JP6847428B2 - A method for determining the load factor of heat source equipment, a simulation system in heat source equipment, a computer program for executing this, and a recording medium on which this program is recorded. - Google Patents

Description

The present invention relates to a method for determining a load factor of a heat source equipment, a simulation system in a heat source equipment, a computer program for executing the simulation system, and a recording medium on which this program is recorded. More specifically, a plurality of heat source devices for producing a heat medium used by a heat load side device group, a plurality of pumps corresponding to each heat source device, the plurality of heat source devices, and the plurality of pumps are connected in parallel. Each of the above in a heat source facility provided with a forward header and a return header for circulating the heat medium between the heat load side device group and the plurality of heat source devices, and a bypass connecting the forward header and the return header. The present invention relates to a method for determining a load factor of a heat source equipment for determining a load factor of a heat source equipment, a simulation system in a heat source equipment, a computer program for executing the simulation system, and a recording medium on which this program is recorded.

Conventionally, when a constant flow rate pump and a variable flow rate control are combined in the above-mentioned heat source equipment, it is difficult to secure a pressure balance between each device (pump). It was common to construct (control) heat source equipment. For example, in the control method of the heat source equipment as shown in Patent Documents 1 and 2, such a heat source equipment is not mentioned, and the control is performed on the premise of one pump (control).

However, in recent years, due to the spread of inverter pumps and the like, a combination of a constant flow rate pump and a variable flow rate control has come to be performed. On the other hand, for example, a control method as described in Non-Patent Document 1 has also been proposed. This control method includes feed-forward control that calculates the operating frequency of the pump that satisfies both the flow rate set value of each heat source device and the differential pressure between the headers from the approximate expression of the differential pressure between the headers and the differential pressure between the headers, and the differential pressure adjustment between the headers. By combining feed-back control, which controls the differential pressure between headers by the opening of the bypass valve, mixed control of variable flow rate compatible heat source equipment and constant flow rate heat source equipment is realized.

Here, in heat source equipment, the differential pressure between headers may be constant or controlled by end differential pressure control. When the heat load increases, the differential pressure between headers increases, and when the heat load decreases, the piping resistance increases. The differential pressure between the headers is reduced and the differential pressure is reduced. As a result, a differential pressure is also generated in the constant flow rate pump and the variable flow rate pump. However, in the above control method, the differential pressure adjustment between headers is mainly specified, and there is a possibility that control cannot be performed when the heat load in the heat load side device fluctuates.

Japanese Patent No. 4435651 Japanese Patent No. 4173973

Tokuomi Okazaki et al., Air Conditioning and Sanitary Engineering Society, Air Conditioning and Sanitary Engineering Society Proceedings No. 155, February 2010, "Study on variable speed control method of pump by modeling heat source system-First report-Examination of control method and confirmation of basic characteristics by experiment", p11-18

In view of such a conventional situation, the present invention is a method for determining a load factor of a heat source device capable of more accurately deriving the load factor of each heat source device even in a heat source facility in which a constant flow rate pump and a variable flow rate control are mixed. It is an object of the present invention to provide a simulation system in a heating source facility, a computer program for executing the simulation system, and a recording medium on which this program is recorded.

In order to achieve the above object, the features of the method for determining the load factor of the heat source equipment according to the present invention are a plurality of heat source equipment for producing the heat medium used by the heat load side equipment group and a plurality of pumps corresponding to each heat source equipment. A forward header and a return header in which the plurality of heat source devices and the plurality of pumps are connected in parallel and the heat medium is circulated between the heat load side device group and the plurality of heat source devices, and the forward header. In the method for determining the load factor of the heat source equipment in the heat source equipment provided with the bypass connecting the pump and the return header, the plurality of pumps include at least a constant flow pump and a variable flow pump. The required flow rate of the heat medium used by the heat load side equipment group including one unit is calculated, the total constant flow rate of the constant flow rate pump is calculated, and the constant flow rate is calculated from the sum of the required flow rate and the bypass flow rate of the bypass. The total variable flow rate of the variable flow pump is calculated by subtracting the total flow rate, and the constant flow pump having a low operation priority is changed to the variable flow pump until the total variable flow rate becomes larger than 0. The variable flow rate total flow rate is repeatedly calculated, and the variable flow rate total flow rate is divided by the rated total flow rate of the variable flow rate pump to obtain the variable flow rate load factor of the variable flow rate pump, and the variable flow rate load factor is preset. If it is smaller than the operating lower limit load factor of the variable flow pump, the variable flow load factor is replaced with the operating lower limit load factor, and the bypass flow rate is calculated by the replaced variable flow load factor, and the plurality of said bypass flow rates are calculated. The average outlet temperature of the heat source equipment is calculated, the inlet temperature of each heat source equipment is calculated, the outlet temperature of each heat source equipment, the inlet temperature, the design temperature difference, the variable flow load factor, and the preset constant flow rate. The load factor of each heat source device is obtained from the constant flow load factor of the pump, and when the load factor exceeds the maximum load factor of each heat source device, all the load factors of the heat source equipment are equal to or less than the maximum load factor. Until then, the outlet temperature of the corresponding heat source equipment is changed to the outlet temperature when operating at the maximum load factor of the equipment, and the average outlet temperature and the inlet temperature are obtained and the load factor is repeatedly calculated to calculate the load. The rate is defined as the load rate of each of the heat source devices.

In a heat source facility where constant flow control and variable flow control are mixed, if the amount of heat medium (heat load) used by the heat load side equipment group increases or decreases, the heat medium between the heat load side equipment group and multiple heat source equipment The differential pressure (differential pressure between headers) increases / decreases (varies) between the forward header and the return header. Even if the differential pressure between the headers fluctuates, the rated flow rate is maintained by adjusting the flow rate control valve on the outlet side of the constant flow rate pump. Therefore, the remaining amount obtained by subtracting the flow rate of the variable flow pump from the required flow rate of the equipment group on the heat load side is passed through the bypass connecting the forward header and the return header, and the frequency of the variable flow pump is set so that the flow rate of the bypass is minimized. By adjusting, the balance between the flow rate and pressure of the heat source equipment is ensured.

