way valves b1, b2, expansion tank EXT as basic components, and further, as a control system, flowmeters Q, 2 for measuring the flow rate of running water that has passed through heat exchangers F1, F2 It is comprised from the pressure gauge P which measures the discharge pressure of the flowing water which passed the next pumps Po21 and Po22, and the controller ctu. The controller ctu receives the flow information from the flow meter Q and controls the operation state of the secondary pumps Po21 and Po22 via the inverters Inv21 and Inv22, and receives the pressure information from the pressure gauge P and releases the relief valve. It has two control functions of adjusting the opening degree of B.

  The operation of the air conditioning system acu is as follows. That is, the water flow recirculated from the return header CHR is divided into two strips and sucked into the primary pumps Po11 and Po12. The water flow pressurized by the primary pumps Po11 and Po12 is led to the cold / hot water generators R1 and R2, where it is cooled or heated, and then led to the feed header CH1. The feed header CH1 and the return header CHR are connected by the bypass path BP1, and the excess water generated in the primary pumps Po11 and Po12 is returned to the return header CHR through the bypass path BP1.

  The water flow is sucked from the feed header CH1 to the secondary pumps Po21 and Po22 and guided to the feed header CH2. Note that a bypass BP2 is provided between the feed header CH1 and the feed header CH2, and an excess amount of water is recirculated from the feed header CH2 to the feed header CH1. A relief valve B is provided in the bypass passage BP2.

  The running water fed from the feed header CH2 is divided into two strips and led to the heat exchangers F1 and F2, where heat exchange with the air is performed to cool or heat the air. Flowing water cooled or heated by heat exchange with air passes through the two-way valves b1 and b2 and is returned to the return header CHR. Note that EXT is an expansion tank that releases excess water when the flowing water is returned to the return header CHR. The two-way valves b1 and b2 are controlled by a control device (not shown) to control the amount of water passing through the heat exchangers F1 and F2, but this control is out of the main part of the present invention. Will be omitted.

  Such an air conditioning system acu is usually provided with a controller ctu that controls the operating state of the secondary pumps Po21 and Po22 by setting the pressure of the feed header CH2. The feed header CH2 is provided with a pressure gauge P, which constantly monitors the discharge pressures of the secondary pumps Po21 and Po22 and transmits pressure information to the controller ctu. A pressure setter (not shown) is provided in the controller ctu. When the water pressure in the feed header CH2 exceeds the set value, the valve opening degree of the relief valve B provided in the bypass passage BP2 is sent. It adjusts according to the water pressure of the header CH2, and the excess water amount in the feed header CH2 is released to the feed header CH1.

  A flow meter Q is installed in the preceding stage of the return header CHR to constantly monitor the flow rate of the water flow returned to the return header CHR, and the flow rate information is transmitted to the controller ctu. Inside the controller ctu, there is provided a start / stop instruction device (not shown) for starting and stopping the secondary pumps Po21, Po22, and 2 according to the increase or decrease of the flow rate of the water flow returned to the return header CHR. The operation states (start / stop and rotation speed) of the next pumps Po21 and Po22 are controlled. Similarly, although not shown in the figure, the flow meter Q is also responsible for setting the number of operating water heaters R1 and R2.

  By such a mechanism, the water pressure of the feed header CH2 is stabilized, and the operating states (start / stop and rotation speed) of the secondary pumps Po21 and Po22 are determined according to the amount of water returned to the return header CHR. By controlling the operation state (start and stop and rotation speed) of the secondary pumps Po21 and Po22 according to the amount of water passing through the heat exchangers F1 and F2, the amount of excess water sent to the heat exchangers F1 and F2 is reduced. Therefore, a certain amount of energy saving effect is also achieved in this conventional air conditioning system ctu.

  In the circuit of FIG. 6, if the change of the water pressure of each part is illustrated, it will be as FIG. 4, FIG. 5 (graph of a comparative example). 4 represents the change in water pressure at the basic flow rate, and FIG. 5 represents the change in water pressure when the flow rate is reduced. The basic flow rate is a flow rate required when the heat exchangers F1 and F2 operate with a capacity of 100%, and the time when the flow rate is reduced means a case where the flow rate is lower than the basic flow rate.

In the above-described conventional technology, some parts where energy is wasted can be pointed out. First, since the primary pumps Po11 and Po12 are always operated at a constant set water pressure, when the load required by the heat exchangers F1 and F2 is low, the amount of water exceeding the required amount of water must be supplied. I won't. Therefore, power is wasted in the primary pumps Po11 and Po12 in this portion. Since the power consumption of the pump is proportional to the cube of the flow rate, when the load required by the heat exchangers F1 and F2 is high, the power consumed wastefully is still small, but the load required by the heat exchangers F1 and F2 is small. If it becomes low, the power consumed wastefully will become enormous.

Next, in the above situation, when the heat exchangers F1 and F2 require a water amount equal to or lower than the water amount corresponding to the minimum rotation speed of the inverters Inv21 and Inv22 on the secondary pump side, the water pressure of the feed header CH2 is set from the set value. Therefore, the surplus water amount must be released from the sending header CH2 to the sending header CH1. Therefore, power is wasted even in the secondary pumps Po21 and Po22.

  Among the above-mentioned points, the present situation is that no energy saving measures are taken for the energy that is wasted in the primary pumps Po11 and Po12. On the other hand, energy saving measures against energy consumed in the secondary pumps Po21 and Po22 are performed in various forms. The “air conditioning system” disclosed in Patent Document 1 below is one example. is there.

  The “air conditioning system” of Patent Document 1 below includes an opening signal of a two-way valve provided in the front stage of a plurality of heat exchangers, and a differential pressure sensor (pressure gauge) provided in the rear stage of the plurality of secondary pumps. It has an input / output calculation unit for controlling the rotation speed of the inverter added to each of the plurality of secondary pumps according to the measured values, and thereby the output (rotation speed) of the plurality of secondary pumps is a load. It can be suppressed to the minimum output required by the heat exchanger, and it is said that significant energy saving is possible in this part.

