JP2011127859A - Cooperation control device and method for heat source system - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To minimize a rotational frequency of a pump for sending a heat medium produced by a heat source machine, in controlling a flow rate of the heat medium in equipment consuming heat. <P>SOLUTION: This cooperation control device is composed of a pump operating state control device for controlling the rotational frequency of an inverter-driven liquid sending pump, and a flow rate control device for controlling the flow rate of heat medium in each load piping system, the operating state control device of the liquid sending pump outputs a command for fully opening a valve to the flow rate control valve of the load piping system and the like having the maximum heat medium flow rate, controls the rotational frequency of the pump to achieve the desired flow rate, and further controls the flow rates of the other piping systems of low required flow rate on the basis of an opening of each flow rate control valve. <P>COPYRIGHT: (C)2011,JPO&INPIT

Description

  The present invention relates to a cooperative control device and a cooperative control method for a heat source system used in production facilities such as factories and air conditioning equipment, and more particularly to a water supply system used in production facilities and the like, a heat medium for a liquid supply system, water, and liquid. The present invention relates to a cooperative control device and a cooperative control method of a heat source system that suitably controls the flow rate of the heat source system.

  Many of the heat source systems, which are facilities that send cold / hot water generated by the heat source machine to the receiving side, for example, as described in [Patent Document 1] and [Patent Document 2], the flow rate of the cold / hot water to be supplied to the receiving side. The flow rate control of cold / hot water is performed by combining variable flow rate control that is reduced according to load and unit control that controls the number of operating heat source units. When the variable flow rate control is not performed, for example, as described in [Prior Art] of [Patent Document 2], by controlling the flow rate of the bypass flow path from the heat source unit side to the downstream side of the load. The flow rate required by the load is balanced with the water flow rate on the heat source side.

  Among these conventional techniques, the conventional technique described in [Patent Document 1] assumes that the relationship between the heat demand of the load and the flow rate determined from the internal resistance of the load is unknown, and as a result, the heat flowing as a result. Using the flow rate of the medium and the measurement result of the temperature of the heat medium at the outlet side of the load, the heat quantity and flow rate required on the heat source unit side are calculated independently, the number of operating units and the heat medium flow rate are determined, and the heat source unit The number of units and the flow rate of the heat transfer pump that is an auxiliary machine are controlled. As a result, the number of heat source units and the operation state can be controlled to meet the heat load, and thus energy saving can be realized as compared with the case of bypassing.

  However, in the conventional technology of [Patent Document 1], from the viewpoint of cooperation between the load facility and the heat source system, the control of the flow rate of the heat medium is performed only on the heat source unit side, and from the load facility assumed to be plural, Only the two pieces of information of the heat medium flow rate and the outlet temperature as a whole are utilized for control.

  As a conventional technique for improving the operation efficiency of the heat source system by obtaining more information from the load facility, there is one described in [Patent Document 3]. In this prior art, valve opening information of a flow rate control valve for controlling the flow rate of the heat medium is acquired on the load equipment side provided in parallel, and the number of heat source devices is controlled based on this information. In this unit control, if there is a load with the valve opening fully open, it is determined that the generated energy as a heat source is insufficient, and the number of heat source units started is increased (increased). If there is zero load, the number of heat source units is reduced (decreased).

  Regarding the linkage with the load equipment, in addition to the valve opening shown here, an example of using a deviation between the temperature target at each load and the actual temperature (temperature target at each load-actual temperature) is also shown. In this example, if the maximum value of deviation (there is a plus side and a minus side) is larger than the reference value, the stage is reduced or increased. For example, when the heat source is cold, the step is increased if the negative maximum value is larger than the reference value, and is decreased if the positive maximum value is larger than the set value. According to this prior art, it is said that the wasteful operation of the heat source device can be optimally eliminated in consideration of various operation states of the load facility.

  In [Patent Document 1] and [Patent Document 2], when the heat consumption at the load facility is small and the difference between the temperature at the outlet of the heat source unit and the temperature at the load facility outlet is smaller than the design value, Focusing on the fact that the load of the heat source machine becomes smaller than the design value, the flow rate of the heat medium is a flow rate that matches the design heat load (constant x design temperature difference x design flow rate = design flow rate determined by heat source machine capacity. = When the heat load is larger than the absolute value (heat source machine outlet temperature at design-load outlet temperature at design) and the heat load is smaller than the design temperature difference, more heat medium is sent than the design flow rate. A technique called overflow control that allows liquid to flow is also described. As a result, when the heat medium flow rate is required even though the heat load is low, the loss caused by excessively starting the heat source device in terms of heat is reduced.