According to the above configuration, the required flow rate of the heat medium used by the heat load side equipment group is calculated, the total constant flow rate of the constant flow rate pump is calculated, and the sum of the required flow rate and the bypass flow rate of the bypass is used. The total flow rate of the variable flow rate is calculated by subtracting the total flow rate of the constant flow rate, and the constant flow rate pump having a low operation priority is changed to the variable flow rate pump until the total flow rate of the variable flow rate becomes larger than 0. Then, the total flow rate of the variable flow rate is repeatedly calculated, and the total flow rate of the variable flow rate is divided by the total rated flow rate of the variable flow rate pump to obtain the variable flow rate load factor of the variable flow rate pump, and the variable flow rate load factor is set in advance. If it is smaller than the operating lower limit load factor of the variable flow rate pump, the variable flow rate load factor is replaced with the operating lower limit load factor, and the bypass flow rate is calculated by the replaced variable flow rate load factor. It is possible to derive a value that is in line with reality, taking into consideration the balance between the flow rate and pressure of the heat source equipment.

Then, the load factor of each heat source device is obtained from the outlet temperature of each heat source device, the inlet temperature, the design temperature difference, the variable flow rate load factor, and the preset constant flow rate load rate of the constant flow rate pump, and the load is obtained. When the rate exceeds the maximum load factor of each heat source device, the outlet temperature of the corresponding heat source device is operated at the maximum load factor of the device until all the load factors of the heat source device are equal to or less than the maximum load factor. The load factor is repeatedly calculated by changing to the outlet temperature at the time of the pumping and obtaining the average outlet temperature and the inlet temperature. In this way, since the load factor of the heat source equipment is calculated in consideration of the variable flow rate load factor of the variable flow rate pump in the state where the flow rate and the pressure of the heat source equipment are balanced as described above, the constant flow rate pump and the variable flow rate control can be used. The load factor of each heat source equipment of the mixed heat source equipment can be derived more accurately.

In such a configuration, the variable flow rate load factor may be the same value in a plurality of variable flow rate pumps. This simplifies the calculation and speeds up the process.

Further, the calculation of the bypass flow rate is performed based on the following equation (4).

In any of the above configurations, the plurality of heat source devices are either cold water devices, hot water devices, or low cold water devices, and the heat medium is any of cold water, hot water, and low cold water.

In order to achieve the above object, the features of the simulation system in the heat source equipment according to the present invention are a plurality of heat source equipment for producing the heat medium used by the heat load side equipment group, a plurality of pumps corresponding to each heat source equipment, and a plurality of pumps. The forward header and the return header, the forward header and the return header, in which the plurality of heat source devices and the plurality of pumps are connected in parallel and the heat medium is circulated between the heat load side device group and the plurality of heat source devices, and the forward header and the said. In a heat source facility provided with a bypass connecting the return header, at least in the configuration of the heat source facility for obtaining the relationship between the operating conditions of the plurality of heat source devices and the usage amount or the production amount of the heat medium, the plurality of pumps are used. , A heat load amount setting unit that includes at least one constant flow pump and one variable flow pump, and sets the heat load amount of the heat medium required by the heat load side equipment group for each time zone on a daily basis. Manufacture of at least the heat medium among the results of operating the heat source equipment according to the operation conditions of the operation condition setting unit for setting the operation enablement and operation priority for each heat source device for each time zone and the operation conditions of the operation condition setting unit. A calculation unit that calculates the amount, a first flow rate calculation unit that calculates the required flow rate of the heat medium used by the heat load side equipment group, and a constant flow rate total flow rate of the constant flow rate pump, and the required flow rate and the above. The second flow rate calculation unit that calculates the total variable flow rate of the variable flow pump by subtracting the total constant flow rate from the sum of the bypass flow rates of the bypass, and the total variable flow rate are calculated by the rated total flow rate of the variable flow pump. A flow load factor calculation unit that obtains the variable flow load factor of the variable flow pump by dividing, a temperature calculation unit that calculates the average outlet temperature of the plurality of heat source devices and the inlet temperature of each heat source device, and the above. A load factor calculation unit that obtains the load factor of each heat source device from the outlet temperature of each heat source device, the inlet temperature, the design temperature difference, the variable flow rate load factor, and the preset constant flow rate load rate of the constant flow rate pump. The second flow rate calculation unit repeatedly calculates the variable flow rate total flow rate by changing the constant flow rate pump having a low operation priority to the variable flow rate pump until the variable flow rate total flow rate becomes larger than 0. Then, when the variable flow load factor is smaller than the preset operating lower limit load factor of the variable flow pump, the flow rate load factor calculation unit replaces the variable flow load factor with the operating lower limit load factor. When the load factor exceeds the maximum load factor of each heat source device, the load factor calculation unit calculates the bypass flow rate with the variable flow rate load factor replaced at the same time. Until the load factor becomes equal to or less than the maximum load factor, the outlet temperature of the corresponding heat source device is changed to the outlet temperature when operating at the device upper limit load factor of the device, and the average outlet temperature and the inlet temperature are obtained. The load factor is repeatedly calculated, and the calculation unit calculates the production amount of the heat medium based on the calculated load factor.