  However, the above input / output calculation unit requires a CPU having an advanced information processing capability similar to that of a computer CPU, and dedicated control software is required to operate the input / output calculation unit. Furthermore, personnel who have specialized information processing technology are indispensable to make adjustments so that the input / output calculation unit can be incorporated into the air conditioning system, and a normal air conditioning system engineer incorporates the input / output calculation unit. Therefore, it must be said that there is a great difficulty in realizing the “air conditioning system” of the following Patent Document 1.

  Although many of those skilled in the art recognize that the “air conditioning system” of the following Patent Document 1 has a remarkable energy saving effect as compared with the prior art, the “Air conditioning system” of the following Patent Document 1 is nevertheless recognized. As mentioned above, the reason why the company has not spread widely is that it requires advanced hardware and software and personnel who can handle them. However, it can be said that the current situation is that the company has taken the second step from the point of view of cost effectiveness.

From the viewpoint of technical contents, the “air conditioning system” of Patent Document 1 below has a considerable energy saving effect on the secondary pump side, but is different from the conventional technique on the primary pump side. However, the fact that no energy-saving measures are considered in this part remains as a problem to be solved.
Japanese Patent Laid-Open No. 2002-213802 Yamatake Co., Ltd. “Easy automatic control chapter 4 PID control”, [online], September 1, 2004, Yamatake Co., Ltd. [search September 16, 2004], Internet <URL: http //www.compoclub.com/jidou-seigyo/jidou-seigyo4.html>

  An air conditioner having a primary pump, a cold / hot water generator placed downstream of the primary pump, a secondary pump placed downstream of the cold / hot water generator, and a heat exchanger placed downstream of the secondary pump In the system, advanced hardware and software and personnel who can handle them with simple control means that do not require any advanced hardware and software and personnel who can handle them as control means to control the operating state of the secondary pump A control method and control apparatus for an air conditioning system having an energy saving effect equivalent to or higher than that of a control means that requires the above.

  Further, in addition to solving the above-mentioned problems, energy saving on the primary pump side, which has not been considered so far, can be realized. Specifically, on the primary pump side, the water flow once pressurized by the primary pump was passed through a cold / hot water generator, and the surplus water amount was released through the bypass passage. The control method and control device of the air conditioning system with the configuration that can control the rotation speed of the primary pump so that only the minimum amount of water required by the cold / hot water generator can be sent from the beginning are combined. Develop.

The present invention has been made to solve the above-described problems, and provides means for solving the problems described below.
<Solution 1>
It comprises a primary pump, a cold / hot water generator placed downstream of the primary pump, a secondary pump placed downstream of the cold / hot water generator, and a heat exchanger placed downstream of the secondary pump. In the air conditioning system
Control means for controlling the rotational speed of the secondary pump;
Having temperature measuring means for measuring the temperature of running water that has passed through the heat exchanger;
A control method for an air conditioning system, wherein the rotational speed of a secondary pump is controlled so that the temperature of running water that has passed through a heat exchanger is kept constant based on temperature information from the temperature measuring means.
<Solution 2>
An air conditioning system controlled by the method for controlling an air conditioning system according to Solution 1.
<Solution 3>
It comprises a primary pump, a cold / hot water generator placed downstream of the primary pump, a secondary pump placed downstream of the cold / hot water generator, and a heat exchanger placed downstream of the secondary pump. In the air conditioning system
Control means for controlling the rotational speed of the secondary pump;
Having temperature measuring means for measuring the temperature of running water that has passed through the heat exchanger;
A control device for an air conditioning system, wherein the number of revolutions of the secondary pump is controlled so that the temperature of running water that has passed through the heat exchanger is kept constant based on temperature information from the temperature measuring means.
<Solution 4>
4. The air conditioning system control device according to claim 3, wherein the temperature measuring means of the air conditioning system is a temperature sensor, and the control means is a temperature setter and an inverter using a PID (calculus) control method.
<Solution 5>
An air conditioning system comprising the control device for an air conditioning system according to Solution 3 or Solution 4.
<Solution 6>
Control means for controlling the rotational speed of the primary pump;
Having temperature measuring means for measuring the temperature of running water that has passed through the cold / hot water generator;
The air conditioning system according to Solution 1, wherein the rotational speed of the primary pump is controlled so that the temperature of the flowing water that has passed through the cold / hot water generator is kept constant based on temperature information from the temperature measuring means. Control method.
<Solution 7>
An air conditioning system controlled by the method for controlling an air conditioning system according to claim 6.
<Solution 8>
Control means for controlling the rotational speed of the primary pump;
Having temperature measuring means for measuring the temperature of running water that has passed through the cold / hot water generator;
The air conditioning system according to Solution 3, wherein the rotational speed of the primary pump is controlled so that the temperature of the flowing water that has passed through the cold / hot water generator is kept constant based on temperature information from the temperature measuring means. Control device.
<Solution 9>
9. The air conditioning system control device according to claim 8, wherein the temperature measuring means of the air conditioning system is a temperature sensor, and the control device is a temperature setter and an inverter using a PID (calculus) control method.
<Solution 10>
An air conditioning system comprising the control device for an air conditioning system according to claim 8 or 9.

In the inventions described in Solution 1 to Solution 3 and Solution 5 of the present invention,
It comprises a primary pump, a cold / hot water generator placed downstream of the primary pump, a secondary pump placed downstream of the cold / hot water generator, and a heat exchanger placed downstream of the secondary pump. In the air conditioning system
Control means for controlling the rotational speed of the secondary pump;
Having temperature measuring means for measuring the temperature of running water that has passed through the heat exchanger;
A control method and control apparatus for an air conditioning system, wherein the rotational speed of the secondary pump is controlled so that the temperature of the flowing water that has passed through the heat exchanger is kept constant based on temperature information from the temperature measuring means, and Since an air conditioning system having the control device is realized,
As a control means for controlling the operation state of the secondary pump, advanced hardware, software and simple personnel that do not require any personnel capable of handling them are required, and advanced hardware, software and personnel capable of handling them are required. It is possible to realize an air conditioning system control method and control device having an energy saving effect equal to or higher than that of the control means, and an air conditioning system including the control device.
The cost required for installation and maintenance is far lower than that of control means that requires sophisticated hardware and software and personnel who can handle them, and has been hesitant to introduce expensive energy-saving systems. It can now be easily installed at business sites without a heavy burden.