  As described above, the load is not controlled in the control system that drives the pump, which is an auxiliary device of the heat source unit, so that the heat medium flow rate matches the amount of heat required by the load by performing variable flow rate control. Such a method is optimal when the flow rate of the load cannot be controlled.

  However, as in the prior art described above, when obtaining the valve opening information of the load facility and controlling the number of heat source facilities, the load state is actually the load-side control system and the target given thereto. It can often be changed depending on the value. On the load side, in order to remove heat or preheat so that the temperature of the process becomes a desired value, the flow rate of the heat medium is controlled, and these controls change the flow path resistance of the heat medium such as valves and vanes. It is carried out by that.

  In such a heat transfer system, the relationship between the channel resistance and the flow rate is a function of the pressure difference applied to the channel, and when the pressure difference is constant, the channel resistance for obtaining a desired flow rate is Determined uniquely. For this reason, the pressure may be adjusted to the target flow rate, but the pressure of the heat medium is usually set to a predetermined pressure sufficiently higher than the pressure difference suitable for the flow path resistance, and at a set constant rotational speed. In operation, the flow rate of the heat medium is controlled by changing the flow path resistance by a control valve or vane provided in each load facility.

JP 2008-309428 A JP 2004-245560 A JP 2009-63231 A

  In the system as described above, since the flow rate is controlled to be a desired heat medium flow rate, the pump that is an auxiliary machine of the heat source unit is determined without depending on the control, such as piping. Not only the resistance but also the pressure loss due to the control valve and vane must work, resulting in energy loss.

  If a single auxiliary pump has a single load, the speed of the pump can be controlled by an inverter instead of a control valve or vane, but multiple loads are installed in parallel to the pressure source. In such a system, it is necessary to control the pump so that the total heat medium flow rate required for all loads can be sent out, depending on the difference in piping resistance and valve opening to each load. It is not always possible to secure.

  Further, in practice, since each individual load is controlled independently, control is not performed so as to operate the pump with minimum power consumption.

  An object of the present invention is to provide a cooperative control device and a cooperative control method of a heat source system that can secure a heat medium flow rate that requires all loads with a minimum water supply or liquid supply pressure as the heat source system.

  In order to achieve the above object, the present invention inputs a required water amount, a required liquid amount or a required heat amount for each load set by a control system for controlling the respective loads arranged in parallel, and has a maximum required flow rate. A pump operation control device that outputs a full open command to the flow control valve of the piping system and controls the pump output so that the flow rate of the fluid flowing through the flow control valve becomes the required value of the load, and the valve opening When there is a flow control depending on the degree and a fully open command from the pump operation control device, the flow control device for each load system is configured to fully open the flow control valve instead of the normal flow control.

  Also, the opening information of the flow control valve that controls the flow rate of the heat medium to a plurality of load systems arranged in parallel is inputted, and either of the opening amounts of the flow control valve is not fully opened or vice versa. The pump operation control device that gradually reduces or increases the flow rate of the pump from the fully open state to the non-fully open state, and the flow rate control so that the flow rate of the heat medium flowing to each load becomes a set amount It is comprised with the flow control apparatus for every load system which controls the opening degree of a valve.

  According to the present invention, since the discharge pressure of the pump that sends the heat medium to the load arranged in parallel can be minimized within a range that satisfies the heat demand, the power load of the heat source system can be reduced.

The block diagram of the heat-source system for demonstrating the driving | operation of a liquid feeding pump. The figure which shows the flow volume-head characteristic for demonstrating liquid feeding pump operation | movement, the resistance curve of a piping system, and a power consumption curve. The block diagram of the heat-source system concerning Example 1 of this invention. The PAD figure which shows the process algorithm in a pump flow control apparatus. The block diagram of a control system at the time of using the pump operation control system of a present Example. The block diagram of the heat-source system concerning Example 2 of this invention. The PAD figure which shows the processing algorithm of the pump operation control apparatus of a present Example. The block diagram of the heat-source system concerning Example 3 of this invention. The block diagram of the heat-source system concerning Example 4 of this invention.

  In order to facilitate understanding of the embodiments of the present invention, a simplified heat source system will be described. FIG. 1 is a configuration diagram of a simplified heat source system, and FIG. 2 shows a state of a heat medium feeding pump in the heat source system shown in FIG.