In such a case, the plurality of heat source equipment includes at least one of cold water system equipment, hot water system equipment, and low cold water system equipment, and the heat source equipment is used in the plurality of heat source equipment and / or the heat load side equipment group. Further, a power generation system device for supplying the power to be generated and a boiler system device for supplying steam used in the heat load side device group are further provided, and the calculation unit may use the power or the power consumption based on the load factor. It is preferable to calculate the amount of steam used or the amount of production before calculating the amount of production, and to calculate the amount of heat medium used or amount of heat before calculating the amount of steam used or amount of production.

The simulation system described in any of the above is realized by a computer program for causing a computer to execute the simulation system, and the computer program is recorded on a recording medium.

According to the method for determining the load factor of the heat source equipment according to the present invention, the simulation system in the heat source equipment, the computer program for executing the simulation system, and the recording medium on which this program is recorded, the constant flow pump and the variable flow control can be used. Even in a mixed heat source facility, it has become possible to derive the load factor of each heat source device more accurately.

Other objects, configurations and effects of the present invention will become apparent from the sections of embodiments of the invention below.

It is the schematic of the thermoelectric equipment which is the object of the simulation system which concerns on this invention. It is a data flow diagram of a simulation system. It is a block diagram of the hardware of the simulation system. It is a block diagram which shows an example of a thermoelectric equipment. It is a block diagram of the software of the simulation system. It is a flow chart which shows the setting procedure of each setting part. It is a figure which shows the whole of the general logic flow. It is a figure which shows the general logic flow of the energy balance of cold water and hot water. It is a figure which shows the general logic flow of a low pressure steam energy balance. It is a figure which shows the general logic flow of the gas engine exhaust hot water energy balance. Diagram showing the general logic flow of energy balance of hot water supply and electric power It is a figure which shows an example of the heat source equipment which mixes the heat source equipment of constant flow rate control and variable flow rate control. It is a flow chart which shows the calculation procedure of the flow rate load factor of a pump. It is a flow chart which shows the calculation procedure of the load factor of a heat source equipment. It is a figure which shows an example of the setting screen of the operating condition of a pump.

Next, the present invention will be described in more detail with reference to the accompanying drawings as appropriate.
As shown in FIG. 1, the thermoelectric equipment ME that is the target of the simulation system 1 according to the present invention is composed of a plurality of thermoelectric devices m1-9. The thermoelectric equipment ME is supplied with receiving high-pressure steam R1, receiving low-pressure steam R2, fossil fuel and other fuel (hereinafter, simply referred to as "fuel") R3, electric power R4, receiving cold water R5, and receiving hot water R6, and steam S (high pressure). Steam S1 and low-pressure steam S2), cold water S3, hot water S4, hot water supply S5, and electric power S6 are produced and supplied to the utilization equipment N (heat load side equipment group of buildings, factories, hotels, hospitals, etc.).

The thermoelectric equipment ME is roughly, power generation equipment m1, boiler equipment m2, cold water equipment m3, hot water equipment m4, low cold water equipment m5, hot water supply equipment m6, cooling tower equipment m7 (group cooling tower), heat storage. The system equipment m8 and the pump system equipment m9 are classified according to the system, and the thermoelectric equipment ME as described above is constructed by appropriately combining these. For example, as the low chilled water system device m5, a low chilled water system electric turbo chiller or a low chilled water system electric heat pump may be provided so that low chilled water can be supplied. In addition, Genelink (registered trademark), which is a cold water system device, effectively utilizes the exhaust heat hot water of 100 ° C or less generated from gas cogeneration (gas engine, fuel cell) to produce cold water. It is a machine. Further, in the present specification, the heat source device MH means a thermoelectric device m1 to 9 excluding the power generation device m1.

As shown in FIG. 2, in the simulation system 1, a plurality of user terminals 2 are connected to the DB server 4 through a network 5 such as TCP / IP.
As shown in FIG. 3, the hardware configuration of the user terminal 2 is roughly composed of a user interface 6 and a processing unit 7 that executes software (program) 10 of the simulation system 1. The user interface 6 includes an output device 6a such as a monitor and an input device 6b such as a keyboard and a mouse, and the user operates buttons and input fields on the screen displayed on the output device 6a. Further, the processing unit 7 is connected to a CPU 7a, a temporary storage memory 7b, a storage device 7c such as an HDD, a communication interface 7d such as a network adapter, and the like by a bus 8 such as a data bus and an address bus. Further, the CPU 7a, the temporary storage memory 7b, the storage device 7c, and the like cooperate with each other to operate the software 10.

The database (hereinafter abbreviated as "DB") group 100 of the DB server 4 includes a power charge DB 101, an environmental load DB 102, an equipment performance DB 103, and a weather condition DB 104. Information on the price of energy is stored and stored in the electricity rate DB 101. Environmental load data (unit environmental load) created from various published data and the like is stored in the environmental load DB 102. In addition, the equipment performance DB 103 includes the partial load characteristics of the equipment, changes in equipment efficiency due to the outside air temperature and wet-bulb temperature, internal power consumption, constraints on the equipment incorporated in the system, etc. by model type and fuel of major manufacturers. , Memorized by ability. In the meteorological condition DB 104, for example, information on the hourly outside air temperature and wet-bulb temperature at 28 points nationwide is stored and stored.

The user of this system accesses the DB server 4 through the network 5, reads the power charge data file 101a, the environmental load data file 102a, the manufacturer / equipment data template file 103a, and the weather condition data file 104a from each DB 101-104. Save as read data 100a. The read data 100a can be manually changed as appropriate and is saved in the case file 106. In this way, the conditions and parameters set in each setting unit described later can be recorded as a case file 106 in a storage device 7c such as an electronic recording medium. The storage device (medium) is not limited to the HDD 7c, and various removable disks such as magnetic disks, optical disks, and RAMs can be used as the electronic recording medium.