In the invention described in Solution 4 and Solution 5 of the present invention,
Since the temperature measuring means of the air conditioning system is a temperature sensor and the control means is a temperature setter and inverter using a PID (calculus) control method,
The circuit configuration is extremely simple and simple, does not use any advanced hardware and software, and can be installed, adjusted and operated by any engineer who can handle ordinary air conditioning equipment. Further, since the circuit configuration is extremely simple and simple, the entire circuit is very stable, there are few failures, and maintenance is not required. In addition, the cost required for introduction is extremely low, and it is possible to achieve a large cost-effectiveness even in small and medium-sized offices.

In the inventions described in Solution 6 to 8 and Solution 10 of the present invention,
In addition to the inventions described in Solution 1 to 3 and Solution 5,
Control means for controlling the rotational speed of the primary pump;
Having temperature measuring means for measuring the temperature of running water that has passed through the cold / hot water generator;
A control method and control apparatus for an air-conditioning system, characterized in that, based on temperature information from the temperature measuring means, the rotational speed of the primary pump is controlled so that the temperature of the flowing water that has passed through the cold / hot water generator is kept constant. And an air conditioning system having the control device is realized,
In addition to energy saving on the secondary pump side, energy saving on the primary pump side was also realized.

Specifically, until now, on the primary pump side, the water flow once pressurized by the primary pump has been passed through the cold / hot water generator, and the excess water amount has been released through the bypass passage. The structure that must be wasted has been changed, and from the beginning, the rotation speed of the primary pump can be controlled so that only the minimum amount of water and water pressure required for the cold / hot water generator can be fed. The energy saving effect of the air conditioning system as a whole has become even greater.
In other words, the primary pump and the secondary pump are connected, and the necessary water head for the entire pipeline is supplied without waste by the two pumps of the primary pump and the secondary pump. Can be achieved.

Moreover, since the control means for controlling the operating state of the primary pump is a simple control means that does not require any advanced hardware, software, and personnel who can handle them, as with the secondary pump, the cost required for introduction and maintenance. However, it is much cheaper than control methods that require advanced hardware and software and personnel who can handle them, and it is a heavy burden even for small and medium-sized offices that have been hesitant to introduce expensive energy-saving systems. It can be easily installed without feeling.

In the invention described in Solution 9 and Solution 10 of the present invention,
Since the temperature measuring means of the air conditioning system is a temperature sensor, and the control means is a temperature setter and inverter using a PID (calculus) control system, the circuit configuration is extremely simple and simple, and advanced hardware It can be installed, adjusted, and operated by any engineer who can handle ordinary air conditioning equipment without using any software. Further, since the circuit configuration is extremely simple and simple, the entire circuit is very stable, there are few failures, and maintenance is not required. In addition, the cost required for introduction is extremely low, and it is possible to achieve a large cost-effectiveness even in small and medium-sized offices.

  The best mode for carrying out the invention will be described below in detail with reference to the drawings. 1st Example described below is one Example of the control method, control apparatus, and air conditioning system of an air conditioning system as described in the solution means 6-10 of this invention.

<Configuration of Example 1>
FIG. 1 is a circuit diagram of an air conditioning system ACU according to the first embodiment. In the air conditioning system ACU, the same reference numerals are used for components common to the air conditioning system acu in FIG.

The air conditioning system ACU has a return header CHR, primary pumps Po11 and Po12, two cold / hot water generators R1 and R2, a feed header CH1, a bypass BP1 from the feed header CH1 to the return header CHR, and an inverter Inv21. Secondary pump Po21, secondary pump Po22 to which inverter Inv22 is added, feed header CH2, bypass passage BP2 from feed header CH2 having relief valve B to feed header CH1, two heat exchangers F1, F2, and two-way The basic components such as the valves b1 and b2 and the expansion tank EXT are the same as those of the air conditioning system acu (see FIG. 6), and the flow meter Q for measuring the flow rate of the flowing water that has passed through the heat exchangers F1 and F2 and the secondary The pressure gauge P that measures the discharge pressure of the flowing water that has passed through the pumps Po21 and Po22, and the controller ctu are also air conditioning systems. A is common with cu (see FIG. 6). Note that the two-way valves b1 and b2 provided at the subsequent stage of the heat exchangers F1 and F2 are not directly related to the gist of the present invention, as in the case of the air conditioning system acu (see FIG. 6).

The difference from the air conditioning system acu (see FIG. 6) on the primary pump side is as follows. That is, the bypass BP1 is provided with a relief valve B1, which is a two-way valve, and the feed header CH1 is provided with a pressure gauge P1. Further, an inverter Inv11 is added to the primary pump Po11, and an inverter Inv12 is added to the primary pump Po12, respectively, a temperature sensor Th11 is provided downstream of the cold / hot water generator R1, and a temperature sensor is provided downstream of the cold / hot water generator R2. Th12 is provided respectively.

Next, the difference from the air conditioning system acu (see FIG. 6) on the secondary pump side is as follows. That is, the temperature sensor 21 is provided before the return header CHR, and the temperature sensor 22 is provided after the feed header CH2.

Further, in the control system, a controller CTU is newly provided in addition to the controller ctu. The detailed configuration of the controller CTU is as shown in FIG. That is, the controller CTU includes a primary pump side controller C1 and a secondary pump side controller C2. The primary pump side controller C1 includes a pressure setter C11 and a temperature setter C12. Both the pressure setter C11 and the temperature setter C12 are PID (calculus) controllers. The PID controller is a PID auto-tuning small digital indicating controller. PID is an abbreviation of “calculus proportionality” (P: proportional, I: integral, D: derivative), and PID control is a P action (Proportional Action) that outputs an output proportional to the deviation between the current value and the set value. The sum of an I action (Integral Action) that produces an output proportional to the integral of the deviation and a D action (DerivativeAction) that produces an output proportional to the differential of the deviation is output and controlled toward the target value (for details) , See Non-Patent Document 1).

