JPWO2018159703A1 - Heat source water control method and heat source water control apparatus - Google Patents

Abstract

In the heat source water control method, the heat source water control device executes a water supply differential pressure acquisition step, an opening degree acquisition step, a target water supply differential pressure calculation step, and a water supply differential pressure control step. The water supply differential pressure acquisition step acquires the water supply differential pressure of the heat source water that is supplied from the heat source unit to the plurality of usage-side heat loads. The opening degree obtaining step obtains the opening degree of at least one valve from the valves provided in the respective use side heat loads and adjusting the supply amount of the heat source water supplied to the use side heat loads. The target water supply differential pressure calculating step calculates a target water supply differential pressure that is a target value of the water supply differential pressure for setting the opening to the target value based on the acquired water supply differential pressure and the acquired opening. The water supply differential pressure control step controls the water supply differential pressure based on the maximum water supply differential pressure that is the maximum value among the calculated target water supply differential pressures.

Description

  Embodiments described herein relate generally to a heat source water control method and a heat source water control apparatus.

  Conventionally, heat source water (cold water or hot water) generated by a heat source machine is used for air-conditioning equipment such as a plurality of air handling units (hereinafter referred to as “air han”), or for use side equipment such as industrial machines that require temperature management. There is a heat source system that pumps water. The air han is a form of an air conditioner, and adjusts the temperature or humidity of air using heat source water supplied from an external heat source machine. The air han has a heat exchanger that is a heat load on the use side and a blower, and blows air that has been heat-exchanged with the heat source water to the indoor unit installed in the air-conditioning target using the blower. The heat source water supplied from the heat source unit to the airhane is heat-exchanged with air in the heat exchanger and then returned to the heat source unit.

  Since the load state of the air han changes depending on the outside air temperature, the operating state of the indoor unit, and the like, the water temperature and the flow rate when the heat source water heat-exchanged by the air han is returned to the heat source device changes depending on the load state of the air han. In order to stabilize the amount of heat source water (hereinafter referred to as “water supply amount”) that is supplied to the use-side equipment such as air han, the heat source unit is a water pressure that supplies the heat source water even if the load state of the use-side equipment changes. There are cases where control is performed to keep the water supply pressure constant. In addition, the heat source unit is a control that keeps the water supply temperature constant even if the load state of the user side device changes in order to stabilize the water temperature of the heat source water (hereinafter referred to as “water supply temperature”) that is supplied to the user side device. May do.

  However, since the load state of the use side device cannot be detected by the heat source device, the heat source device may be operated with a certain margin in the water supply pressure or the water supply temperature. In this case, compared to the actual load state of the use side equipment, heat source water having a water supply pressure or water temperature that is higher than necessary is generated and supplied to generate more power than necessary.

JP 2008-224182 A JP 2014-066389 A Japanese Patent Laid-Open No. 11-063631 JP 2003-262384 A

  The problem to be solved by the present invention is to provide a heat source water control method and a heat source water control device capable of reducing power when generating and sending heat source water.

  In the heat source water control method of the embodiment, the heat source water control device executes a water supply differential pressure acquisition step, an opening degree acquisition step, a target water supply differential pressure calculation step, and a water supply differential pressure control step. The water supply differential pressure acquisition step acquires the water supply differential pressure of the heat source water that is supplied from the heat source unit to the plurality of usage-side heat loads. The opening degree obtaining step obtains the opening degree of at least one valve from among the valves that are provided in the respective use side heat loads and adjust the supply amount of the heat source water supplied to the use side heat loads. The target water supply differential pressure calculating step is a target of the water supply differential pressure for setting the opening to a target value based on the water supply differential pressure acquired in the water supply differential pressure acquisition step and the opening acquired in the opening acquisition step. The target water supply differential pressure that is the value is calculated. The water supply pressure control step controls the water supply differential pressure based on the maximum water supply differential pressure that is the maximum value among the target water supply differential pressures calculated in the target water supply differential pressure calculation step.

The figure which shows an example of the heat source water control system of embodiment. The figure which shows an example of 1st Embodiment by the side of a load. The figure which shows an example of 2nd Embodiment by the side of a load. The figure which shows an example of a software structure of the heat source water control apparatus of embodiment. The figure which shows an example of the structure of the hardware of the heat-source water control apparatus of embodiment. The flowchart which shows an example of the target water pressure calculation operation | movement in the heat-source water control apparatus of embodiment. The flowchart which shows an example of the water supply temperature calculation operation | movement in the heat-source water control apparatus of embodiment. The flowchart which shows the 1st example of the water supply amount calculation operation | movement in the heat-source water control apparatus of embodiment. The flowchart which shows the 2nd example of the water supply amount calculation operation | movement in the heat-source water control apparatus of embodiment. The flowchart which shows an example of the motive power control operation | movement in the heat source water control apparatus of embodiment. The figure which shows an example of the 1st characteristic information of the air hung of embodiment. The figure which shows an example of the 1st characteristic information of the air hung of embodiment. The figure which shows an example of the 1st characteristic information of the air hung of embodiment. The figure which shows an example of the 2nd characteristic information of the air hung of embodiment. The figure which shows an example of the 2nd characteristic information of the air hung of embodiment. The figure which shows an example of the 2nd characteristic information of the air hung of embodiment.

  Hereinafter, a heat source water control method and a heat source water control device of an embodiment will be described with reference to the drawings. In each figure shown below, the same numerals are given about the same composition.

  First, an example of the heat source water control system according to the embodiment will be described with reference to FIG.

  In FIG. 1, a heat source water control system 1 includes a central monitoring device 10 used as a heat source water control device, a heat source machine 12, a differential pressure gauge 13, a bypass valve 14, an outgoing water temperature sensor 15, a water meter 16, and a return water temperature sensor. 17. It has the air han 20, which is a use side device, a valve 21, a thermometer 22, and an indicating controller 23. The heat source water control system 1 feeds the heat source water generated by the heat source device 12 to the plurality of air hans 20. In FIG. 1, the two air hangers 20, that is, the air han 20 a and the air han 20 b are illustrated, but the number of the air hangers 20 may be three or more. A valve 21, a thermometer 22, and an indicating controller 23 are installed for each air hanger 20. The air han 20a is provided with a valve 21a, a thermometer 22a and an indicating controller 23a, and the air han 20b is provided with a valve 21b, a thermometer 22b and an indicating controller 23b.

  The heat source device 12 is a module type chilling unit including a refrigeration cycle apparatus and a primary pump 123, for example, and includes a plurality of modules 120, an MC (Main controller) 121, and a GC (Group controller) 122. The MC 121 controls the water supply differential pressure of the heat source water supplied from the heat source machine 12. The water supply differential pressure is a differential pressure measured by the differential pressure gauge 13 and the return water returned to the heat source machine. The GC 122 controls the temperature of the heat source water sent from the heat source machine 12. The module 120 has one primary pump 123 for three air heat exchangers. The module 120 cools or heats the refrigerant by a compressor (not shown), and generates heat source water by heat exchange with water. The water temperature of the generated heat source water is measured by the outgoing water temperature sensor 15.

  The GC 122 instructs the module 120 on the temperature of the heat source water to be generated based on the water supply temperature instructed from the central monitoring device 10 and the water temperature measured by the outgoing water temperature sensor 15. The water temperature of the heat source water can be changed, for example, by changing the rotation speed or compression rate of a compressor that cools or heats the refrigerant. For example, in cooling, heat source water is cooled. When the water temperature of the heat source water is lowered during cooling, the power for driving the compressor increases. On the other hand, when the water temperature of the heat source water is raised during cooling, the power for driving the compressor can be reduced. Here, the GC 122 may instruct the water supply temperature of the heat source water, and the central monitoring apparatus 10 may collect information on the valve opening and transmit the information to the GC 122.

  The MC 121 controls the rotational speed of the primary pump 123 of the module 120 based on the water supply differential pressure instructed from the central monitoring device 10 and the differential pressure measured by the differential pressure gauge 13. In FIG. 1, in each of the plurality of modules 120, the primary side pump 123 is installed, and the amount of heat source water sent from the heat source unit 12 is the total amount of heat source water discharged from the primary side pump 123. MC121 controls the rotation speed of the primary side pump 123 of each heat source machine 12. FIG. For example, when the water supply differential pressure instructed from the central monitoring device 10 is low, the MC 121 decreases the discharge pressure by reducing the rotational speed of the primary pump 123. On the other hand, when the instructed water supply differential pressure is high, the MC 121 increases the discharge pressure by increasing the rotation speed of the primary pump 123. In addition, when the amount of heat source water supplied from the central monitoring device 10 is small, the MC 121 reduces the number of primary pumps 123 to reduce the amount of water supplied. On the other hand, when the instructed water supply amount is large, the MC 121 increases the number of primary pumps 123 to be operated to increase the water supply amount. Note that the MC 121 may operate a pump that keeps the water supply amount constant, or may operate a pump that makes the water supply differential pressure constant.