In the calculation unit 7p of the processing unit 7, the simulation data obtained by modifying the data according to the energy system evaluated by the user is saved as the case file 106 and the thermoelectric load file 104, and displayed, printed or filed as a graph or form. It is output in the format of. Further, one of the thermoelectric devices includes a partial load characteristic, and the calculation unit 7p sets the load factor of the thermoelectric device so that the production amount of any of the above-mentioned energies becomes the target value set by the energy load setting unit 20. Change and calculate convergence. Further, the calculation unit 7p determines the number of thermoelectric devices and changes the number so that the convergence calculation is completed.

Here, FIG. 4 shows the block flow of the thermoelectric equipment ME. This thermoelectric equipment ME is composed of a gas turbine cogeneration m1a as a power generation equipment, a low pressure boiler m2a as a boiler equipment, an absorption chiller m3a as a cold water equipment, and a turbo chiller m3b. The gas turbine cogeneration m1a includes an exhaust heat boiler m1a1.

As shown in FIG. 5, the program 10 of the simulation system 1 is roughly composed of an energy load setting unit (heat load amount setting unit) 20, a basic condition setting unit 30, a system construction setting unit 40, an operation condition setting unit 50, and an operation result. It includes an output unit 60, a case file creation unit 70, a display control unit 80, and a heat source device calculation unit 90.

The basic condition setting unit 30 includes a utility cost setting unit 31, a process condition setting unit 32, an environmental load setting unit 33, and a temperature data setting unit 34. The utility cost setting unit 31 includes an electric power cost setting unit 31a and a fuel cost setting unit 31b. Utility costs are calculated by multiplying the energy supplied and the price of that energy.

Here, FIG. 6 shows a setting procedure of each setting unit of the simulation system.
In this setting procedure, first, the energy load is set by the energy load setting unit 20 (S201). Next, the process condition setting unit 32 sets the process conditions of the heat medium (S202). Then, the environmental load data and the utility cost are set by reading from the environmental load DB 102 and the electricity charge DB 101 by the environmental load setting unit 33 and the utility cost setting unit 31 (S203, 204). After setting these, the system construction setting unit 40 constructs the thermoelectric equipment by selecting the thermoelectric equipment and reading the equipment performance data (S206, 207), and sets the operating conditions in the constructed thermoelectric equipment to the operation condition setting unit 50. (S208). The construction status of the thermoelectric equipment is appropriately displayed on the flow chart via the display control unit 80. The conditions set in each of the above steps can be appropriately saved as individual data 100b such as the user device template file 103b, the thermoelectric load file 105, and the case file 106 by the case file or the like creation unit 70. Further, although various data of the DB group 100 are used for setting in each of the above steps, it is also possible to make various settings using the stored individual data 100b.

Then, based on these setting conditions, the time zone-specific and / or yearly simulation is executed by the calculation unit 7p (S209). The result is output by the operation result output unit 60 in the form of a graph or a form (S210). It is also possible to change the conditions and perform the simulation repeatedly. In such cases, changes in operation priority, operation availability and minimum power purchase amount, electric power owner, heat owner, etc. (S211) are performed under operating conditions, and equipment additions, changes, and deletions (S212) for comparative examination are performed in the system. Perform in the build settings. Then, the simulation is executed again and output (S209, 210).

In the energy load setting (S201), the energy load setting unit 20 sets the amount of combined energy required for the equipment to be used for each time zone by month, day, and pattern. For example, the chilled water load, the steam load, the electric power load, the chilled water supply temperature, and the chilled water return temperature are set as the outside air temperature, the wet bulb temperature, and the thermoelectric load data. The outside air temperature is related to the intake air temperature of the gas turbine, and the intake air temperature is a parameter of the gas turbine power generation amount. The wet-bulb temperature affects the cooling water temperature, becomes a variable of the performance (COP) of the absorption chiller and the turbo chiller, and is related to the power consumption and fossil fuel consumption.

For thermoelectric load data such as cold water load, hot water load, low-voltage steam, high-pressure steam, hot water supply load, and electric power load, if the thermoelectric equipment is already in operation, use the thermoelectric load data collected during the operation. Can be set. In addition, this energy load setting can be set for 12 months with 24-hour data up to a maximum of 8 patterns of load each month. The supply temperature and return temperature of cold water, low cold water, and hot water can be set in the same manner.

Next, in the process condition setting (S202), the process condition setting unit 32 sets the process conditions of the heat medium such as the basic conditions, the fuel data, the electric system / steam system, and the type of recovered steam such as the gas turbine. The process condition setting unit 32 selects whether to use the temperature difference of the heat medium, the outside air temperature, and the wet-bulb temperature of the energy load setting unit 20, and determines each of the supply temperature and the return temperature of cold water, hot water, and low cold water. Set the target temperature difference and the minimum by-bus flow rate. In addition, the conditions for high-pressure and low-pressure steam (pressure MpaG, steam enthalpy kJ / kg, return water enthalpy kJ / kg, steam recovery rate%) are set.

In the fuel process conditions, the calorific value and specific gravity of gas, heavy oil, kerosene and other oils are set. For the electric system and steam system, the power load of thermoelectric load data, the breakdown of low-pressure steam load, the supply destination of generated power, the gas turbine and reheating gas turbine, the recovery steam type of the gas engine, and the power recovery by steam decompression are set respectively. To do.

The breakdown of the electric power load of the thermoelectric load data selects whether the electric power load set by the energy load setting unit 20 is the electric power load supplied to other than the thermoelectric equipment or the electric power load including the electric power of the thermoelectric equipment. Similarly, the breakdown of the low-voltage steam load in the thermoelectric load data selects whether the low-voltage steam load is a steam load supplied to other than the thermoelectric facility or a steam load generated in the thermoelectric facility. In addition, when the total steam load (steam load from the steam generator) is selected, it is the case where steam is supplied to the equipment used and steam is used in the thermoelectric equipment, and it is set as the total flow rate generated from the steam generator. Will be done.