The pressure gauge P1 constantly monitors the water pressure in the feed header CH1, and the pressure information of the pressure gauge P1 is sent to the pressure setter C11. On the other hand, the relief valve B1 is normally closed in a normal operation state, and only when the water pressure in the feed header CH1 exceeds the set value, a valve opening command is sent from the pressure setter C11 to the relief valve B1, and the relief valve B1 is open. As a result, the surplus water amount is returned from the feed header CH1 to the return header CHR through the bypass BP1, and when the water pressure in the feed header CH1 falls below the set value, a valve closing command is sent from the pressure setter C11 to the relief valve B1. The valve B1 is configured to be in a closed state.

The temperature sensor Th11 constantly monitors the temperature of the flowing water that has passed through the cold / hot water generator R1, and the temperature information of the temperature sensor Th11 is sent to the temperature setter C12. The temperature setter C12 generates a frequency signal for changing the rotational speed of the primary pump Po11 so that the temperature of the temperature sensor Th11 is always kept constant based on a minute change in temperature information of the temperature sensor Th11. It is configured to transmit to the inverter Inv11 of Po11.

The temperature sensor Th12 constantly monitors the temperature of the flowing water that has passed through the cold / hot water generator R2, and the temperature information of the temperature sensor Th12 is sent to the temperature setter C12. The temperature setter C12 generates a frequency signal for changing the rotational speed of the primary pump Po12 so that the temperature of the temperature sensor Th12 is always kept constant based on a minute change in the temperature information of the temperature sensor Th12. It is configured to transmit to the inverter Inv12 of Po12.

  The secondary pump side controller C2 is a temperature setter C21, and the temperature setter C21 is a PID (calculus) controller. The temperature sensor Th21 constantly monitors the temperature of the flowing water that has passed through the heat exchangers F1 and F2, and the temperature information of the temperature sensor Th21 is sent to the temperature setting device C21. The temperature setter C21 outputs 2 frequency signals for changing the rotational speeds of the secondary pumps Po21 and Po22 so that the temperature of the temperature sensor Th21 is always kept constant based on a minute change in the temperature information of the temperature sensor Th21. Transmission is performed to the inverter Inv21 of the secondary pump Po21 and the inverter Inv22 of the secondary pump Po22.

  The temperature sensor Th22 complements the function of the temperature sensor Th21 and is provided to stabilize the control. The temperature sensor Th22 constantly monitors the temperature of the water flow that has passed through the secondary pumps Po21 and Po22, and temperature information of the temperature sensor Th22 is provided. Is sent to the temperature setter C21. The temperature sensor Th22 is effective to some extent in the configuration of the first embodiment, but is not essential. However, in the configuration where the control mechanism is not provided on the primary pump side (solution means 1 to 5), it is greatly useful for accurately adjusting the rotation speed of the secondary pumps Po21 and Po22 by the temperature sensor Th21 and the temperature setting device C21. (This point will be described later in detail).

  The controller ctu has substantially the same configuration as the controller ctu shown in FIG. 6, but there are some differences. That is, the controller ctu is provided with a start / stop instruction device c2 that controls only the start and stop of the secondary pumps Po21 and Po22 (the controller ctu shown in FIG. 6 also performs rotation speed control). The start / stop instruction device c2 operates two secondary pumps Po21 and Po22 in accordance with the flow rate of the water flow returned to the return header CHR monitored by the flow meter Q provided in the preceding stage of the return header CHR. It is determined whether to operate only one unit, and an instruction signal for starting and stopping the secondary pumps Po21 and Po22 is transmitted to the inverters Inv21 and Inv22. The inverters Inv21 and Inv22 control the operation / stop of the secondary pumps Po21 and Po22 based on the instruction signal.

  Further, the controller ctu is configured to transmit pressure information on the discharge pressures of the secondary pumps Po21 and Po22 that are constantly monitored by the pressure gauge P provided in the feed header CH2 to the pressure setting device c1 in the controller ctu. ing. A signal that opens the relief valve B from the pressure setting device c1 of the controller ctu only when the relief valve B provided in the bypass BP2 is normally closed and the pressure information of the pressure gauge P indicates abnormal pressure. Is sent to the relief valve B, and the relief valve B is opened to send an excess amount of water to the header CH1.

  Regarding the control system of the air conditioning system ACU, as shown in FIG. 2, the primary pump side control system centered on the primary pump side controller C1 and the secondary pump side centered on the secondary pump side controller C1. Largely divided into control systems. Further, the configuration corresponding to the “control device” described in the solving means 3 in FIG. 2 is a secondary pump side controller C2, inverters Inv21, Inv22, and a temperature sensor Th21. Further, the configuration corresponding to the “control device” described in the solving means 6 is a temperature setter C12, inverters Inv11 and Inv12, and temperature sensors Th11 and Th12.

<Operation of Example 1>
The operation of the air conditioning system ACU is as follows (see FIGS. 1 and 2). First, the operation on the primary pump side will be described. The water flow returned from the return header CHR is divided into two strips and sucked into the primary pumps Po11 and Po12. The water flow pressurized by the primary pumps Po11 and Po12 is led to the cold / hot water generators R1 and R2, where it is cooled or heated, and then led to the feed header CH1. The feed header CH1 and the return header CHR are connected by a bypass BP1, but the relief valve B1 provided in the bypass BP1 is normally closed in a normal operation state, and the water pressure of the feed header CH1 is secondary. Only when the minimum required water pressure on the pump side is exceeded, the relief valve B1 is opened and the surplus water amount is returned to the return header CHR through the bypass BP1. This point will be described in detail later.

  The temperature sensor Th11 provided in the subsequent stage of the cold / hot water generator R1 constantly monitors the water temperature of the water flow that has passed through the cold / hot water generator R1, and the temperature information of the water temperature is always the temperature in the primary pump controller C1. A frequency signal that determines the rotational speed of the primary pump Po11 is transmitted from the temperature setter C12 to the inverter Inv11. When the detected temperature of the temperature sensor Th11 deviates from the set value, the temperature setter C12 sends a frequency signal for adjusting the rotation speed of the primary pump Po11 to the inverter Inv11 so that the detected temperature of the temperature sensor Th11 is returned to the set value. The rotation speed of the primary pump Po11 is adjusted so that the temperature detected by the temperature sensor Th11 is returned to the set value. In this way, the water temperature discharged from the cold / hot water generator R1 is kept constant.