  In the heat source system shown in FIG. 1, the heat medium generated by the heat source device 151 is pressurized by the liquid feed pump 113 and sent to the load equipment 154 and the load equipment 155 via the forward header 152. The heat exchanged heat medium is once collected in the return header 153 through the return pipe, and then supplied to the heat source device 151 again.

  Normally, a temperature control system for setting the flow rate is provided according to the heating amount or cooling amount of the load equipment 154, 155, and the valve opening degree is controlled based on the flow rate measurement value so that the set flow rate is obtained. In addition, the flow rate of the heating medium of the load equipment 154, 155 is controlled according to the heat demand. In the example of FIG. 1, an example is shown in which the flow rate control system is configured by the flow rate sensors 124 and 134, the flow rate control devices 125 and 135, and the flow rate control valves 122 and 132. The determination of the liquid supply pressure of the liquid supply pump 113 will be described with reference to FIG. 2, taking as an example the case where the required flow rates at the load facilities 154 and 155 are Q1 and Q2, respectively.

  A curve 323 shown in FIG. 2 indicates a load on the piping system 120 or 130 when the flow control valve 122 or 123 is fully opened. A flow rate-lifting curve when the liquid feed pump 113 is operated at a certain rotation speed is shown by a curve 301. Here, when the flow rate Q1 is necessary for the load facility 154 and the flow rate Q2 is necessary for the load facility 155, the flow rate control device 125 changes the load characteristic of the piping system 120 as indicated by a curve 303 by narrowing the valve opening. Similarly, in the piping system 130, the load characteristic of the flow control valve 132 is controlled to be a curve 302.

  However, ideally, of the flow rates Q1 and Q2, the opening of the valve with the larger flow rate is fully opened, the load characteristic is changed from the curve 303 to the curve 323, and the flow rate Q1 is obtained so that the necessary flow rate Q1 can be obtained at that time. -Power consumption can be reduced by controlling the pump rotation speed so that the pump operation is performed at the rotation speed at which the lift curve becomes the curve 321. In a state where the liquid feed pump 113 is controlled so as to maintain this rotational speed, the flow rate control valve 132 on the load facility 155 side can take a valve opening larger than the curve 302, and the characteristic becomes the curve 322. Drive to.

  Curves 304, 324, 305, 325, 332, and 342 are curves connecting states in which the power consumption in the liquid feed pump 113 is constant (constant on the curve but different between the curves). , And the flow-lift curve is changed from the curve 301 to the curve 321, the power consumption for the load equipment 154 is changed from the curve 304 to the curve 324, and the power consumption for the load equipment 155 is changed from the curve 305 to the curve 325. In other words, the power consumption by the pump operation can be controlled to be minimized within a range satisfying the flow rates Q1 and Q2 of the heat medium demand.

  The final operating state of the pump is a curve 331 and the power consumption is a curve 332. On the other hand, when the load characteristics of the piping system 120 and the piping system 130 are the curve 303 and the curve 302, respectively, the entire characteristic is represented by the curve 340, the operation state of the liquid feed pump 113 is the curve 341, and the power consumption at that time is the curve. 342.

  Thus, it can be seen that the power consumption of the curve 342 can be shifted to the power consumption of the curve 332 by cooperatively controlling the flow rate control valve and the liquid feeding pump.

  A first embodiment of the present invention will be described with reference to FIGS.

  The heat source system shown in FIG. 3 supplies a heat medium to the load facilities 154, 155, and 156 via the forward header 152 disposed on the outlet side of the heat source unit 151. The heat medium exchanged by the load facilities 154, 155, and 156 is collected in the return header 153 through the pipes, and is supplied from the return header 153 to the heat source unit 151 by the liquid feed pump 113. Used to heat or remove heat at 155,156.

  The load facilities 154, 155, and 156 are provided with flow control devices 125, 135, and 145 that control the flow rate of the heat medium as necessary, and the heat flowing through the load facilities measured by the flow meters 124, 134, and 144. Based on the medium flow rate, the opening degree of the flow rate control valves 122, 132, 142 that change the flow resistance of the heat medium flow path is controlled to control the flow rate set values 127, 137, 147.