  The differential pressure gauge 13 measures the differential pressure between the pressure of the heat source water (outbound water) sent from the heat source device 12 and the pressure of the heat source water (return water) returned to the heat source device 12. The differential pressure measured by the differential pressure gauge 13 is referred to as “water supply differential pressure”. As described above, the MC 121 controls the operation of the primary pump 123 based on the water supply differential pressure measured by the differential pressure gauge 13. In order to control the operation of the primary pump 123, the water supply differential pressure is measured in the vicinity of the inlet / outlet of the heat source water of the heat source unit 12. On the other hand, since the air hung 20 is installed at a location away from the heat source unit 12, a pressure drop is generated due to the piping resistance from the heat source unit 12 to the air hung 20. The pressure drop to each air hanger 20 may differ depending on the piping resistance from the heat source unit 12 to the air hanger 20. For example, when the distance from the heat source unit 12 to the air hung 20a is short, the piping resistance from the heat source unit 12 to the air hung 20a is reduced, so the pressure drop of the heat source water supplied to the air hung 20a is reduced. On the other hand, when the distance from the heat source device 12 to the air hung 20b is long, the pressure drop increases because the pipe resistance increases. Therefore, the actual water pressure of the heat source water provided to each air hanger 20 is an estimated value.

  The bypass valve 14 adjusts the flow rate of the bypass water that flows through the bypass pipe installed near the entrance and exit of the heat source water of the heat source machine 12. When the opening degree of the bypass valve 14 is increased, the flow rate of the bypass water increases and the water supply differential pressure decreases. On the other hand, when the opening degree of the bypass valve 14 is reduced, the flow rate of the bypass water is reduced and the drop in the water supply differential pressure is reduced. For example, when the primary pump 123 is operated at a constant speed, a predetermined water flow rate is required to operate the pump. Even when the load of the air hung 20 is small and the amount of heat source water supplied to the air hung 20 is small, it is possible to secure the amount of water necessary for the operation of the primary pump 123 by the flow rate of the bypass water. Further, when the water supply differential pressure becomes too high, the water supply differential pressure can be reduced by increasing the opening degree of the bypass valve 14.

  The incoming water temperature sensor 15 measures the water supply temperature of the heat source water that is supplied from the heat source unit 12 to the air han 20a and the air han 20b. In addition, water supply temperature shall not change with piping etc. in the middle of water supply from the heat source machine 12 to the air hung 20. That is, the temperature of the heat source water sent from the heat source device 12 is assumed to be the same as the water temperature at the inlet of each air hanger 20. The measured water supply temperature is input to the GC 122.

  The water meter 16 measures the amount of heat source water fed from the heat source unit 12 to the air hanger 20. The amount of water supply is the total amount of heat source water supplied to the plurality of air hans 20. The measured water supply amount is input to the central monitoring apparatus 10 via the MC 121 and the GC 122.

  The return water temperature sensor 17 measures the return water temperature of the heat source water recirculated from the air han 20 to the heat source unit 12. The difference between the water supply temperature and the return water temperature varies depending on the heat exchange amount in the air hanger 20. The measured return water temperature is input to the GC 122. The heat exchange amount in the air hanger 20 will be described later. The air han 20 is a heat load on the heat source water, and is an air han, for example.

  The valve 21 adjusts the flow rate of the heat source water supplied to the air hanger 20 according to the valve opening. The thermometer 22 measures the temperature of the air hanger 20. The thermometer 22 can be composed of one or more sensors. The instruction controller 23 adjusts the valve opening degree of the valve 21 based on the temperature of the air hanger 20 measured by the thermometer 22. The valve opening degree of the valve 21 is input to the central monitoring device 10 and also to the GC 122.

  The valve 21 changes the flow rate by changing the valve opening. The characteristic of the change in flow rate with respect to the change in valve opening is called the flow rate characteristic of the valve. In a valve for adjusting the flow rate, a valve having a linear characteristic or an equal percentage characteristic is often used. The linear characteristic is a flow characteristic in which the flow rate changes in proportion to the valve opening. The equal percent characteristic is a characteristic in which the amount of change in the flow rate is the same as the flow rate before the change regardless of the position of the valve opening. That is, in the equal percentage characteristic, the rate of change of the flow rate is proportional to the flow rate.

<First Embodiment on Load Side>
Next, an example of the first embodiment on the load side will be described with reference to FIG. The load side is a configuration on the air han 20 side that uses heat source water generated by the heat source unit 12.

  In FIG. 2, the air han 20 includes a heat exchanger 201 and a blower 202 which are utilization side heat loads. The air han 20 is an air han, for example. The air han 20 includes both an external air conditioner and an air conditioner other than the external air conditioner. The external air conditioner adjusts the outside air by heat exchange. In the air conditioner other than the external air conditioner and the external air conditioner, heat exchange characteristics described later are different. In the following description, the air hung 20 includes an external air conditioner, and an air conditioner other than the external air conditioner is referred to as “CAV (Constant Air Volume)” or “VAV (Variable Air Volume)”. CAV maintains a constant air volume even if conditions such as room temperature change. VAV makes air volume variable according to conditions such as room temperature.

  Heat source water is supplied to the heat exchanger 201. A valve 21 is installed on the outlet side of the heat source water of the air hanger 20 to adjust the amount of heat source water. The heat exchanger 201 exchanges heat between the heat source water and air. The blower 202 blows the heat-exchanged air to the indoor unit.

  The sensor 111 measures the valve opening degree of the valve 21. The sensor 111 outputs a current of 4-20 mA based on the valve opening, for example. The valve opening degree of the sensor 111 is output to the central monitoring device 10. The central monitoring device 10 can acquire information on whether the valve 21 that has acquired the valve opening degree has linear characteristics or equal percent characteristics. For example, the central monitoring device 10 acquires and stores the flow rate characteristics of the valve 21 in advance.

  The sensor 112 measures the inlet pressure of the valve 21. The sensor 112 outputs the measured inlet pressure to the central monitoring device 10. The sensor 113 measures the outlet pressure of the valve 21. The sensor 113 outputs the measured outlet pressure to the central monitoring device 10.

  The sensor 114 measures the inlet temperature of the heat source water. The sensor 115 measures the outlet temperature of the heat source water. The sensor 116 measures the valve flow rate of the heat source water in the valve 21. The inlet temperature is the temperature of the heat source water before heat exchange supplied to the heat exchanger 201. The outlet temperature is the water temperature of the heat source water after heat exchange in the heat exchanger 201. The amount of heat exchange in the heat exchanger 201 can be calculated from the water temperature difference between the inlet temperature and the outlet temperature and the valve flow rate. The sensor 114 outputs the measured inlet temperature to the central monitoring device 10. The sensor 115 outputs the measured inlet temperature to the central monitoring device 10. The sensor 116 outputs the measured valve flow rate to the central monitoring device 10.

  The sensor 221 and the sensor 222 are an example of the thermometer 22 in FIG. Moreover, the ventilation temperature PID controller 231 and the indoor temperature PID controller 232 are examples of the instruction controller 23 of FIG. The sensor 221 measures the blowing temperature of the heat-exchanged air blown to the indoor unit. The sensor 221 outputs the measured blowing temperature to the blowing temperature PID controller 231. The sensor 222 measures the suction temperature in the indoor unit of the air blown by heat exchange in the heat exchanger 201. The sensor 222 outputs the measured suction temperature to the room temperature PID controller 232.

  The room temperature PID controller 232 calculates a target value for the blowing temperature based on the suction temperature measured by the sensor 222. The room temperature PID controller 232 outputs the calculated target value of the blowing temperature to the blowing temperature PID controller 231. The air temperature PID controller 231 adjusts the valve opening degree of the valve 21 based on the target value of the air temperature acquired from the indoor temperature PID controller 232 and the air temperature acquired from the sensor 221. By increasing the valve opening, the flow rate of the heat source water is increased, and the blowing temperature is changed as the heat exchange amount is increased.

  When the temperature or flow rate of the heat source water is changed, the blowing temperature changes in about 5 to 10 minutes due to heat exchange in the heat exchanger 201, for example. On the other hand, the suction temperature changes, for example, after 30 to 60 minutes after changing the temperature and flow rate of the heat source water, considering the heat capacity of the air in the air duct. In the first embodiment on the load side, since the air temperature acquired from the sensor 221 is used for adjusting the air temperature PID controller 231, the response speed by adjusting the opening degree of the valve 21 is improved, and the control is performed. It can be stabilized. Thereby, control of the central monitoring apparatus 10 which uses the valve opening degree mentioned later as an input value can be stabilized, and motive power can be reduced by preventing the overshoot of water supply differential pressure or water supply temperature.

  In addition, although the case where the number of indoor units is one is illustrated in FIG. 2, a plurality of indoor units may be connected to one air hanger 20 and air after heat exchange may be blown. When there are a plurality of indoor units, the sensor 222 may be installed for each indoor unit.

<Second Embodiment on Load Side>
Next, an example of the load-side second embodiment will be described with reference to FIG. The second embodiment on the load side is an embodiment different from the first embodiment on the load side in the method for adjusting the valve opening of the valve 21. In FIG. 3, the same components as those in FIG.