  The temperature sensor Th12, the temperature setting device C12, the inverter Inv12, the primary pump Po12, and the cold / hot water generator R2 have the same operation as described above, and as a result, the temperature sensor Th12 passes through the cold / hot water generator R2 by the temperature signal of the temperature sensor Th12. The temperature of the running water is kept constant.

  That is, the idea is to manage the flow rate so that the outlet temperature of the cold / hot water generators R1, R2 is fixed to a set value, and the inverters Inv11, Inv12 having the minimum required water amount of the cold / hot water generators R1, R2 as the lower limit. The basic operation is a flow rate fluctuation operation in which the frequency is set as a basic set value and the flow rates of the primary pumps Po11 and Po12 are changed according to the fluctuation of the suction head in the feed header CH1 accompanying the flow rate fluctuation of the secondary pumps Po21 and Po22 in the subsequent stage.

The above operation will be described in detail as follows. That is, q is represented by the following equation, where q is the energy requirement of the water flow flowing through the circuit, Q is the amount of water, and Δt is the temperature change.
q = a × Q × Δt (Formula 1)
However, in this case,
a is a constant,
q is the minimum required energy required by the secondary pump side,
Q is the amount of water flowing through the cold / hot water generators R1, R2,
Δt is a temperature difference between the front and rear stages of the cold / hot water generators R1 and R2.

  The running water sent to the feed header CH1 only needs to have the amount of water required by the secondary pump as a result, and if the amount of water more than that is sent, all of the excess water is wasted. Therefore, the basic principle is that the primary pump side first supplies the minimum amount of water on the secondary pump side at a constant temperature.

  In the above formula 1, the required energy q varies depending on the load variation on the secondary pump side. In this case, if the temperature change Δt is constant, the required energy q is proportional to the amount of water Q. Therefore, when it is desired to keep the change Δt in temperature constant, it is clear that the water amount Q may be varied according to the load variation on the secondary pump side. Therefore, the inverters Inv11 and Inv12 are caused to change the amount of water Q. If this mechanism works automatically, as a result, the flowing water fed to the feed header CH1 is always maintained at the amount of water required by the secondary pump side, and energy waste is theoretically zero. This operation is performed by the temperature sensors Th11 and Th12, the temperature setting device C12, and the inverters Inv11 and Inv12, and as a result, the energy that is wasted on the primary pump side is first brought to zero as much as possible.

  Since the above configuration performs an automatic control action very smoothly in a normal state, the water pressure in the feed header CH1 is always kept at the minimum required water pressure on the secondary pump side. In the conventional technique, since such control is not performed, the feed header CH1 on the secondary pump side is fixed at water pressure, and the load on the secondary pump side, that is, the amount of water required by the heat exchangers F1 and F2 is large. Even when the load on the secondary pump side decreases and the required amount of water drops, the amount of water far exceeding that amount is sent to the feed header CH1, and the excess amount of water is returned to the return header through the bypass BP1. There was a waste of constant escape to CHR. Thus, in the prior art, since water was always supplied with the fixed water pressure on the secondary pump side, the bypass BP1 was always open and no mechanism for controlling the return water flow was provided (see FIG. 6).

  However, in the air conditioning system ACU shown in FIG. 1, in a normal operation state, the feed header CH1 only has a minimum water pressure that matches the load on the secondary pump side, and thus it is necessary to return the amount of water through the bypass BP1. Absent. Therefore, it is not necessary to provide the bypass BP1 in a normal operation state. However, when the load on the secondary pump side is extremely reduced or when an abnormal water pressure occurs due to a failure of the inverters Inv11 and Inv12, the amount of water needs to be returned to the return header CHR through the bypass BP1.

  Therefore, a relief valve B1 is provided in the bypass BP1 to monitor both the normal operation and the case where it is necessary to return the amount of water to the return header CHR, and the water pressure in the feed header CH1 is monitored. Thus, when the water pressure of the feed header CH1 exceeds the set value, the relief valve B1 is automatically opened, and a mechanism for allowing the water amount of the feed header CH1 to escape to the return header CHR through the bypass BP1 becomes necessary.

  In the air conditioning system ACU of FIG. 1, this mechanism is made up of a pressure gauge P1 provided in the feed header CH1, a pressure setting device (PID controller) C11 (see FIG. 2) in the primary pump side controller C1, and a bypass path. It is constituted by a relief valve B1 provided in BP1. That is, the bypass BP1 is closed by the relief valve B1 in a normal operation state, but the pressure gauge P1 constantly monitors the water pressure of the feed header CH1, and the water pressure of the feed header CH1 exceeds the set value. The pressure setter C11 that has received the information transmits a valve opening command to the relief valve B1. As a result, the relief valve B1 is opened, and the excess water amount in the feed header CH1 is returned to the return header CHR through the bypass BP1. When the water pressure in the feed header CH1 returns to the set value, the pressure setter C11 transmits a valve closing command to the relief valve B1, and the relief valve B1 is closed to return to the normal operation state.

Next, the operation on the secondary pump side will be described in detail (see FIGS. 1 and 2).
The water flow branches from the feed header CH1 and is sucked into the secondary pumps Po21 and Po22 and guided to the feed header CH2.

  The water flow is sucked from the feed header CH1 to the secondary pumps Po21 and Po22 and guided to the feed header CH2. At this time, the secondary pumps Po21 and Po22 feed the minimum amount of water required by the heat exchangers F1 and F2. Thus, the inverters Inv21 and Inv22 are controlled. The control method is as follows.

  A temperature sensor Th21 is provided in the preceding stage of the return header CHR, and constantly monitors the temperature of the water flow that has passed through the heat exchangers F1 and F2. This temperature information is transmitted to the temperature setter (PID controller) C21 of the secondary pump side controller C2, and the rotation speeds of the secondary pumps Po21 and Po22 are transmitted from the temperature setter C21 via the inverters Inv21 and Inv22. The frequency signal to be controlled is output.