In this embodiment, there is a pump operation control device 100 that controls the liquid feed pump 113 that sends heat generated by the heat source device 151 to the system by a heat medium. The pump operation control apparatus 100 receives the measured values 121, 131, and 141 of the flow rate of the heat medium flowing through each load facility and the flow rate setting values 127, 137, and 147 as inputs, and the flow rate control apparatuses 125, 135, and The full-open selection commands 123, 133, and 143 are output to the selectors 126, 136, and 146 that select the output of 145 and the full-open command. Further, the rotational speed command value 112 is also output to the liquid feed pump 113.
The inverter 111 that controls the rotational speed of the liquid feed pump 113 receives this command and controls the rotational speed of the liquid feed pump 113 to be the rotational speed command value 112.

  Next, the processing algorithm of the pump operation control apparatus 100 of the present embodiment will be described with reference to FIG. The algorithm shown in FIG. 4 is a process that is performed, for example, at a cycle of 1 second.

  STEP 401, which is the first step of the process, is a process for the flow rate control system for controlling each load piping system. For all load systems connected in parallel, the flow rate set value set in STEP 402, for example, as shown in FIG. In this case, a process of reading the flow rate set values 127, 137, and 147 is performed.

  In STEP 403, the load piping system having the maximum flow rate setting value is selected from all the read load systems, and the flow rate setting value is extracted. In STEP 404, a full-open selection command is output to the selector of the piping system having the maximum flow rate, for example, one of the selectors 126, 136, and 146 in the case of FIG. In STEP 405, the pump rotational speed command value is determined based on the error between the flow rate setting value of the load piping system selected in STEP 403 and the actual flow rate and output to the inverter 111 for the liquid feed pump 113.

  Note that, in load piping systems other than the load piping system selected in STEP 403, the flow rate control values 125, 135, and 145 shown in FIG. The opening degree of 122,132,142 is controlled and it controls to become a desired flow volume.

  FIG. 5 is a block diagram of the control system shown in FIG. The flow control devices for each piping system are represented by blocks 901, 902, and 903. The head of the liquid feed pump 113 controlled by the pump operation control device 100 affects the relationship between the opening degree of the flow control valve and the flow rate. On the other hand, the opening degree of each flow control valve affects the pipe resistance of the total load side of the liquid feed pump 113. Because of this relationship, adjustment of the control system may be more complicated than when each is composed of a single control system, but stabilization is possible considering the following behavior.

  For example, when the flow rate command value of the flow rate control system 903 increases, the opening degree of the flow rate control valve is increased in order to increase the flow rate. When operated in this way, in the pump operation control system, the flow rate of the piping system decreases, so that control is performed to increase the number of revolutions of the pump, and the pump head is increased. As a result, the flow rate of the piping system that flows through the flow rate control system 903 further increases, so that the control works in the direction of narrowing the opening degree of the flow rate control valve, so that there is no behavior that greatly impairs stability.

  Further, in the pump operation control system, when the flow rate command value of the piping system rises, control that increases the rotation speed of the pump works, and the pump head increases. This increases the flow rate of the piping systems 901 to 903 controlled by the flow rate control system, but acts in the direction to throttle the flow rate control valve, and can be stabilized to the original value if the command value of the flow rate control system is constant. . Eventually, stabilization can be achieved in that the rotational speed is increased by an amount corresponding to the increase in the instruction value of the pump operation control system.

  According to the present embodiment, the pump system that requires the maximum flow rate has a minimum flow resistance, and the number of rotations of the pump is controlled to the minimum within a range in which the necessary flow rate is ensured. Operation that minimizes power consumption can be realized.

  In the above description, a system in which a plurality of loads are connected in parallel to a single pump has been described. However, if a pump is provided for each piping system or the like, power consumption can be further suppressed.

  A second embodiment of the present invention will be described with reference to FIGS. FIG. 6 is an equipment configuration diagram in the present embodiment.

  Although the present embodiment is configured in the same manner as the embodiment shown in FIG. 3, in this embodiment, the configuration of the control system is further simplified, and the flow rate control devices 125, 135, and 145 for the heat medium to each load are configured. The selectors 126, 136, and 146 for selecting the output and the full-open command are not provided, and the signals of the flow rate setting values 127, 137, and 147 are not input to the pump operation control device 100.

  That is, there is a structural difference in that the outputs 523, 533, and 543 of the flow control devices 125, 135, and 145 of the load piping systems are provided to the flow control valves 122, 132, and 142 and the pump operation control device 500. .

  FIG. 7 is a diagram showing a processing algorithm of the pump operation control apparatus in the present embodiment shown in FIG. The algorithm shown in FIG. 7 is a process performed with a period of 1 second, for example.