  The sensor 114 measures the inlet temperature of the heat source water in the heat exchanger. The sensor 115 measures the outlet temperature of the heat source water in the heat exchanger. The sensor 116 measures the valve flow rate of the heat source water in the valve 21. The sensor 114 outputs the measured inlet temperature to the central monitoring device 10 and the flow rate calculator 234. The sensor 115 outputs the measured outlet temperature to the central monitoring device 10 and the flow rate calculator 234. The sensor 116 outputs the measured valve flow rate to the central monitoring device 10 and the two-way valve flow rate PID controller 233.

  The room temperature PID controller 232 calculates a target value of the exchange heat quantity based on the suction temperature in the indoor unit acquired from the sensor 222. For example, when the difference between the set value of the indoor unit and the suction temperature is small during cooling, the indoor temperature PID controller 232 increases the target value of the exchange heat amount in order to lower the suction temperature.

  The flow rate calculator 234 passes the valve 21 based on the target value of the exchange heat quantity acquired from the indoor temperature PID controller 232 and the water temperature difference between the inlet temperature acquired from the sensor 114 and the outlet temperature acquired from the sensor 115. The target value of is calculated. The flow rate calculator 234 outputs the calculated target value of the flow rate of the valve 21 to the two-way valve flow rate PID controller 233. The two-way valve flow rate PID controller 233 adjusts the valve opening degree of the valve 21 based on the valve flow rate acquired from the sensor 116 and the target value of the flow rate of the valve 21 acquired from the flow rate calculator 234.

  The second embodiment on the load side measures the water temperature difference at the inlet and outlet of the heat source water in the heat exchanger instead of measuring the air blowing temperature of the air blown to the indoor unit measured in the first embodiment on the load side. This is different from the first embodiment on the load side. The change in the water temperature difference at the inlet / outlet of the heat exchanger after changing the temperature and flow rate of the heat source water further improves the response speed compared to the air temperature. For this reason, the response speed by adjusting the opening degree of the valve 21 is improved, the control can be further stabilized, and the power can be further reduced by preventing the overshoot of the water supply differential pressure and the water supply temperature.

  In FIG. 3, as in FIG. 2, the case where there is one indoor unit is illustrated. However, even if a plurality of indoor units are connected to one air hanger 20 and air after heat exchange is blown. Good. When there are a plurality of indoor units, the sensor 222 may be installed for each indoor unit.

  Next, the software configuration of the heat source water control apparatus according to the embodiment will be described with reference to FIG.

  4, the central monitoring device 10 includes a water supply differential pressure acquisition unit 51, an opening degree acquisition unit 52, a valve differential pressure acquisition unit 53, a flow rate acquisition unit 54, a target water supply differential pressure calculation unit 61, a generated power calculation unit 62, and a water supply. It has functions of a power calculation unit 63, a water temperature difference calculation unit 64, a water supply amount calculation unit 65, a load factor calculation unit 66, a water supply temperature calculation unit 67, a power control unit 71, a water supply differential pressure control unit 72, and a water supply temperature control unit 73. .

  The water supply differential pressure acquisition unit 51 to the flow rate acquisition unit 54 have a function of acquiring predetermined information from the outside of the central monitoring device 10. The target water supply differential pressure calculation unit 61 to the water supply temperature calculation unit 67 is a function that executes a predetermined calculation based on the acquired information. Further, the power control unit 71 to the water supply temperature control unit 73 are functions for executing control on the outside of the central monitoring device 10 based on the acquired information or the executed calculation result. In the present embodiment, each of these functions will be described as being realized by executing software (program). That is, FIG. 4 has shown the one aspect | mode of the heat source water control program which performs a heat source water control process.

  The water supply differential pressure acquisition unit 51 acquires the water supply differential pressure of the heat source water supplied from the heat source device 12 to the plurality of heat exchangers 201. The water supply differential pressure acquisition unit 51 acquires the water supply differential pressure from the differential pressure gauge 13. Note that “water supply differential pressure”, “opening”, “valve differential pressure”, and the like acquired in the central monitoring device 10 described below refers to information representing pressure and opening as electrical data. For example, “water supply differential pressure” or “opening degree” is information obtained by converting pressure or percentage information into information of 4-20 mA current or voltage of 0-5V. Such information can be acquired, for example, constantly or at predetermined time intervals. The acquired information can be stored in a storage unit (not shown).

    The opening acquisition unit 52 acquires the opening of the valve 21. The opening degree of the valve 21 is expressed as a percentage of 0 to 100%, for example. The valve 21 is provided on the outlet side of the heat source water of the heat exchanger 201 of each air han 20. The valve 21 adjusts the amount of heat source water supplied to the heat exchanger 201 according to the opening degree. The opening degree acquisition unit 52 acquires the opening degree of at least one valve from the valves 21 provided in each heat exchanger. For example, when a plurality of air hans are installed and there are a plurality of heat exchangers 201, the opening degree acquiring unit 52 acquires the opening degrees of all the valves 21. Further, the opening degree obtaining unit 52 may obtain the opening degree of the valve 21 as a representative. For example, when there are a plurality of air hans whose load states are approximate, the opening degree obtaining unit 52 obtains the opening degree of one valve 21 among the valves 21 installed in each air han. Further, for example, the opening degree of only the valve 21 having the maximum opening degree may be acquired.

  The valve differential pressure acquisition unit 53 acquires the differential pressure between the inlet and the outlet of the valve 21. The valve differential pressure acquisition unit 53 acquires a differential pressure from the difference between the pressure at the inlet of the valve 21 acquired from the sensor 112 and the pressure at the outlet of the valve 21 acquired from the sensor 113. The differential pressure varies depending on the opening degree of the valve 21 and the flow rate of the heat source water. For example, the differential pressure increases as the valve opening decreases or the heat source water flow increases. Here, the valve differential pressure acquisition unit 53 is not limited to acquiring the valve differential pressure calculated from the inlet and outlet pressures of the valve 21 acquired from the sensors 112 and 113, and cannot detect the pressure due to a sensor failure or the like. In this case, a predetermined set value may be recognized as the valve differential pressure. The predetermined set value may be, for example, a value calculated based on the opening degree of the valve 21 and the detected flow rate of the flow meter.

  The target water supply differential pressure calculation unit 61 sets the opening of the valve 21 to the target value based on the water supply differential pressure acquired by the water supply differential pressure acquisition unit 51 and the opening of the valve 21 acquired by the opening acquisition unit 52. Calculate the target water supply differential pressure. The target water supply differential pressure is a target value of the water supply differential pressure acquired from the differential pressure gauge 13. The target water supply differential pressure calculation unit 61 calculates the target water supply differential pressure in each valve when the opening degrees in the plurality of valves are acquired. The target opening degree can be acquired from the instruction controller 23, for example. Note that the target water supply differential pressure calculation unit 61 may calculate the target water supply differential pressure at a predetermined target opening.

  The water supply differential pressure control unit 72 controls the water supply differential pressure based on the maximum water supply differential pressure that is the maximum value among the target water supply differential pressures calculated by the target water supply differential pressure calculation unit 61. The control of the water supply differential pressure can be controlled, for example, by changing the number of operating primary pumps 123, the number of rotations of the pumps, or the opening degree of the bypass valve 14. For example, the water supply differential pressure control unit 72 varies the number of rotations of a motor that drives the primary pump 123 by a transmission means such as an inverter.

  The piping resistance in the piping path of the heat source water from the heat source device 12 to the air hanger 20 varies depending on each air hanger 20. The pipe resistance can be calculated based on the design drawing of the pipe path. The calculated pipe resistance can be expressed as a pipe resistance curve, for example. By preparing a piping resistance curve for each air hanger in advance, a pressure loss from the heat source machine 12 to the air hung 20 when the flow rate of the heat source water changes can be obtained, so target water feed when water is fed from the heat source machine 12 The differential pressure can be calculated. However, even if the piping resistance curve is calculated based on the piping distance or branching of the piping, the actual piping route includes piping joints and valves such as elbows and tees, so the calculated value and the measured value may deviate. There are many. Moreover, labor is required to perform detailed calculations. Therefore, when the measured value of the pipe resistance is larger than the calculated value, there is a possibility that sufficient water pressure cannot be obtained in the air hanger. On the other hand, when a margin is provided for the water supply differential pressure in the heat source unit 12, unnecessary power is required in the operation of the primary pump 123 or the like.

  Next, a calculation method of the target water supply differential pressure in the target water supply differential pressure calculation unit 61 will be described. The target water supply differential pressure calculation unit 61 calculates the target water supply differential pressure based on the range ability of the valve and the flow rate characteristic of the valve.

  The rangeability of a valve is the ratio of the maximum flow rate to the minimum flow rate that can be adjusted by the valve. A valve having a high range ability has a wide control range in which the flow rate can be controlled. The target water supply differential pressure is calculated for each flow rate characteristic of the valve.