  When the detected temperature of the temperature sensor Th21 deviates from the set value of the temperature setter C21, the temperature setter C21 controls the rotational speed of the secondary pumps Po21 and Po22 so as to return the detected temperature of the temperature sensor Th21 to the set value. A signal is sent to the inverters Inv21 and Inv22, and the rotational speeds of the secondary pumps Po21 and Po22 are controlled so as to return the detected temperature of the temperature sensor Th21 to the set value. As a result, the flowing water sent to the heat exchangers F1 and F2 The flow rate is adjusted, and the water temperature of the running water that has passed through the heat exchangers F1 and F2 is returned to the set value. In this way, the temperature of the flowing water that has passed through the heat exchangers F1 and F2 is kept constant by the temperature signal of the temperature sensor Th21.

  That is, based on the same principle as the primary pump side, the idea is to manage the amount of flowing water so that the outlet temperature of the heat exchangers F1 and F2 is fixed to the set value, and the inverter is controlled by the outlet temperature of the heat exchangers F1 and F2. The flow rate fluctuation operation for controlling the frequency of Inv21 and Inv22 is performed. The above-described operation is explained based on the same principle as that on the primary pump side.

  That is, similarly to the primary pump side, the fluctuations in energy required in the heat exchangers F1 and F2 are caused by the amount of flowing water passing through the heat exchangers F1 and F2, the upstream and downstream stages of the heat exchangers F1 and F2. Therefore, if the amount of change in water temperature is desired to be constant, the amount of water may be changed in proportion to the required energy. If this mechanism works automatically, as a result, the running water sent to the feed header CH2 is always kept at the minimum amount of water required by the heat exchangers F1 and F2, and energy waste is theoretically reduced. Becomes zero. This operation is performed by the temperature sensor Th21, the temperature setting device C12, and the inverters Inv21 and Inv22, and as a result, energy that is wastedly consumed even on the secondary pump side is made as close to zero as possible.

In Example 1, since the water supply temperature management is already performed by the temperature sensors Th11 and Th12, the temperature setting device C12, and the inverters Inv11 and Inv12 on the primary pump side, the temperature sensor Th22 is the heat exchanger F1, It is provided only for the purpose of confirming the water temperature before F2. However, the temperature sensors Th11 and Th12, the temperature setting device C12, the inverters Inv11 and Inv12 are lacking on the primary pump side, and the water supply temperature management on the primary pump side is left only to the temperature management function of the cold / hot water generators R1 and R2. In the case of being present, the water temperature fed to the secondary pump side varies. Therefore, in this case, the temperature sensor Th22 monitors the water temperature upstream of the heat exchangers F1 and F2, and the temperature sensor Th21 monitors the water temperature downstream of the heat exchangers F1 and F2, and the difference between the two water temperatures is constant. In addition, it is necessary to control the amount of water flow sent to the heat exchangers F1 and F2 so that the temperature monitored by the temperature sensor Th21 is constant.

  Further, regarding the bypass passage BP2, in the air conditioning system ACU shown in FIG. 1, in the normal operation state, only the amount of water corresponding to the amount of water required for the heat exchangers F1 and F2 is sent to the feed header CH2, so that the bypass passage There is no need to return the amount of water through BP2. Therefore, in a normal operation state, the relief valve B of the bypass passage BP2 may be closed. However, when the load of the heat exchangers F1 and F2 is extremely reduced and the amount of water required by the heat exchangers F1 and F2 falls below the minimum output (minimum rotation speed) of the secondary pumps Po21 and Po22, Since there are cases where the amount of water in the feed header CH2 becomes excessive, it is necessary to return the amount of water to the feed header CH1 through the bypass BP2 only in this case.

  Therefore, in order to cope with both the case of normal operation and the case where the amount of water required by the heat exchangers F1 and F2 falls below the minimum output (minimum number of rotations) of the secondary pumps Po21 and Po22, the bypass path BP2 is provided with a relief valve B, the water pressure in the feed header CH2 is monitored, and when the water pressure in the feed header CH2 exceeds a set value, the relief valve B is automatically opened, and the amount of water in the feed header CH2 is bypassed BP2. Therefore, a mechanism for escaping to the sending header CH1 is required.

  In the air conditioning system ACU in FIG. 1, this mechanism is provided in the pressure gauge P provided in the feed header CH2, the pressure setter (PID controller) c1 (see FIG. 2) in the controller ctu, and the bypass BP2. The relief valve B is used. That is, the bypass BP2 is closed by the relief valve B in a normal operation state, but the pressure gauge P constantly monitors the water pressure of the feed header CH2, and the water pressure of the feed header CH2 exceeds the set value. Then, the pressure setting device c1 receiving the information transmits a valve opening command to the relief valve B. As a result, the relief valve B is opened, and the excess water amount of the feed header CH2 is returned to the feed header CH1 through the bypass BP2. When the water pressure in the feed header CH2 returns to the set value, the pressure setter c1 transmits a valve closing command to the relief valve B, the relief valve B is closed, and the normal operation state is restored.

  Further, in FIG. 1, a flow meter Q is provided in front of the temperature sensor Th21, which constantly monitors the flow rate returned to the return header CHR, and sends flow information to the start / stop instruction of the controller ctu. Transmit to device c2 (see FIG. 2). Based on this flow rate information, the start / stop instruction device c2 sends a start / stop signal indicating whether the two secondary pumps Po21 and Po22 are operating together, or only one of them, to operate the inverter Inv21, 2 of the secondary pump Po21. It transmits to the inverter Inv22 of the next pump Po22. In the conventional air conditioning system acu shown in FIG. 6, the command transmitted from the controller ctu to the inverters Inv21 and Inv22 includes a frequency signal for controlling the rotation speed of the inverters Inv21 and Inv22 in addition to the start / stop signal. In the air conditioning system of the first embodiment, since the rotation speed control of the inverters Inv21 and Inv22 is all performed only by the frequency signal from the temperature setting device C21, the command from the start / stop instruction device c2 of the controller ctu is only the start / stop signal. It becomes.