  STEP 601 which is the first step of the process is a process for the flow rate control system for controlling each load piping system. In STEP 602, the opening degree commands from the respective control devices indicated by 523, 533 and 543 in the example of FIG. In step 603, the valve control state is determined from comparison with the past opening command of the control device. In the present embodiment, the valve control state is identified by five ways of “opening increase”, “opening decrease”, “fully open”, “fully closed”, and “hold”.

  In STEP 610, it is checked whether the valve control state of the flow rate control meter is changed from “opening degree increase” to “fully open” and the pump control state is “pump decelerating”. If this condition is met, pump deceleration is stopped in STEP 611, and the processing shown in FIG. In this case, the pump control state is a “pump constant speed” state.

  In STEP 620, it is checked whether the state changes from “fully open” to “opening reduction” and the pump control state is “pump speed increasing”. If this condition is met, pump acceleration is stopped at STEP 621 and the processing of FIG. 6 is terminated at STEP 622. In this case, the pump control state is a “pump constant speed” state. In the pump control state, three states of “pump speed increasing”, “pump decelerating” and “pump constant speed” are set.

  If none of the checks in STEP 610 and STEP 620 correspond, the STEP 630 is checked. In STEP 630, it is checked whether all the flow control valves are not in the “fully open” state (the fully open state) and the pump control state is “pump decelerating”. If this condition is met, in STEP 631, the pump is controlled. Continue to slow down. In STEP 640, it is checked whether one or more flow control valves are in the “fully open” state and the pump control state is “pump speed increasing”. If the check result is true, the speed increase of the pump is continued in STEP641.

  In STEP650, there is a flow rate control system in which the pump control state is "pump constant speed" state, and the flow rate control valve is in a state of "increase in opening" from "hold" in one or more flow rate control systems Check whether or not. If there is such a flow rate control system, in STEP 651, the pump control state is switched from the “hold” state to the “speed increase” state, and the pump speed increase is started. If the check result of STEP 650 is false and the pump state is the “pump constant speed” state, the presence or absence of a system in which the valve control state is “hold” to “decrease opening” is checked in STEP 652. If there is such a flow rate control system, in STEP 653, the pump control state is switched from the “hold” to the “deceleration” state, and the pump starts decelerating.

  By performing the above processing at a constant cycle, the flow control can be performed so that the opening of the flow control valve of one flow control system is in the vicinity of the fully open, and the other valve openings are required.

  According to the present embodiment, when the pump discharge pressure is initially high, the flow control system of each load throttles the valve to control the flow rate to a required value, but the pump operation control device controls the pump discharge pressure. Since it gradually decreases, the flow control system of each load operates to open the valve and secure the flow rate. By stopping the pump discharge pressure reduction when any one of the valve openings is fully opened, the pump operation can be performed such that the power consumption is minimized under the conditions satisfying the heat medium flow rate required by the load.

  On the other hand, when the pump discharge pressure is low and a desired flow rate cannot be secured at the load, the valve opening of the load piping control system other than the fully open load becomes large. By increasing the pump discharge pressure until the valve opening is fully open after the valve is fully opened, the pump operation with the minimum power consumption can be performed under conditions that satisfy the heat medium flow rate required by the load. .

  A third embodiment of the present invention will be described with reference to FIG. FIG. 8 is an equipment configuration diagram in the present embodiment.

  The present embodiment is configured in the same manner as the embodiment shown in FIG. 3, but in this embodiment, a heat storage tank 761 is provided instead of the forward header 152 and the return header 153, and the heat source device 151 is used as the heat storage tank. The temperature is controlled at 761.

  The heat medium in the heat storage tank 761 whose amount of heat deviates from the set value due to the return heat medium is sent to the heat source device 151 by the pump 760, and the heat medium in the heat storage tank 761 measured by the temperature sensor 763 installed in the heat storage tank 761. Preheating and heat removal in the heat source device 151 are controlled using the temperature 762 and are sent to the heat storage tank 761 as a heat medium having a set temperature.

  Although the liquid transfer of the heat medium to the load facility is performed by the pump 713, this control can be performed by the pump operation control device 100 described in FIGS. 3 and 4. The block diagram of the control system shown in FIG. 8 has the configuration shown in FIG.

  A fourth embodiment of the present invention will be described with reference to FIG. FIG. 9 is an equipment configuration diagram in the present embodiment.