In addition, power recovery by steam decompression is set for a power recovery facility that can recover power when there is a surplus in high-pressure steam and the pressure is reduced to low-pressure steam. In this case, set the enthalpy of high-pressure steam and exhaust steam required for the maximum power generation amount and partial load power generation amount. For each recovered steam type, it is selected whether the steam generated from the power generation system equipment (gas turbine, reheating gas turbine, gas engine) is low-pressure steam or high-pressure steam.

When setting the supply destination of generated power, in order to determine where to supply and use the electricity generated by the power generation equipment, the power of the thermoelectric equipment and the equipment used is borne, the power of only the thermoelectric equipment is borne, and only the equipment used. Select the power of the burden from one of the burdens. When the power supply destination is selected as "supply to thermoelectric equipment", the power is balanced so that the power generation equipment generates power according to the amount of power consumed by the thermoelectric equipment. Also, if "Consumer only" is selected, the power is similarly balanced so that the power generation equipment generates power according to the amount of power other than the heat source.

In the environmental load data setting (S203), the environmental load data setting unit 33 sets the environmental load data. Specifically, the power consumption and fossil fuel and other fuel consumptions obtained under the conditions set by the energy load setting unit 20, the basic condition setting unit 30, the system construction setting unit 40, and the operating condition setting unit 50. On the other hand, it is set to output the _{environmental load (primary energy, CO 2} , NO _x , SO _x ) by multiplying the environmental load data (unit environmental load). _{The data to be set are CO 2} , NO _x , and SO _x emission intensity and crude oil conversion values for each of electricity, gas, kerosene, heavy oil, and other oils. For electric power, a primary energy conversion value is further set. Further, the electric power can be set for each time zone such as daytime and nighttime.

Next, in the utility cost setting (S204), the electric power cost setting unit 31a and the fuel cost setting unit 31b set the electric power and the fuel cost. The electric power cost setting unit 31a sets the electric power cost determined by the electric power contract type, the additional type of the optional clause, and the electric energy consumption.

In the system construction setting (S206), the system construction setting unit 40 constructs the system configuration of the thermoelectric equipment ME. The system construction setting unit 40 arbitrarily sets a plurality of thermoelectric devices of the same model, models with different capacities, models with different energies for operation, or models with different manufacturers, and each of them is set according to the operating conditions of the operating condition setting unit 50. It is possible to operate.

Each performance data of the thermoelectric device is stored in the device performance DB 103 of the DB group 100, and is set by reading the performance data in the device data reading (S207). The device performance DB 103 is classified and stored according to the above-mentioned device system, by device, by manufacturer, by model number, by fuel, by ability, and by performance. The performance data is read by selecting these classifications via the system construction setting unit 40 and the display control unit 80. The performance of each of the above device performance data can be changed arbitrarily.

Here, the device performance data of the thermoelectric device read from the device performance DB 103 as described above will be described.
The equipment performance data of the gas turbine cogeneration m1a includes the relationship between the operating load factor%, the power generation efficiency%, and the exhaust heat boiler heat recovery rate% for each intake temperature of the gas turbine (for example, 0 ° C., 15 ° C., 30 ° C.). There is. Based on this relationship, the performance for that time is determined by the outside air temperature set in the energy load setting unit 20. The power generation efficiency and heat recovery rate are determined by the intake air temperature of 15 ° C. and the load factor by a multivariate regression model with the explanatory variables as the intake air temperature and the load factor. In addition, the intake air temperature can be changed, and the performance curve for each temperature can be displayed as a graph by changing the intake air temperature. As described above, for the temperature performance other than the set temperature, the power generation efficiency and the heat recovery rate are determined by the intake air temperature and the load factor by this regression equation.

The equipment performance data of the low-pressure boiler m2a sets the thermal efficiency% at a plurality of arbitrary load factors% of the low-pressure boiler. Further, in the same manner as described above, the blowdown amount, the capacity / number / fuel of the main engine, the NOx value, the power consumption of the auxiliary engine, and the energy loss at the time of starting are set. The equipment performance data of the low-pressure boiler m2a is also set by reading the data in the same manner as described above.

The equipment performance data of the absorption chiller m3a sets the COP during cold water mode operation at any plurality of partial load factors. By setting these, the relationship between the COP in each mode and the changing COP% is set with the cooling water temperature as a parameter, as in the above regression equation. Also, set the design temperature difference between cold water and cooling water.

The relationship between the cold water mode COP and the COP% that changes with the cooling water temperature as a parameter is obtained by the above regression equation. In addition, the number of main engines, design capacity and actual capacity (capacity when deteriorated over time), capacity and power consumption per fan of the attached cooling tower, cooling tower capacity and make-up water concentration ratio of the attached cooling tower are set. ..

Further, as shown in FIG. 10, the flow rate control method of the pump, the operating lower limit load factor, the actual head, and the like are set. Further, the power consumption of the auxiliary machine of the absorption chiller and the energy loss at the time of starting are set in the same manner as described above.

The equipment performance data of the turbo chiller m3b sets the capacity and number of main engines. In addition, the partial load factor and the COP during cold water operation are set, and the relationship between the cold water COP and the COP% that changes with the cooling water temperature as a parameter is set. Set the design chilled water temperature difference and chilled water temperature difference. These settings are similar to the absorption chiller. Further, the relationship between the cold water COP and the load factor as parameters and the changing COP and the relationship between the cold water COP and the cooling water temperature as parameters are also obtained by the regression equation. In addition, the pump efficiency is set in the same way as the absorption chiller, and is set by reading the equipment data.