<When flow rate characteristic is equal percentage characteristic>
The target water supply differential pressure calculation unit 61 first calculates the target differential pressure deviation dΔPV by equation (1), and then calculates the target water supply differential pressure Ps by equation (2).

dΔPV = ΔPV {ρ ^{2 (σ−σs)} −1} (1)
(However, ρ: Range ability, σ: Opening, σs: Target opening, ΔPV: Valve differential pressure)
Ps = P + dΔPV (2)
(However, P: Target water supply differential pressure Ps set in the previous calculation)

<When the flow characteristics are linear characteristics>
The target water supply differential pressure calculation unit 61 first calculates a target differential pressure deviation dΔPV by equation (3), and then calculates a target water supply differential pressure Ps by equation (2).

dΔPV = ΔPV [[{1 / ρ + (1-1 / ρ) σ} / {1 / ρ + (1-1 / ρ) σs}] ² −1]
... Formula (3)
(However, ρ: Range ability, σ: Opening, σs: Target opening, ΔPV: Valve differential pressure)
Ps = P + dΔPV (2)
(However, P: Target water supply differential pressure Ps set in the previous calculation)

  In this embodiment, since the opening degree σ and the valve differential pressure ΔPV in the valve 21 are acquired and the target water supply differential pressure Ps is calculated, the operation and the like of the primary pump 123 are controlled with the necessary and sufficient water supply differential pressure. Can do. Further, it is possible to prevent hunting of the pump rotation speed and the opening degree of the valve 21 due to excessive target water supply differential pressure. Further, since the flow rate characteristic and the range ability are fixed values common to the valve 21 type regardless of the diameter (size) of the valve 21, the target water supply differential pressure Ps can be easily calculated.

  The generated power calculation unit 62 calculates generated power information indicating the relationship between the water supply temperature of the heat source water and the generated power for generating the heat source water. The heat source unit 12 generates heat source water by cooling or heating the refrigerant compressed / conveyed by the compressor of the refrigeration cycle apparatus and exchanging heat with the heat source water, for example. The generation power for generating the heat source water is determined by the temperature of the heat source water to be generated and the flow rate of the heat source water. For example, in cooling, the change in sensible heat of the heat source water increases to lower the temperature of the heat source water, so cooling of the refrigerant is necessary to increase the amount of heat exchange from the cooled refrigerant, increasing the generation power Let On the other hand, in cooling, when the temperature of the heat source water is increased, the change in the sensible heat of the heat source water is reduced and the generated power is reduced. The generated power calculation unit 62 calculates generated power information indicating the relationship between the water supply temperature of the heat source water and the generated power for generating the heat source water, based on the heat source water generation capability prepared in advance in the heat source device 12. For example, when the horizontal axis is the water supply temperature and the vertical axis is the generation power, the relationship between the water supply temperature and the generation power is the relationship between the water supply temperature and the generation power for generating the heat source water. As the amount of heat increases, the rate of increase in generated power increases.

  The water supply power calculation unit 63 calculates water supply power information indicating the relationship between the water supply temperature and the water supply power for supplying the heat source water. The water supply power calculation unit 63 calculates the generated power information based on the maximum water supply differential pressure calculated by the target water supply differential pressure calculation unit and the change in the water supply amount required when the water supply temperature of the heat source water is changed. .

  The water supply power can be obtained by the product of the water supply differential pressure and the water supply amount. As described above, the amount of heat exchange from the heat source water to the air in the heat exchanger 201 is determined by the water temperature difference at the inlet / outlet of the heat exchanger 201 and the amount of heat source water supplied to the heat exchanger. For example, when performing control to keep the heat exchange amount constant, the amount of heat source water is decreased if the water temperature difference is increased, and the amount of heat source water is increased if the water temperature difference is decreased. Therefore, when the difference in the water supply temperature of the heat source water in the heat exchanger 201 determined by the water supply temperature becomes small, the amount of water supply increases and the water supply power increases. On the other hand, when the water supply temperature difference increases, the water supply amount decreases and the water supply power decreases. For example, when the horizontal axis is the water supply temperature and the vertical axis is the water supply power, the ratio between the water supply temperature and the water supply power is such that the rate of decrease in the water supply power increases as the temperature difference of the heat source water to be supplied increases. Details of the water supply power calculation unit 63 will be described below.

  The water supply power calculation unit 63 includes a water temperature difference calculation unit 64, a water supply amount calculation unit 65, and a load factor calculation unit 66.

  The water temperature difference calculation unit 64 acquires the inlet temperature and the outlet temperature of the heat source water in each heat exchanger, and calculates the water temperature difference between the inlet temperature and the outlet temperature. The inlet temperature of the heat source water in the heat exchanger can be obtained from the sensor 114. The outlet temperature of the heat source water in the heat exchanger can be obtained from the sensor 115. The water temperature difference calculation unit 64 calculates a water temperature difference from the acquired inlet temperature and outlet temperature. As described above, the water temperature difference of the heat source water is proportional to the amount of heat exchange in the heat exchanger when the flow rate is constant. On the other hand, the water temperature difference is inversely proportional to the flow rate when the heat exchange amount is constant. Here, in addition to the above, the average water temperature difference of the plurality of heat exchangers may be calculated from the going-water temperature sensor 15 and the return water temperature sensor 17 and may be the water temperature difference of the heat exchanger.

<Water temperature difference-Calculation of water supply amount using water temperature difference variation characteristics>
Based on the characteristic information indicating the characteristics of the air han including the heat exchanger indicated by the change amount of the water temperature difference with respect to the change of the water temperature difference and the change amount of the water supply temperature of the heat source water, the water supply amount calculation unit 65 performs each heat exchange. Calculate the amount of change in the flow rate of the heat source water supplied to each heat exchanger when the amount of heat exchange in the heat exchanger is constant, and sum the amount of change in the flow rate in all heat exchangers to change the amount of water delivered Is calculated.

  Characteristic information indicating the characteristics of the air hanger is prepared in advance. The characteristic information is, for example, information represented by a graph in which the horizontal axis indicates the water temperature difference and the vertical axis indicates the amount of change in the water temperature difference. When the horizontal axis is selected based on the characteristic information, the amount of change in the temperature difference when the temperature of the heat source water changes by 1 ° C. can be obtained. In addition, the specific example of the characteristic view by a water temperature difference is mentioned later. The characteristic information is stored, for example, in a storage unit (not shown) of the central monitoring device 10 and read from the water supply amount calculation unit 65.

  The water temperature difference is inversely proportional to the flow rate when the heat exchange amount is constant. Therefore, when the water temperature difference is changed, when the change amount of the water temperature difference is changed, the flow rate is changed in proportion to the change amount. The water supply amount calculation unit 65 calculates the water supply amount by summing the amount of change in the flow rate with respect to the change in the water temperature difference in each heat exchanger.

<Calculation of the amount of water delivered using the load factor-water temperature difference variation characteristic>
The flow rate acquisition unit 54 acquires the flow rate of the heat source water supplied to each heat exchanger from the sensor 116. The flow rate of the heat source water supplied to the heat exchanger is adjusted by the opening degree of the valve 21.

  The load factor calculation unit 66 calculates the load factor of each heat exchanger based on the flow rate acquired by the flow rate acquisition unit 54 and the water temperature difference calculated by the water temperature difference calculation unit 64. The load factor is an actual heat exchange amount when the maximum heat exchange amount capable of heat exchange in the heat exchanger 201 is 100%. The amount of heat exchange in the heat exchanger can be determined by the product of the water temperature difference and the flow rate. When the flow rate is constant, the heat exchange amount increases as the water temperature difference increases, and decreases as the water temperature difference decreases.

  The water supply amount calculation unit 65 includes characteristic information indicating the characteristics of the air handling unit including the heat factor indicated by the load factor calculated by the load factor calculation unit 66, and the change amount of the water temperature difference with respect to the change of the load factor, and the heat source Based on the amount of change in water supply temperature, calculate the amount of change in flow rate when the heat exchange amount in each heat exchanger is constant, and sum the amount of change in flow rate in all heat exchangers. The amount of change is calculated.

  Characteristic information indicating the characteristics of the air hanger is prepared in advance. The characteristic information is, for example, information represented by a graph with the load factor on the horizontal axis and the amount of change in the water temperature difference on the vertical axis. When the horizontal axis is selected based on the characteristic information, the amount of change in temperature difference when the temperature of the heat source water changes by 1 ° C. can be obtained at the load factor. A specific example of the characteristic diagram based on the load factor will be described later. The characteristic information is stored, for example, in a storage unit (not shown) of the central monitoring device 10 and read from the water supply amount calculation unit 65.

  The load factor is proportional to the flow rate when the heat exchange amount is constant. Accordingly, when the load factor is changed, if the amount of change in the water temperature difference changes, the flow rate changes in inverse proportion to the amount of change. The water supply amount calculation unit 65 calculates the water supply amount by summing the amount of change in the flow rate with respect to the change in the water temperature difference in each heat exchanger.

  The water supply temperature calculation unit 67 is based on the generated power information calculated by the generated power calculation unit 62 and the water supply power information calculated by the water supply power calculation unit 63, and the water supply temperature at which the sum of the generated power and the water supply power is minimized. Is calculated. In cooling, when the temperature of the heat source water decreases, the generation power required for cooling increases, while the water supply power decreases. In heating, when the temperature of the heat source water rises, the generation power required for heating increases, while the water supply power decreases. Therefore, when the generation power and the water supply power are summed, there is a water supply temperature at which the total value is minimum. The water supply temperature calculation unit 67 can calculate (select) the water supply temperature at which the total value is minimum by calculating the total value at each water supply temperature.