  Although this embodiment is configured in the same manner as the embodiment shown in FIG. 6, in this embodiment, a heat storage tank 761 is provided instead of the forward header 152 and the return header 153, and the heat source device 151 is used as the heat storage tank. The temperature is controlled at 761.

  The heat medium in the heat storage tank 761 whose amount of heat deviates from the set value due to the return heat medium is sent to the heat source device 151 by the pump 760, and the heat medium in the heat storage tank 761 measured by the temperature sensor 763 installed in the heat storage tank 761. Preheating and heat removal in the heat source device 151 are controlled using the temperature 762 and are sent to the heat storage tank 761 as a heat medium having a set temperature.

  Although the liquid supply of the heat medium to the load facility is performed by the pump 713, this control can be performed by the pump operation control device 500 described with reference to FIGS.

100, 500 Pump operation control device 111 Inverter 113 Liquid feed pumps 122, 132, 142 Flow rate control valves 125, 135, 145 Flow rate control devices 126, 136, 146 Selector 151 Heat source machine 152 Out header 153 Return header 154, 155, 156 Load Facility

Claims (7)

  A full open command is output to the flow rate control valve of the piping system having the maximum required flow rate among the required flow rates of the plurality of load devices arranged in parallel downstream of the liquid feed pump, and flows through the flow rate control valve. The output of the liquid feeding pump is controlled so that the flow rate of the fluid becomes the required flow rate of the load device, and the flow rate of the other piping system with a low required flow rate is controlled by the opening degree of each flow control valve. Coordinated control device for heat source system.   Calculate the load amount of each of multiple load devices arranged in parallel downstream of the pump from the operation plan of the load facility, and output a fully open command to the flow control valve of the piping system with the maximum required flow rate. The output of the liquid feeding pump is controlled so that the flow rate of the fluid flowing through the flow rate control valve becomes the required flow rate of the load device. A heat source system linkage control device that controls the flow rate according to the valve opening.   Calculate the load amount of each of the multiple load devices arranged in parallel downstream of the liquid pump from the operation plan of the heat load facility, and issue a fully open command to the flow control valve of the piping system, which is the maximum heat load. Output and control the output of the liquid feed pump so that the flow rate of the heat medium flowing through the flow rate control valve becomes the required flow rate of the heat load. A cooperative control device of a heat source system that controls the opening degree of the flow control valve so as to ensure a necessary flow rate of the heat medium according to a thermal load such as.   Based on the required flow rate of each load set in the cooperative control system for multiple load devices arranged in parallel downstream of the liquid pump, the flow rate of the piping system that is the maximum required flow rate matches the required flow rate For the flow control valve that controls the discharge pressure or the rotation speed of the liquid feed pump and controls the flow rate of the piping system, a signal for increasing the valve opening is output, and the other required flow rate is small A cooperative control device for a heat source system that controls the flow rate according to the opening degree of the flow rate control valve of the piping system.   A full open command is output to the flow rate control valve of the piping system having the maximum required flow rate among the required flow rates of the plurality of load devices arranged in parallel downstream of the liquid feed pump, and flows through the flow rate control valve. The output of the liquid feeding pump is controlled so that the flow rate of the fluid becomes the required flow rate of the load device, and the flow rate of the other piping system with a low required flow rate is controlled by the opening degree of each flow control valve. A cooperative control method for the heat source system.   The load amount of each of a plurality of load devices arranged in parallel downstream of the liquid feed pump is calculated from the operation plan of the load facility, and the feed rate is adjusted so that the flow rate of the piping system that is the maximum required flow rate matches the required flow rate. For the flow control valve that controls the discharge pressure or rotation speed of the liquid pump and controls the flow rate of the piping system, it outputs a signal to increase the valve opening, and for other piping systems with a low required flow rate Is a cooperative control method of the heat source system that controls the flow rate by the valve opening degree of the flow control valve.   Calculate the thermal load amount of each of the multiple thermal load devices arranged in parallel downstream of the liquid pump from the operation plan of the thermal load facility, and the flow rate of the piping system that is the maximum required flow rate matches the required flow rate In this way, the discharge pressure or the rotation speed of the liquid feed pump is controlled, and a signal for increasing the valve opening is output to the flow rate control valve of the piping system, and the flow rate control of other piping systems with less heat load is performed. For a valve, a heat source system cooperative control method for controlling the valve opening degree so as to ensure a necessary heat medium flow rate according to the heat load of the piping system or the like.

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