In the operation condition setting (S208), the operation condition setting unit 50 sets the operation availability and / or the operation priority for each thermoelectric device for each month, day, and pattern for each time zone. An operation plan for thermoelectric equipment is constructed by setting these operating conditions. For cold water and hot water equipment, in addition to the priority, set the outlet temperature of each equipment. Low cold water equipment can be set in the same way.

Set the amount of high-pressure steam, low-pressure steam, cold water, hot water, and electricity that can be used externally. For each received amount, a plurality of arbitrary time zones are set, and the received amount in each time zone is set respectively. The total amount of combined energy that can be manufactured by thermoelectric equipment and supplied to other equipment is also set in the same way. These set values are taken into consideration to balance the supply energy and the total combined energy. High-pressure steam, cold water, hot water, and electric power are all treated in the same way. Thereby, the operation plan of the thermoelectric equipment can be set by the operation condition setting unit 50 while referring to the energy load set by the energy load setting unit 20.

After setting the operating conditions, the simulation is executed (S209) and the result is output. In the output step (S210), the operation result output unit 60 outputs the simulation result as a time zone-based and / or annual calculation. Output formats include graphs and forms.

The operation condition setting (S208) by the operation condition setting unit 50 and the simulation calculation procedure by the calculation unit 7p consist of the steps S01 to 07 of FIG. 7A, and each step corresponds to FIGS. 7B to 7E. In each of the following descriptions, the electric power main (power priority) operation is an operation in which a reverse tide does not occur in the electric power, and the heat main (heat load priority) operation is an operation in which, for example, steam is not released. Further, in the explanation of each step, only the steps related to the example using the thermoelectric equipment of FIG. 4 are shown first. Further, since the details of the simulation calculation are in the earlier application (Japanese Patent Application No. 2010-504354) of the applicant of the present application, detailed description thereof will be omitted.

The flow shown in FIG. 7A is a general balance calculation processing procedure in the simulation, and is a cold water energy balance step (hereinafter abbreviated as “EB”) (S01), hot water EB (S02), and low pressure steam EB (S03). , High-pressure steam EB (S04), gas engine exhaust hot water EB (S05), hot water supply EB (S06), and electric power EB (S07). In this way, the supplied energy is sequentially calculated in the order of steam energy before electric power energy and other energy before this steam energy, based on the setting conditions in each of the above steps.

Here, in the case where the thermoelectric equipment is in the main operation, if G1> Ea-W1, it is determined whether the ABS (G1- (Ea-W1)) is within the allowable error range α (S73 in FIG. 7C). In the present embodiment, the permissible error range α = ± 1 kW or less, and if it is within the error range, the calculation ends. The ABS in the figure is a function obtained by removing the sign +-from the numerical value. G1 is the amount of power generation, Ea is the amount of power consumption in the system, and W1 is the minimum amount of power purchased.

If the permissible error is not within ± 1 kW, for example, the load factor P1 of the GT cogeneration of the power generation system equipment is changed, and the load factor P1 is obtained from Equation 2 so that G1 = Ea−W1. However, when the load factor P1 is changed and the recovered steam amount S1 fluctuates, the internal power consumption fluctuates according to the fluctuation of the operating conditions of the GT cogeneration and other devices, and the power consumption Ea in the system also fluctuates. The original purpose of preventing reverse tide in main operation cannot be achieved. Therefore, until the convergence of S73 is achieved, it is necessary to perform the convergence calculation of repeating S35c to S71 after changing the load factor P1 of S74 as follows.

Here, the relationship between the GT cogeneration load factor P and the exhaust heat recovery rate S% is expressed as in Equation 1, and the relationship between the same load factor P and the power generation efficiency G% is expressed as in Equation 2. Both relational expressions are general forms of multivariate regression model and independent bivariate expression. However, the intake air temperature is T ° C.
S = f (T, P) Equation 1
G = g (T, P) Equation 2

When the intake air temperature is constant, the load factor% can be obtained as a solution of the quadratic equation by obtaining the load factor% from the target power generation amount created as the quadratic equation by each explanatory variable. However, since the gas turbine is limited by the minimum load factor%, the calculation start point is the intermediate value (Pmid%) between the maximum load factor (Pmax%) and the minimum load factor (Pmin%). Therefore, when the amount of power generation at Pmid% is larger than the target amount of power generation, Pmax = Pmid, and when the amount of power generation at Pmid% is smaller than the target amount of power generation, Pmin = Pmid. Find the target load factor% with. At the same time, the margin of error between the power generation amount kW at Pmid% and the target power generation amount kW is 1 kW or less. The maximum number of convergence calculations is set to 20 in consideration of the case where convergence is not possible, but the number of convergences can be set as appropriate. If it converges, proceed to the next step. The two-minute search method is only an example of a convergence calculation method based on an algebraic equation numerical calculation method. Convergence calculation method by algebraic equation numerical calculation method is numerical calculation of equations that do not include differentiation and integration such as higher-order algebraic equations, fractional equations, irrational equations, and transcendental equations. Each of these methods can be used for all convergence calculations in the present invention.

Unlike the above, in the thermal main operation of S37a to S38b, it is examined whether or not the difference between the recovered steam amount S1 and the low pressure steam load S2 is within the error range α. Normally, it is sufficient to change the load factor P1 for that purpose once, and it is not necessary to perform the convergence calculation. However, in a device such as a thermoelectric variable GT cogeneration, it is possible to recover the generated steam again and improve the power generation efficiency. In such a case, it is possible to change the steam recovery rate and / or the load factor P1 and perform the convergence calculation so that there is no excess or deficiency of low-pressure steam and no reverse tide of electric power is generated.

When the load factor P1 was reset in the main operation, for convenience of explanation, it was set to return to the front of S35c of the low-voltage steam EB03 (K in FIG. 7C), but as long as there is no contradiction in the calculation, for example. It may be set to return to the initial position of the cold water EB01 (K'in FIG. 7B). It is meaningful to reset the conditions, readjust the operating conditions of all the equipment of the system, and converge the specific supplied energy to the target value.