  The water supply temperature calculation unit 67 does not calculate a water temperature having a water temperature difference lower than the lower limit value as the water supply temperature. In the water supply temperature calculation unit 67, the lower limit value based on the characteristic information indicating the characteristics of the air handling unit including the heat exchanger indicated by the change amount of the water temperature difference with respect to the change in the water temperature difference, and the water supply temperature calculated in the water supply temperature calculation unit Is calculated. In the characteristic information indicating the characteristics of the air handling unit including the heat exchanger indicated by the change amount of the water temperature difference, the lower limit value of the water temperature difference is the limit of the heat exchange capability of the heat exchanger 201. For this reason, the water supply temperature from which a water temperature difference becomes below a lower limit is excluded from calculation objects.

  In addition, the water supply temperature calculation unit 67 does not calculate a water temperature higher than the outside air dew point temperature during cooling as the water supply temperature, and dew condensation does not occur at a water temperature higher than the outside air dew point temperature during cooling, so air cannot be dehumidified. Note that the water supply temperature calculation unit 67 may calculate a water supply temperature that is equal to or lower than a predetermined temperature with respect to the outside air dew point temperature during cooling.

  The power control unit 71 controls the generation power and the water supply power of the heat source water based on the water supply temperature calculated by the water supply temperature calculation unit 67. In the water supply temperature control unit 73, the power control unit 71 controls the temperature of the heat source water generated by the heat source machine 12 so that the total value of the generation power and the water supply power becomes the minimum. The water supply temperature control unit 73 controls the water supply temperature of the heat source water by changing the rotation speed and compression rate of the compressor that cools or heats the refrigerant.

  Further, the power control unit 71 controls the water supply differential pressure at the water supply temperature in the water supply differential pressure control unit 72. Thereby, the power control unit 71 can control the heat source water that minimizes the total value of the generated power and the water supply power.

  In FIG. 4, the water supply differential pressure acquisition unit 51, the opening degree acquisition unit 52, the valve differential pressure acquisition unit 53, the flow rate acquisition unit 54, the target water supply differential pressure calculation unit 61, and the generated power calculation that the central monitoring device 10 has. 62, water supply power calculation unit 63, water temperature difference calculation unit 64, water supply amount calculation unit 65, load factor calculation unit 66, water supply temperature calculation unit 67, power control unit 71, water supply differential pressure control unit 72, and water supply temperature control unit 73 The case where each function is realized by software was explained. However, the one or more functions of the central monitoring device 10 may be realized by hardware.

  In addition, each of the functions of the central monitoring device 10 may be implemented by dividing one function into a plurality of functions. Further, each of the above functions that the central monitoring apparatus 10 has may be implemented by integrating two or more functions into one function.

  The central monitoring device 10 may be a device realized by a single housing or a system realized by a plurality of devices connected via a network or the like. For example, the central monitoring device 10 may be a device such as a server device, a notebook PC, a tablet PC, a PDA, or a smartphone, and is a virtual device such as a cloud service provided by a cloud computing system. May be.

  Moreover, you may make it implement | achieve one or more functions of the said each function of the central monitoring apparatus 10 in another apparatus. That is, the central monitoring apparatus 10 does not have to have all the functions described above, and may have some functions.

  Further, a part or all of the functions of the central monitoring apparatus 10 may be provided in the MC or GC. For example, a water supply differential pressure acquisition unit 51, an opening degree acquisition unit 52, a valve differential pressure acquisition unit 53, a flow rate acquisition unit 54, a target water supply differential pressure calculation unit 61, a generated power calculation unit 62, a water supply power calculation unit 63, a water temperature difference calculation Functions of the unit 64, the water supply amount calculation unit 65, the load factor calculation unit 66, the water supply temperature calculation unit 67, the power control unit 71, the water supply differential pressure control unit 72, the water supply temperature control unit 73, and the like are provided in the MC 121 and the GC 122. May be. Further, the flow rate characteristics of the valve 21 may be acquired and stored by the MC 121 or the GC 122 instead of the central monitoring device 10. Moreover, you may perform a part of operation | movement of a heat-source control system using the control function with which MC121 or GC122 is equipped. Thereby, the operation | movement of the whole system can be performed favorably, without expanding the function of the central monitoring apparatus 10 more than necessary.

  Moreover, although the heat source water control apparatus in this embodiment is demonstrated as the central monitoring apparatus 10, it is good also as a heat source water control apparatus including at least any one of MC and GC. That is, you may make MC and GC function as a heat source water control apparatus.

  Next, the hardware configuration of the central monitoring apparatus 10 according to the embodiment will be described with reference to FIG.

  In FIG. 5, the central monitoring apparatus 10 includes a CPU 101, a RAM (Random Access Memory) 102, a ROM (Read Only Memory) 103, an HDD 104, an operation unit 105, a display unit 106, and a communication I / F (Interface) 107.

  The central monitoring device 10 can be a general-purpose computer such as a desktop PC or a server device. The central monitoring device 10 may be a control device dedicated to a heat source device or an industrial control device such as a PLC (Programmable Logic Controller). Moreover, the central monitoring apparatus 10 may share hardware with MC121 or GC122. The central monitoring apparatus 10 executes the heat source water control program described in FIG.

  The CPU 101 controls the central monitoring apparatus 10 by executing a worker training program stored in the RAM 102, ROM 103, or HDD 104. The heat source water control program is acquired from, for example, a recording medium that records the heat source water control program or a server that provides the program via a network, installed in the HDD 104, and stored in the RAM 102 so as to be readable from the CPU 101.

  The operation unit 105 is, for example, a keyboard, a mouse, or a switch that enables an operation input by an operator of the central monitoring apparatus 10. The display unit 106 has a display function for displaying information to an operator, for example, a liquid crystal display or a lamp. Note that the operation unit 105 and the display unit 106 may be, for example, a touch panel having an operation display function.

  The communication I / F 107 controls communication with other devices via wireless LAN communication, wired LAN communication, infrared communication, short-range wireless communication, and the like. The communication I / F 107 controls communication with the cloud server 91 via the PLC 124, the MC 121, the GC 122, or the network 9, for example. The PLC 124 relays information on pressure acquired from the sensors 111 to 116, for example. For example, the cloud server 91 monitors or records the operation state of the central monitoring device 10.

  Next, the target water pressure calculation operation in the central monitoring apparatus 10 of the embodiment will be described with reference to FIG. The operations of the flowcharts illustrated in FIGS. 6 to 10 are operations performed by the functions of the central monitoring apparatus 10 described with reference to FIG. 4, and can be realized by the CPU 101 executing the heat source water control program. Each operation will be described as being performed by the central monitoring apparatus 10.

  In FIG. 6, the central monitoring device 10 determines whether or not to start a target water supply differential pressure calculation operation (step S <b> 11). Whether or not to start the operation of calculating the target water supply differential pressure is determined by, for example, an instruction from the operator of the central monitoring apparatus 10 or an instruction from a timer set with a predetermined time interval. When it is determined that the calculation operation of the target water supply differential pressure is not started (step S11: NO), the central monitoring device 10 repeats the process of step S11 and waits for the start of the calculation operation.

  On the other hand, when it is determined that the calculation operation of the target water supply differential pressure is started (step S11: YES), the central monitoring device 10 starts the operation of the water supply pump in the initial state (step S12). The operation in the initial state is, for example, an operation under preset conditions such as the number of operating pumps, the number of rotations of the pump, and the opening of the valve.

  After executing the process of step S12, the central monitoring apparatus 10 acquires the water supply differential pressure (step S13). Acquisition of the water supply differential pressure can be executed by the water supply differential pressure acquisition unit 51 acquiring the water supply differential pressure of the heat source water supplied from the heat source device 12 to the plurality of heat exchangers 201 from the differential pressure gauge 13.

  After executing the process of step S13, the central monitoring apparatus 10 acquires the opening degree (step S14). The opening degree can be acquired by the opening degree obtaining unit 52 obtaining the opening degree of the valve 21 provided on the outlet side of the heat source water of the heat exchanger 201 of each air hanger 20 from the sensor 111. The opening degree acquisition unit 52 acquires the opening degree of at least one valve from the valves 21 provided in each heat exchanger.

  After executing the process of step S14, the central monitoring apparatus 10 acquires the valve differential pressure (step S15). The valve differential pressure can be acquired by the valve differential pressure acquisition unit 53 acquiring a differential pressure from the difference between the pressure at the inlet of the valve 21 acquired from the sensor 112 and the pressure at the outlet of the valve 21 acquired from the sensor 113. .

  If the pressure at the inlet or outlet of the valve 21 cannot be measured due to a failure of the sensors 112 and 113 or when the sensor itself is not installed, the predetermined set value may be recognized as the valve differential pressure. Good. The predetermined set value may be, for example, a value determined in advance in a data table or the like, or a value calculated based on the opening degree of the valve 21 and the detected flow rate of the flow meter.