  3a is a concept comparing the operating point of the primary pump in the conventional air conditioning system acu (hereinafter referred to as a comparative example) of FIG. 6 and the operating point of the primary pump in the air conditioning system ACU of the embodiment 1 of FIG. FIG. In this case, FIG. 3a shows the operating state of the primary pump Po11 or the primary pump Po12. If the primary pump Po11 and the primary pump Po12 are pumps having the same performance, both graphs are the same. It becomes. Since this is a conceptual diagram to the last, no specific numerical scale is included. 6 shows a comparison of pump operating points when the conventional air conditioning system acu of FIG. 6 is assembled with the same performance pump (comparative example) and when the air conditioning system ACU of the embodiment 1 of FIG. 1 is assembled (example). It is.

  In FIG. 3a, PA11 represented by a solid line is a pump performance curve of the primary pump Po11 or the primary pump Po12, and PR1 represented by a two-dot chain line is a circuit resistance curve of the circuit. Then, the point where the pump performance curve PA11 and the pipe resistance curve PR1 intersect becomes the maximum flow rate (horizontal axis) and the maximum water pressure (vertical axis) required by the secondary pump side in the feed header CH1. Therefore, in both the comparative example and the example 1, the operating point d1a (comparative example) and the operating point D1a (example 1) overlap at this point.

  However, in the comparative example, even when the flow rate required on the secondary pump side in the feed header CH1 decreases, the primary pump Po11 or the primary pump Po12 is operated at a constant water pressure, so at the operating point d1b. The flow rate decreases, but the water pressure is the same as the operating point d1a. On the other hand, in the first embodiment, the primary pump Po11 or the primary pump Po12 is always operated at the minimum flow rate and water pressure required on the secondary pump side. However, this point is almost on the pipeline resistance curve PR1. Therefore, when the operating point d1b and the operating point D1b are compared, the operating point D1b is energy-saving by the difference in water pressure. It is clear that the difference in water pressure increases as the flow rate decreases as d1c vs. D1c, d1d vs. D1D. In addition, since water pressure is proportional to the square of the amount of water and power consumption is proportional to the cube of the amount of water, a significant reduction in power consumption has been realized even though there is a slight decrease in water pressure in FIG. 3a. Become.

  Next, FIG. 3b compares the operating point of the secondary pump in the conventional air conditioning system acu (hereinafter referred to as a comparative example) of FIG. 6 and the operating point of the secondary pump in the air conditioning system ACU of the embodiment 1 of FIG. FIG. In this case, FIG. 3b shows two operating states of the secondary pump Po21 and the secondary pump Po22 (pump performance curve PA22) or one of the operating states (pump performance curve PA21 where two pumps have the same performance). Assumable). Since this is a conceptual diagram just like FIG. 3a, no specific numerical scale is included. 6 shows a comparison of pump operating points when the conventional air conditioning system acu of FIG. 6 is assembled with the same performance pump (comparative example) and when the air conditioning system ACU of the embodiment 1 of FIG. 1 is assembled (example 1). Is. In the figure, PA22a is a pump performance curve when two secondary pumps Po21 and Po22 are operated at 75% output, and PA22b is two secondary pumps Po21 and Po22 at 50% output. It is a pump performance curve at the time of driving | operation.

  During operation of two units, the point where the pump performance curve PA22 and the pipe resistance curve PR2 intersect is the maximum flow rate required by the load (heat exchangers F1 and F2) at the feed header CH2, as in FIG. 3a. Horizontal axis) and maximum water pressure (vertical axis). Therefore, in both the comparative example and the example 1, the operating point d2a (comparative example) and the operating point D2a (example 1) overlap at this point.

  However, in the comparative example, even when the flow rate required on the load (heat exchangers F1, F2) side is reduced to 75% in the feed header CH2, the secondary pumps Po21, Po22 have a constant water pressure (set water pressure T). Therefore, the flow rate is reduced at the operating point d2b, but the water pressure is the same as that at the operating point d2a. On the other hand, in the first embodiment, the secondary pump Po21 and the secondary pump Po22 are always operated at the minimum flow rate and water pressure required on the load (heat exchangers F1 and F2) side, so that the water pressure decreases with the flow rate. The operating point D2b is approximately on the pipe resistance curve PR2. Therefore, when the operating point d2b and the operating point D2b are compared, the operating point D2b is energy-saving by the difference in water pressure. It can be seen that the difference in water pressure further increases at d2c vs. D2c (50%). As described above, the water pressure is proportional to the square of the pump water volume, and the power consumption is proportional to the cube of the pump water volume. Therefore, even if the water pressure drop is small in FIG. Is realized. If the minimum discharge flow rate of the secondary pumps Po21 and Po22 is 50%, the secondary pumps Po21 and Po22 shift to the constant pressure operation at 50% or less. Accordingly, the difference in water pressure between the operating point d2d and the operating point D2d is not different from the difference between the operating point d2c and the operating point D2c.

  FIG. 4 illustrates changes in the pump head of the circuit at the basic flow rate in Example 1 and the comparative example. As is apparent from this figure, in each part of the return header CHR, the primary pumps Po11, Po12, the feed header CH1, and the secondary pumps Po21, Po22, the embodiment 1 is clearly energy saving compared to the comparative example. You can see that. As described above, the discharge pressure of the pump is proportional to the square of the amount of water, but the power consumption is proportional to the cube of the amount of water. Therefore, in FIG. Although it may not seem, it is a big difference in power consumption. The basic flow rate is a flow rate required when the heat exchangers F1 and F2 are operated at a capacity of 100% as described above, and the time when the flow rate is reduced means that the flow rate is lower than the basic flow rate. To do.

  FIG. 5 illustrates the change in the pump head of the circuit when the flow rate is reduced in Example 1 and the comparative example. Compared to the basic flow rate, the required water amount converted to the pump head is approximately equal on the primary pump side. In the case of 3 m, on the secondary pump side, it shows a case where it has decreased about 6 m. As is apparent from this figure, in each part of the return header CHR, the primary pumps Po11, Po12, the feed header CH1, and the secondary pumps Po21, Po22, the embodiment 1 is clearly energy saving compared to the comparative example. In particular, it can be seen that there is a large difference between the return header CHR and the secondary pumps Po21 and Po22. Moreover, as described above, the discharge pressure of the pump is proportional to the square of the amount of water, but since the power consumption is proportional to the cube of the amount of water, there is a much larger difference in power consumption. Thus, although there is a great difference from the comparative example even at the basic flow rate, the energy saving effect of Example 1 becomes very remarkable when the flow rate is reduced.