In this way, the procedure for calculating the system balance is to assemble the thermoelectric balance in the order of cold water, hot water, low-pressure steam, high-pressure steam, hot water supply, and electric power for each series. When the assembled conditions change, the convergence calculation is performed by the multivariable algebraic equation numerical analysis method, and the thermoelectric balance of all systems is calculated. Based on this balance result, the output of the device operated and output under the load of each device is organized into necessary information and output by the operation result output unit 60 as described above.

By the way, the thermoelectric equipment ME to be simulated includes, for example, the heat source equipment MH as shown in FIG. This heat source equipment MH includes a plurality of heat source equipment mh for manufacturing the heat medium R used by the heat load side equipment group N (utilization equipment), a plurality of pumps p corresponding to each heat source equipment mh, and a plurality of heat source equipment mh. And the forward header HF and the return header HB in which a plurality of pumps p are connected in parallel and the heat medium R is circulated between the heat load side equipment group N and the plurality of heat source equipment mh, and the forward header HF and the return header HB. It is provided with a bypass B for connecting the above.

The plurality of heat source devices mh are the rated constant flow rate control heat source devices mh1 to mhm and the corresponding constant flow rate pumps p1 to pm, and are composed of the variable flow rate control heat source devices mhm + 1 to mhn and the variable flow rate pumps pm + 1 to pn. There is. As described above, the plurality of pumps p include at least one constant flow rate pump and one variable flow rate pump. The present invention accurately determines (simulates) the operating load factor of each heat source device in a heat source facility in which constant flow rate control and variable flow rate control coexist.

In the example of the figure and the following description, a plurality of heat source devices mh will be described as cold water devices, and the heat medium R will be described as cold water, but the present invention is not limited thereto. The plurality of heat source devices mh are not limited to cold water devices, and may be at least one of cold water devices, hot water devices, and low cold water devices. Further, the heat medium R is not limited to cold water, but may be cold water, hot water, or low cold water. Similar to the case of cold water below, hot water and low cold water are also treated.

Next, the calculation of the load factor of the cold water system equipment will be described in more detail with reference to FIGS. 5, 9A and 9B.

As shown in FIG. 5, the load factor calculation unit 90 of the simulation system 1 is roughly composed of a first flow rate calculation unit 91, a second flow rate calculation unit 92, a flow rate load rate calculation unit 93, and a temperature calculation unit 94. A load factor calculation unit 95 is provided. Further, the calculation step roughly includes a flow rate load factor calculation step of the pump shown in FIG. 9A and a load factor calculation step of the heat source device shown in FIG. 9B.

^{First, the first flow rate calculation unit 91 calculates the required flow rate F (m 3} / h) of the cold water R required (used) in the heat load side equipment group N (utilized equipment) by the following formula (1) (1). S101). In the following equation (1), Q is the cold water load, and ΔT is the temperature difference between the cold water.

Here, the cold water minimum bypass flow rate of the bypass B to F _B, coolant flow rate F _T should be delivered to the heat load side equipment group N across multiple pumps p1~pn (m ³ / h) becomes F + F _B ..

Further, the first flow rate calculation unit 91 calculates the total flow rate of the constant flow rates of the constant flow rate pumps p1 to pm (S102). Here, the rated pump capacity F _R of the constant flow pump p1~pm Since found by chilled water system equipment mh1~mhm design capabilities (MJ / h) /4.18605 (MJ / Mcal) / design temperature difference (℃) , the sum of the rated pump capacity F _R is constant flow total flow rate. During this calculation, in the present embodiment, the flow rate load factor P _R of the constant flow pump p1~pm are all 100%. The variable flow rate pump pm + 1 to pn shares the rest with a uniform load factor. This simplifies the calculation and processes it at high speed.

By subtracting the constant flow total flow rate from the sum (= coolant flow rate F _T) of the constant flow pump p1~pm the required flow rate F and cold minimum bypass flow rate F _B of cold R obtained above, variable flow pump pm + 1~pn The total flow rate of the variable flow rate can be obtained. Therefore, the second flow rate calculation unit 93 calculates the total variable flow rate by the following formula (2) (S103). In the following formulas (2), F _i is variable flow pump flow, F _iR is Teikakujo flow pump flow. Further, the number of constant flow rate pumps is i = 1 to m, and the number of variable flow rate pumps is i = m + 1 to n.

Here, the obtained total variable flow rate may be negative (0 or less) (S104). In such a case, the operation condition setting unit 50 changes the constant flow rate pump having the lowest rank in the preset operation priority to the variable flow rate pump (S105). Then, the second flow rate calculation unit 92 performs the calculation again under the changed operating conditions (S103). This calculation is repeated until the total variable flow rate becomes positive (greater than 0). However, the power consumption may be calculated by the power consumption of a constant flow rate. This is because it is assumed that the flow rate becomes negative temporarily and the flow rate balance cannot be secured.

When the variable flow total flow rate is positive, the flow rate load factor calculating unit 93 calculates a variable flow load factor L _F of the variable flow pump by the following formula (3) (S106).

Here, as for the pump conditions, as shown in FIG. 10, the operating lower limit load factor of the pump is set according to the equipment performance data. When the obtained variable flow rate load factor L _F is smaller than the preset operating lower limit load factor, the flow rate load factor calculation unit 93 _{replaces the obtained variable flow rate load factor L F} with the lower operating lower limit load factor. at a flow rate load factor L _F calculating the bypass flow rate F _B (S108). By substituting the obtained variable flow rate load factor L _F with the operation lower limit load factor, the flow rate required by the heat load side equipment group N can be further increased. Therefore, the following equation (4) to calculate a cold minimum bypass flow rate F _B. This formula is a back calculation of the above formula (3). In this way, the flow rate load factor L _{F of} each variable flow rate pump pm + 1 to pn can be obtained.