  After executing the process of step S15, the central monitoring apparatus 10 calculates the target water supply differential pressure (step S16). The target water supply differential pressure is calculated based on the water supply differential pressure acquired by the water supply differential pressure acquisition unit 51 and the opening degree of the valve 21 acquired by the opening degree acquisition unit 52. This can be executed by calculating the target water supply differential pressure.

  After executing the process of step S16, the central monitoring apparatus 10 stores the target water supply differential pressure (step S17). The storage of the target water supply differential pressure can be executed, for example, by the target water supply differential pressure calculation unit 61 storing the calculated target water supply differential pressure in the HDD 104 or the like.

  After executing the process of step S17, the central monitoring apparatus 10 determines whether or not to finish calculating the target water supply differential pressure (step S18). The determination of whether or not to end the calculation of the target water supply differential pressure may be ended, for example, when a predetermined time has elapsed from the start of the calculation of the target water supply differential pressure and the calculated numerical value becomes stable. When it is determined that the calculation of the target water supply differential pressure is not finished (step S18: NO), the central monitoring apparatus 10 returns to the process of step S13 and repeats the calculation of the target water supply differential pressure. On the other hand, when it is determined that the calculation of the target water supply differential pressure is to be ended (step S18: YES), the central monitoring apparatus 10 ends the process shown in the slow chart.

  Next, the water supply temperature calculation operation in the central monitoring apparatus 10 according to the embodiment will be described with reference to FIG.

  In FIG. 7, the central monitoring device 10 determines whether or not to start the calculation operation of the water supply temperature (step S21). Whether or not to start the operation of calculating the water supply temperature is determined by, for example, an instruction from the operator of the central monitoring apparatus 10 or an instruction from a timer set with a predetermined time interval. When it is determined that the calculation operation of the water supply temperature is not started (step S21: NO), the central monitoring apparatus 10 repeats the process of step S21 and waits for the start of the calculation operation.

  On the other hand, if it is determined that the operation for calculating the water supply temperature is started (step S21: YES), the central monitoring apparatus 10 calculates the generated power (step S22). The generation power can be calculated by the generation power calculation unit 62 calculating generation power information indicating the relationship between the water supply temperature of the heat source water and the generation power for generating the heat source water. The generation power is determined by the temperature of the heat source water to be generated and the flow rate of the heat source water. The generated power calculation unit 62 calculates generated power information indicating the relationship between the water supply temperature of the heat source water and the generated power for generating the heat source water, based on the heat source water generation capability prepared in advance in the heat source device 12.

  After executing the process of step S22, the central monitoring apparatus 10 calculates water supply power (step S23). The calculation of the water supply power can be executed by the water supply power calculation unit 63 calculating water supply power information indicating the relationship between the water supply temperature and the water supply power for supplying the heat source water. The water supply power calculation unit 63 calculates the generated power information based on the maximum water supply differential pressure calculated by the target water supply differential pressure calculation unit and the change in the water supply amount required when the water supply temperature of the heat source water is changed. .

  After executing the process of step S23, the central monitoring apparatus 10 calculates the water supply temperature (step S24). The water supply temperature is calculated based on the generated power information calculated by the generated power calculation unit 62 and the generated power information calculated by the generated power calculation unit 63. This can be done by calculating the water supply temperature at which the minimum is reached. The water supply temperature calculation unit 67 calculates (selects) the water supply temperature at which the total value is minimum by calculating the total value at each water supply temperature.

  After executing the process of step S24, the central monitoring apparatus 10 stores the water supply temperature (step S25). The storage of the water supply temperature can be executed, for example, by the water supply temperature calculation unit 67 storing the calculated water supply temperature in the HDD 104 or the like.

  After executing the process of step S25, the central monitoring apparatus 10 determines whether or not to end the calculation of the water supply temperature (step S26). The determination as to whether or not to end the calculation of the water supply temperature may be ended, for example, when a predetermined time has elapsed from the start of the calculation of the water supply temperature and the calculated numerical value has stabilized. If it is determined not to end the calculation of the water supply temperature (step S26: NO), the central monitoring apparatus 10 returns to the process of step S22 and repeats the calculation of the water supply temperature. On the other hand, when it is determined that the calculation of the water supply temperature is to be ended (step S26: YES), the central monitoring apparatus 10 ends the process shown in the slow chart.

  Next, the 1st example of the water supply amount calculation operation | movement in the heat-source water control apparatus of embodiment is demonstrated using FIG. The first example of the water supply amount calculation operation is the operation related to the calculation of the water supply amount using the water temperature difference and the water temperature difference change amount characteristic described above.

  In FIG. 8, the central monitoring device 10 determines whether or not to start the operation for calculating the water supply amount (step S31). Whether or not to start the operation of calculating the water supply amount is determined by, for example, an instruction from the operator of the central monitoring apparatus 10 or an instruction from a timer set with a predetermined time interval. When it is determined that the calculation operation of the water supply amount is not started (step S31: NO), the central monitoring apparatus 10 repeats the process of step S31 and waits for the start of the calculation operation.

  On the other hand, when it is determined to start the operation for calculating the water supply amount (step S31: YES), the central monitoring apparatus 10 calculates the water temperature difference (step S32). The water temperature difference is calculated by the water temperature difference calculating unit 64 acquiring the inlet temperature and the outlet temperature of the heat source water in each heat exchanger, the inlet temperature acquired from the sensor 114, and the temperature of the outlet temperature acquired from the sensor 115. This can be done by calculating the water temperature difference from the difference. Here, in addition to the above, the average water temperature difference of the plurality of heat exchangers may be calculated from the incoming water temperature sensor 15 and the return water temperature sensor 17 to obtain the water temperature difference of the heat exchanger.

  After performing the process of step S32, the central monitoring apparatus 10 calculates the water supply amount (step S33). In the first example of the water supply amount calculation operation, the calculation of the water supply amount includes the characteristic information indicating the characteristics of the air han including the heat exchanger indicated by the change amount of the water temperature difference with respect to the change of the water temperature difference. The amount of change in the flow rate of the heat source water supplied to each heat exchanger when the amount of heat exchange in each heat exchanger is made constant based on the amount of change in the water supply temperature of the heat source water is calculated. It can be performed by calculating the amount of change in the amount of water supplied by summing the amount of change in the flow rate in the heat exchanger.

  After performing the process of step S33, the central monitoring apparatus 10 stores the water supply amount (step S34). The storage of the water supply amount can be executed, for example, when the water supply amount calculation unit 65 stores the calculated water supply amount in the HDD 104 or the like.

  After performing the process of step S34, the central monitoring apparatus 10 determines whether or not to end the calculation of the water supply amount (step S35). The determination as to whether or not to end the calculation of the water supply amount may be ended when, for example, a predetermined time has elapsed from the start of the calculation of the water supply amount and the calculated numerical value has stabilized. When it is determined not to end the calculation of the water supply amount (step S35: NO), the central monitoring apparatus 10 returns to the process of step S32 and repeats the calculation of the water supply amount. On the other hand, when it is determined that the calculation of the water supply amount is to be ended (step S35: YES), the central monitoring apparatus 10 ends the process shown in the slow chart.

  Next, the 2nd example of the water supply amount calculation operation | movement in the heat-source water control apparatus of embodiment is demonstrated using FIG. The second example of the water supply amount calculation operation is the operation related to the calculation of the water supply amount using the load factor and the water temperature difference change amount characteristic described above. Note that, in the second example of the water supply amount calculation operation, the same processes as those in the first example of the water supply amount calculation operation are denoted by the same step numbers and description thereof is omitted.

  In FIG. 9, after performing the process of step S32, the central monitoring apparatus 10 calculates a load factor (step S41). For calculating the load factor, the load factor calculating unit 66 calculates the load factor of each heat exchanger based on the flow rate acquired by the flow rate acquiring unit 54 and the water temperature difference calculated by the water temperature difference calculating unit 64. Can be executed.

  After performing the process of step S41, the central monitoring apparatus 10 calculates the water supply amount (step S42). In the second example of the water supply amount calculating operation, the calculation of the water supply amount is indicated by the water supply amount calculating unit 65 by the load factor calculated by the load factor calculating unit 66 and the change amount of the water temperature difference with respect to the change of the load factor. Based on the characteristic information indicating the characteristics of the air handling unit including the heat exchanger and the amount of change in the water supply temperature of the heat source water, the amount of change in the flow rate when the amount of heat exchange in each heat exchanger is constant is calculated. This can be performed by calculating the amount of change in the amount of water supplied by summing the amount of change in the flow rate in all heat exchangers. The water supply amount calculation unit 65 calculates the water supply amount by summing the amount of change in the flow rate with respect to the change in the water temperature difference in each heat exchanger.

  Next, the power control operation in the heat source water control apparatus of the embodiment will be described using FIG.