  As shown in FIGS. 4 and 5, in the normal operation state of the first embodiment, there is no portion for returning the water pressure anywhere, so the primary pumps Po11 and Po12 and the secondary pumps Po21 and Po22 are completely connected. In this state, the cold / hot water generators R1 and R2 and the heat exchangers F1 and F2 work to provide a minimum amount of water and water pressure, so that an energy saving state that is almost ideal is achieved. In the first embodiment, the circuit configuration is made with two primary pumps and two secondary pumps, but it is natural that the number of primary pumps and the number of secondary pumps can be arbitrarily set. It is. It is also possible to combine a plurality of primary pumps having different performances or a plurality of secondary pumps having different performances. These setting changes are naturally included in the scope of the present invention.

  The present invention is close to a theoretical value with a simple configuration without using any advanced hardware or software on the secondary pump side of the air conditioning system or on both the primary pump side and the secondary pump side. It can achieve high energy savings and can be easily integrated into existing air conditioning systems. Therefore, the industrial applicability is very wide, especially for small and medium-sized business establishments who were hesitant to introduce an air conditioning system using advanced hardware and software. As a superior cost-effective air conditioning system that can achieve the above, there is a possibility of widespread use.

It is a circuit diagram of one example of an air-conditioning system of the present invention. It is explanatory drawing explaining the control system structure of one Example of the air conditioning system of this invention. (A) It is a conceptual diagram which shows the comparison of the operating point of the primary pump of 1 Example of an air-conditioning system of this invention, and a comparative example (prior art). (B) It is a conceptual diagram which shows the comparison of the operating point of the secondary pump of 1 Example of an air-conditioning system of this invention, and a comparative example (prior art). It is explanatory drawing which shows the pump head change at the time of the basic flow rate of 1 Example of an air conditioning system of this invention, and a comparative example (an example of the air conditioning system of a prior art). It is explanatory drawing which shows the pump head change at the time of flow volume reduction of 1 Example of an air-conditioning system of this invention, and a comparative example (an example of a prior art air-conditioning system). It is a circuit diagram of an example of the conventional air conditioning system.

Explanation of symbols

ACU air conditioning system
B Relief valve B1 Relief valve BP1 Bypass path BP2 Bypass path C1 Primary pump side controller C11 Pressure setter C12 Temperature setter C21 Temperature setter C2 Secondary pump side controller CH1 Feed header CH2 Feed header CHR Return header CTU controller D1a operating point D1b operating point D1c operating point D1d operating point D2a operating point D2b operating point D2c operating point D2d operating point EXT expansion tank F load F1 heat exchanger F2 heat exchanger Inv11 inverter Inv12 inverter Inv21 inverter Inv21 inverter Inv21 inverter Inv21 inverter Inv21 inverter Inv21 inverter Total PA11 Pump performance curve PA21 Pump performance curve PA22 Pump performance curve PA22a Pump performance curve PA22b Pump performance curve PR1 Pipe resistance curve PR2 Pipe resistance curve Po11 Primary pump Po 2 Primary pump Po21 Primary pump Po22 Primary pump Q Flow meter R1 Cold / hot water generator R2 Cold / hot water generator T Set water pressure Th11 Temperature sensor Th12 Temperature sensor Th21 Temperature sensor Th22 Temperature sensor acu Air conditioning system b1 Two-way valve b2 Two-way Valve c1 Pressure setting device c2 Start / stop instruction device ctu controller d1a operating point d1b operating point d1c operating point d1d operating point d2a operating point d2b operating point d2c operating point d2d operating point

Claims (10)

It comprises a primary pump, a cold / hot water generator placed downstream of the primary pump, a secondary pump placed downstream of the cold / hot water generator, and a heat exchanger placed downstream of the secondary pump. In the air conditioning system
Control means for controlling the rotational speed of the secondary pump;
Having temperature measuring means for measuring the temperature of running water that has passed through the heat exchanger;
A control method for an air conditioning system, wherein the rotational speed of a secondary pump is controlled so that the temperature of running water that has passed through a heat exchanger is kept constant based on temperature information from the temperature measuring means.   The air-conditioning system controlled by the control method of the air-conditioning system of Claim 1. It comprises a primary pump, a cold / hot water generator placed downstream of the primary pump, a secondary pump placed downstream of the cold / hot water generator, and a heat exchanger placed downstream of the secondary pump. In the air conditioning system
Control means for controlling the rotational speed of the secondary pump;
Having temperature measuring means for measuring the temperature of running water that has passed through the heat exchanger;
A control device for an air conditioning system, wherein the number of rotations of the secondary pump is controlled so that the temperature of the flowing water that has passed through the heat exchanger is kept constant based on temperature information from the temperature measuring means.   4. The air conditioning system control device according to claim 3, wherein the temperature measuring means of the air conditioning system is a temperature sensor, and the control means is a temperature setter and an inverter using a PID (calculus) control method.   An air conditioning system comprising the control device for an air conditioning system according to claim 3. Control means for controlling the rotational speed of the primary pump;
Having temperature measuring means for measuring the temperature of running water that has passed through the cold / hot water generator;
2. The air conditioning system according to claim 1, wherein the rotational speed of the primary pump is controlled so that the temperature of the flowing water that has passed through the cold / hot water generator is kept constant based on temperature information from the temperature measuring means. Control method.   It is controlled by the control method of the air-conditioning system according to claim 6. Control means for controlling the rotational speed of the primary pump;
Having temperature measuring means for measuring the temperature of running water that has passed through the cold / hot water generator;
4. The air conditioning system according to claim 3, wherein the number of revolutions of the primary pump is controlled so that the temperature of the flowing water that has passed through the cold / hot water generator is kept constant based on temperature information from the temperature measuring means. Control device.   9. The control device for an air conditioning system according to claim 8, wherein the temperature measuring means of the air conditioning system is a temperature sensor, and the control device is a temperature setter and an inverter using a PID (calculus) control method. An air conditioning system comprising the control device for an air conditioning system according to claim 8 or 9.

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