  In FIG. 10, the central monitoring apparatus 10 determines whether or not to start the power control operation (step S51). Power control is control for generating and supplying heat source water so that power is minimized. Whether or not to start the power control operation is determined by, for example, an instruction from the operator of the central monitoring apparatus 10 or an instruction from a timer set with a predetermined time interval. If it is determined that the power control operation is not started (step S51: NO), the central monitoring apparatus 10 repeats the process of step S51 and waits for the start of the calculation operation.

  On the other hand, when it is judged that the operation | movement of motive power control is started (step S51: YES), the central monitoring apparatus 10 acquires water supply temperature (step S52). Acquisition of water supply temperature can be performed by acquiring the water supply temperature memorize | stored by the process of step S25.

  After performing the process of step S52, the central monitoring apparatus 10 acquires the water supply amount (step S53). Acquisition of the water supply amount can be executed by acquiring the water supply amount stored in the process of step S34.

  After executing the process of step S53, the central monitoring apparatus 10 acquires the water supply differential pressure (step S54). Acquisition of the water supply differential pressure can be performed by acquiring the water supply differential pressure stored in the process of step S17.

  After performing the process of step S54, the central monitoring apparatus 10 outputs the instruction values of the water supply temperature, the water supply amount, and the water supply differential pressure acquired in steps S52 to S54.

  The central monitoring device 10 outputs an indication value of the water supply temperature to the GC 122. The GC 122 controls the module 120 so that the water temperature measured by the outgoing water temperature sensor 15 becomes the instruction value based on the instruction value of the water supply temperature of the heat source water instructed from the central monitoring device 10. The central monitoring apparatus 10 may further output an instruction value for the amount of water supplied to the GC 122. The product of the water supply temperature and the water supply amount becomes a load for generating heat source water in the module 120.

  Moreover, the central monitoring apparatus 10 outputs the instruction value of the water supply differential pressure to the MC 121. The MC 121 controls the primary pump 123 so that the differential pressure measured by the differential pressure gauge 13 becomes the indicated value based on the indicated value of the water supply differential pressure indicated by the central monitoring device 10. MC121 controls the rotation speed of the primary side pump 123, and the opening degree of the bypass valve 14, for example. The central monitoring device 10 may further output an instruction value for the amount of water supplied to the MC 121. The MC 121 controls, for example, the number of primary pumps 123 (modules 120) that operate according to the indicated value of the water supply amount.

  After executing the process of step S55, the central monitoring apparatus 10 determines whether or not to end the power control operation (step S56). The determination as to whether or not to end the power control operation is made based on whether or not the operator of the central monitoring device 10 has been operated when the water supply of the heat source water is ended, for example. The operation of the power control may be ended when switching to the operation of the conventional heat source machine 12 that does not perform power control, for example. In the present embodiment, the case where the water supply temperature, the water supply amount, and the water supply differential pressure are all controlled has been shown. However, the central monitoring device 10 may output only the instruction value of the water supply differential pressure, for example. Good. In this case, the water supply temperature of the heat source water is operated at a constant value.

  If it is determined that the power control operation is not to be ended (step S56: NO), the central monitoring apparatus 10 returns to the process of step S52 and repeats the power control operation. On the other hand, when it is determined that the power control operation is to be ended (step S56: YES), the central monitoring apparatus 10 ends the processing shown in the slow chart.

  Next, the first characteristic information of the air hung according to the embodiment will be described with reference to FIG. The first characteristic information of the air han is the water temperature difference and the water temperature difference variation characteristic information in the air han described above.

  FIG. 11A shows CAV characteristic information when the air hanger is other than an external air conditioner and during cooling. The horizontal axis represents the temperature difference (water temperature difference) at the inlet / outlet of the air han of the heat source water. The vertical axis represents the amount of change in the temperature difference (water temperature difference) at the inlet / outlet of the airhan of the heat source water. The water temperature difference is proportional to the amount of heat exchange. That is, FIG. 11A shows the amount of change in the heat exchange amount when the temperature of the heat source water is changed by 1 ° C. with respect to the heat exchange amount. The amount of change in the water temperature difference increases as the water temperature difference decreases, and the amount of change does not change when the water temperature difference is a certain value or less. FIG. 11A shows that the change amount becomes a constant value when the water temperature difference is about 11 ° C. or less. That is, when the water temperature difference is about 11 ° C. or less, even if the temperature of the heat source water is changed, the amount of change in the temperature difference due to heat exchange is the same, which is the limit of the performance of the heat exchanger. When calculating the feed water temperature of the heat source water in the CAV during cooling, the temperature difference should not be 11 ° C. or less.

  FIG. 11B shows the characteristic information of the VAV in the case where the air han is other than the external air conditioner and is cooled. Further, FIG. 11C shows characteristic information during cooling when the air hanger is an external air conditioner. In FIGS. 11A, 11B, and 11C, the characteristic information of the air han during cooling is shown, but similar characteristic information is also prepared during heating.

  Next, the second characteristic information of the air hung according to the embodiment will be described with reference to FIG. The second characteristic information of the air han is the above-described load factor and water temperature difference variation characteristic information in the air han.

  FIG. 12A shows CAV characteristic information when the air hanger is other than an external air conditioner and is cooled. The horizontal axis represents the load factor of the air han. The vertical axis represents the amount of change in the temperature difference (water temperature difference) at the inlet / outlet of the airhan of the heat source water. The load factor is calculated by the load factor calculator 66. That is, the load factor is a numerical value of 0 (1%) to 1 (100%) calculated by the water temperature difference and the flow rate. The amount of change in the heat exchange amount when the temperature of the heat source water is changed by 1 ° C. increases according to the load factor. In other words, the amount of change in the water temperature difference when the temperature of the heat source water is changed by 1 ° C. increases according to the load factor.

  FIG. 12B shows the characteristic information of the VAV in the case where the air han is other than the external air conditioner and during cooling. FIG. 12C shows characteristic information during cooling when the air hanger is an external air conditioner. In FIGS. 12A, 12B, and 12C, the characteristic information of the air han during cooling is shown, but similar characteristic information is also prepared during heating.

  As described above, this embodiment is a heat source water control method, in which a heat source water control device acquires a water supply differential pressure in which heat source water is supplied from a heat source unit to a plurality of usage-side heat loads. An opening degree obtaining step for obtaining an opening degree of at least one of the valves provided in each of the use side heat loads and adjusting a supply amount of heat source water supplied to the use side heat load; Based on the valve differential pressure acquisition step for acquiring the differential pressure between the inlet and the outlet of the water, the water supply differential pressure acquired in the water supply differential pressure acquisition step, and the opening acquired in the opening acquisition step, the opening is set to the target value. The target water supply differential pressure calculating step for calculating the target water supply differential pressure, which is the target value of the water supply differential pressure, and the maximum water supply that is the maximum value among the target water supply differential pressure calculated in the target water supply differential pressure calculation step Based on the differential pressure, Performing a water differential pressure control step of controlling the differential pressure. Thereby, the motive power at the time of producing | generating heat-source water and sending water can be reduced.

  In the heat source water control method according to the present embodiment, the heat source water control device calculates the target water supply differential pressure based on the range ability of the valve and the flow rate characteristic of the valve in the target water supply differential pressure calculation step. As a result, a common fixed value can be used in the valve type regardless of the diameter (size) of the valve, so that the target water supply differential pressure can be easily calculated.

  Further, in the heat source water control method according to the present embodiment, the heat source water control device calculates generation power information indicating a relationship between the water supply temperature of the heat source water and the generation power for generating the heat source water, and The water supply power calculation step for calculating the water supply power information indicating the relationship between the water supply temperature and the water supply power for supplying the heat source water, the generation power information calculated in the generation power calculation step, and the water supply power calculation step Based on the water supply power information, a water supply temperature calculation step for calculating a water supply temperature at which the sum of the generated power and the water supply power is minimized, and based on the water supply temperature calculated in the water supply temperature calculation step, the generation power and the water supply power of the heat source water And a power control step for controlling. Thereby, the production power and water supply power of heat source water can be reduced.

  Further, the heat source water control method in the present embodiment is based on the maximum water supply differential pressure and the change in the amount of water required when the heat source water control apparatus changes the water supply temperature of the heat source water in the water supply power calculation step. Based on this, the generated power information is calculated. Thereby, the generated power information can be calculated.

  Further, in the heat source water control method according to the present embodiment, the heat source water control device acquires the inlet temperature and the outlet temperature of the heat source water at each use-side heat load in the water supply power calculation step, and calculates the inlet temperature and the outlet temperature. Water temperature difference calculation step for calculating the water temperature difference, characteristic information indicating the characteristics of the air handling unit including the use side heat load indicated by the change amount of the water temperature difference with respect to the change of the water temperature difference, and the change amount of the water supply temperature of the heat source water Based on the above, calculate the amount of change in the flow rate of the heat source water supplied to each user-side heat load when the heat exchange amount in each user-side heat load is constant, and change the flow rate in all user-side heat loads. A water supply amount calculation step of calculating the change amount of the water supply amount by summing the amounts is further executed. Thereby, the water supply amount can be calculated.

  Further, in the heat source water control method according to the present embodiment, the heat source water control device acquires the inlet temperature and the outlet temperature of the heat source water at each use-side heat load in the water supply power calculation step, and calculates the inlet temperature and the outlet temperature. Calculated in the water temperature difference calculation step for calculating the water temperature difference, the flow rate acquisition step for acquiring the flow rate of the heat source water supplied to each use side heat load, the flow rate acquired in the flow rate acquisition step, and the water temperature difference calculation step Load factor calculation step for calculating the load factor of each use-side thermal load based on the difference in water temperature, the load factor calculated in the load factor calculation step, and the usage indicated by the amount of change in the water temperature difference with respect to the change in the load factor Based on the characteristic information indicating the characteristics of the air handling unit including the side heat load and the amount of change in the water supply temperature of the heat source water, The amount of change in flow rate when the heat exchange amount is constant is calculated, and the amount of change in flow rate is calculated by summing the amount of change in flow rate for all use-side heat loads . Thereby, the water supply amount can be calculated.

  In the heat source water control method according to the present embodiment, the heat source water control device does not calculate the water temperature at which the water temperature difference is lower than the lower limit value as the water supply temperature in the water supply temperature calculation step. Thereby, it is possible not to calculate the water supply temperature exceeding the capacity of the use side heat load.

  In the heat source water control method according to the present embodiment, the heat source water control device shows characteristics of the air handling unit including the use-side heat load indicated by the change amount of the water temperature difference with respect to the change of the water temperature difference in the water supply temperature calculation step. A lower limit value is calculated based on the characteristic information and the water supply temperature calculated in the water supply temperature calculation step. Thereby, it is possible not to calculate the water supply temperature exceeding the capacity of the use side heat load.

  In the heat source water control method according to the present embodiment, the heat source water control device does not calculate the water temperature higher than the outside dew point temperature during cooling as the water supply temperature in the water supply temperature calculation step. Thereby, it is possible not to calculate a water supply temperature at which dehumidification cannot be performed.

  In the heat source water control method according to the present embodiment, the heat source water control device shows characteristics of the air handling unit including the use-side heat load indicated by the change amount of the water temperature difference with respect to the change of the water temperature difference in the water supply temperature calculation step. A lower limit value is calculated based on the characteristic information and the water supply temperature calculated in the water supply temperature calculation step. Thereby, water supply temperature can be stabilized and power can be reduced.

  Further, in the heat source water control method according to the present embodiment, the heat source water control device is configured such that, in the opening degree acquisition step, the water temperature difference between the inlet temperature and the outlet temperature of the heat source water in the use side heat load, and the heat exchange amount in the use side heat load. The opening degree adjusted based on is acquired. Thereby, water supply temperature can be stabilized and power can be reduced.

  In the present embodiment, the heat source water control device controls water supply or generation of the heat source water by the heat source water control method described above. Thereby, the motive power at the time of producing | generating heat-source water and sending water can be reduced.

  According to at least one embodiment described above, in the heat source water control method, the heat source water control device includes a water supply differential pressure acquisition step, an opening degree acquisition step, a valve differential pressure acquisition step, and a target water supply differential pressure calculation step. And the power at the time of producing | generating heat-source water and sending water can be reduced by performing a water-feeding differential pressure control step.

  Although several embodiments of the present invention have been described, these embodiments are presented by way of example and are not intended to limit the scope of the invention.

  For example, in the above-described embodiment, the heat source water control system is described in which the heat source water is conveyed by the primary pump of the heat source unit and the flow rate is adjusted by the bypass valve provided in the bypass flow path. For example, a heat source water control system that does not have a bypass valve in the bypass pipe and adjusts the system flow rate with a secondary pump provided in a header or the like may be used.

  These embodiments can be implemented in various other forms, and various omissions, replacements, and changes can be made without departing from the spirit of the invention. These embodiments and their modifications are included in the scope and gist of the invention, and are also included in the invention described in the claims and the equivalents thereof.

Claims (12)

Heat source water control device
A water supply differential pressure acquisition step for acquiring a water supply differential pressure of heat source water supplied from a heat source machine to a plurality of use side heat loads;
An opening degree obtaining step for obtaining an opening degree of at least one of the valves provided in each use side heat load and adjusting a supply amount of the heat source water supplied to the use side heat load;
Based on the water supply differential pressure acquired in the water supply differential pressure acquisition step and the opening degree acquired in the opening degree acquisition step, a target value of the water supply differential pressure for setting the opening degree to a target value. A target water supply differential pressure calculating step for calculating a certain target water supply differential pressure;
A heat source water control that executes a water supply differential pressure control step for controlling the water supply differential pressure based on a maximum water supply differential pressure that is a maximum value among the target water supply differential pressures calculated in the target water supply differential pressure calculating step. Method. The heat source water control device further includes a valve differential pressure acquisition step of acquiring a valve differential pressure that is a difference between the pressure of the heat source water at the inlet of the valve and the pressure of the heat source water at the outlet of the valve;
2. The heat source water control method according to claim 1, wherein, in the target water supply differential pressure calculating step, the target water supply differential pressure is calculated further based on the rangeability of the valve, the flow rate characteristic of the valve, and the valve differential pressure. The heat source water control device is
A generation power calculation step for calculating generation power information indicating a relationship between a water supply temperature of the heat source water and a generation power for generating the heat source water;
A water supply power calculation step of calculating water supply power information indicating a relationship between the water supply temperature and the water supply power for supplying the heat source water;
Based on the generated power information calculated in the generated power calculation step and the water supply power information calculated in the water supply power calculation step, water supply for calculating the water supply temperature at which the sum of the generated power and the water supply power is minimized. A temperature calculation step;
The heat source water control method according to claim 1 or 2, further comprising: a power control step of controlling generation power and water supply power of the heat source water based on the water supply temperature calculated in the water supply temperature calculation step. . The heat source water control device is
4. The generated power information according to claim 3, wherein in the water supply power calculation step, the generated power information is calculated based on the maximum water supply differential pressure and a change in a water supply amount required when a water supply temperature of the heat source water is changed. Heat source water control method. The heat source water control device, in the water supply power calculation step,
A water temperature difference calculating step of acquiring an inlet temperature and an outlet temperature of the heat source water in each of the use side heat loads, and calculating a water temperature difference between the inlet temperature and the outlet temperature;
Based on the characteristic information indicating the characteristics of the usage-side equipment including the usage-side heat load indicated by the amount of change in the water temperature difference relative to the change in the water temperature difference, and the amount of change in the water supply temperature of the heat source water, the respective usage Calculate the amount of change in the flow rate of the heat source water supplied to each use side heat load when the heat exchange amount in the side heat load is constant, and calculate the amount of change in the flow rate in all the use side heat loads. The heat source water control method according to claim 4, further comprising a water supply amount calculation step of calculating a change amount of the water supply amount in total. The heat source water control device, in the water supply power calculation step,
A water temperature difference calculating step of acquiring an inlet temperature and an outlet temperature of the heat source water in each of the use side heat loads, and calculating a water temperature difference between the inlet temperature and the outlet temperature;
A flow rate acquisition step of acquiring a flow rate of the heat source water supplied to each of the use side heat loads;
A load factor calculating step for calculating a load factor of each use-side thermal load based on the flow rate acquired in the flow rate acquiring step and the water temperature difference calculated in the water temperature difference calculating step;
The load factor calculated in the load factor calculation step, characteristic information indicating characteristics of the usage-side equipment including the usage-side thermal load indicated by the amount of change in the water temperature difference with respect to the change in the load factor, and the heat source water Based on the amount of change in the water supply temperature, the amount of change in the flow rate when the amount of heat exchange in each use side heat load is made constant is calculated, and the amount of change in the flow rate in all the use side heat loads is totaled The heat source water control method according to claim 4, further comprising a water supply amount calculation step of calculating a change amount of the water supply amount. The heat source water control device is
The heat source water control method according to claim 5 or 6, wherein, in the water supply temperature calculation step, a water temperature at which the water temperature difference is lower than a lower limit value is not calculated as the water supply temperature. The heat source water control device is
In the water supply temperature calculation step,
8. The lower limit value is calculated based on characteristic information indicating characteristics of the usage-side device indicated by a change amount of the water temperature difference with respect to a change in the water temperature difference, and a water supply temperature calculated in the water supply temperature calculation step. The heat source water control method described in 1. The heat source water control device is
The heat source water control method according to any one of claims 3 to 8, wherein in the water supply temperature calculation step, a water temperature higher than an outside dew point temperature during cooling is not calculated as the water supply temperature. The heat source water control device is
The said opening degree acquisition step WHEREIN: The said opening degree adjusted based on the ventilation temperature of the air heat-exchanged by the said use side heat load and ventilated to an indoor unit is acquired as described in any one of Claim 1 to 9 The heat source water control method as described. The heat source water control device is
The said opening degree acquisition step WHEREIN: The said opening degree adjusted based on the water temperature difference of the inlet temperature of the said heat source water in the said use side heat load and outlet temperature, and the heat exchange amount in the said use side heat load is acquired. The heat source water control method according to any one of 1 to 10.   The heat source water control apparatus which controls water supply or the production | generation of the said heat source water by the heat source water control method as described in any one of Claim 1 to 11.

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