Thus with a flow rate load factor L _F of the variable flow pump pm + 1~pn determined, in the procedure shown in FIG. 9B, determining the load factor L _i of each chilled water system equipment Mh1～mhn.
First, the temperature calculating section 94, based on each variable flow pump flow F _i corresponding to the outlet temperature T _i and chilled water system equipment of each chilled water system equipment mh1~mhn set in operating condition setting unit 50, the following formula ( 5) calculating an average outlet temperature T _T (S 111). Here, the pump changed from the constant flow rate pump to the variable flow rate pump in step S105 is calculated with the flow rate of the variable flow rate pump pm + 1 to pn.

The temperature calculation section 94, by the following equation (6) using the average outlet temperature T _T determined obtaining the inlet temperature T _U of the chilled water system equipment mh1~mhn (S112).

Then, the load factor calculation unit 95 includes the outlet temperature T _i of each cold water system device mh1 to mhn, the obtained inlet temperature T _{U , the design temperature difference ΔT i} set in advance by the process condition setting unit 32, and the previously obtained change. Using the flow rate load factor L _{Fi , the load factor L i} of each cold water system device mh1 to mhn is calculated by the following formula (7) (S113). Here, in the case of the cold water system equipment mh1 to mhm corresponding to the constant flow rate pumps p1 to pm, the variable flow rate load factor L _Fi is calculated as the constant flow rate load rate (for example, 100%) of the preset constant flow rate pumps p1 to pm. To do.

Here, when the load factor L _i of each chilled water system equipment Mh1～mhn determined exceeds the maximum load factor of each chilled water system equipment mh1~mhn (S114), in all of the chilled water system equipment Mh1～mhn, load factor L _{Until i} becomes less than the maximum load factor, the outlet temperature T _i of the corresponding cold water system equipment mh is changed to the outlet temperature when operating at the equipment upper limit load factor of the equipment (S115), and the average outlet temperature _TT and seeking inlet temperature T _U repeatedly calculating a load factor L _i% (S113~S115).

In this way, when the load factor _Li is equal to or less than the maximum load factor, the cold water EB step is performed at the _{load factor L i.} Further, using the variable flow load factor L _Fi obtained above, the power consumption is calculated according to the operation control method of the pump of each cold water system device. In the case of "variable flow rate control by valve", the following formula (8), in the case of "constant discharge pressure inverter variable flow rate control", the following formula (9), in the case of "discharge pressure fluctuation inverter variable flow rate control", the following formula (10) is used.

Then, the process proceeds to the other energy balance step described above, simulation of cold water, for example, in the heat source equipment MH is performed, and the amount of energy used is calculated.

The present invention is a thermoelectric facility in which a plurality of thermoelectric devices are connected, at least electric power and fossil fuel are supplied, and electric power, low cold water, cold water, hot water, hot water supply, high pressure steam and low pressure steam are produced and supplied to the utilization equipment. It can be used as a simulation system for thermoelectric equipment that simulates the amount of energy used to produce any of the combined total energy. Further, the present invention relates to the power consumption, fossil fuel and other fuel consumption, and the environmental load data setting unit obtained by the conditions of the energy load setting unit, the basic condition setting unit, the system construction setting unit, and the operating condition setting unit. It can be used as a system that simulates the environmental load (primary energy, CO _{2, NOx, SOx) by multiplying each unit environmental load.} Further, the present invention can be used for operation diagnosis by simulating the current state of thermoelectric equipment, energy saving by changing the operation method, improvement by equipment renewal and its energy saving, evaluation and consultation of reduction of environmental load.

1: Simulation system 2: User terminal 4: DB server 5: Network, 6: User interface, 6a: Output device, 6b: Input device, 7: Processing unit, 7a: CPU, 7b: Temporary storage memory, 7c : Storage device, 7d: Communication interface, 7: Processing unit, 7p: Calculation unit, 8: Bus, 10: Software (program), 20: Energy load setting unit (heat load amount setting unit), 30: Basic condition setting unit , 31: Utility cost setting unit, 31a: Electric power cost setting unit, 31b: Fuel cost setting unit, 32: Process condition setting unit, 33: Environmental load setting unit, 34: Temperature data setting unit, 40: System construction setting unit, 50: Operating condition setting unit, 60: Operation result output unit, 70: Case file creation unit, 80: Display control unit, 90: Heat source equipment calculation unit, 91: First flow rate calculation unit, 92: Second flow rate calculation unit , 93: Flow rate load factor calculation unit, 94: Temperature calculation unit, 95: Load factor calculation unit, 100: DB group, 100a: Read data, 101: Power charge data file, 101a: Power charge data file, 102: Environmental load DB, 102a: Environmental load data file, 103: Equipment performance DB, 103a: Equipment data file, 104: Meteorological condition DB, 104a: Meteorological condition data file, 105: Thermoelectric load file, 106: Case file, ME: Thermoelectric equipment, MH: Heat source equipment, R1: High pressure steam, R2: Low pressure steam, R3: Fuel, R4: Electric power, R5: Cold water, R6: Hot water, S1: High pressure steam, S2: Low pressure steam, S3: Cold water, S4: Hot water, S5 : Hot water supply, S6: Electric power, N: Equipment used (heat load side equipment group), m1: Power generation equipment, m2: Boiler equipment, m3: Cold water equipment, m4: Hot water equipment, m5: Low cold water equipment, m6: Hot water supply system equipment, m7: Cooling tower system equipment (group cooling tower), m8: Heat storage system equipment, m9: Pump system equipment, mh: Heat source equipment, R: Heat medium, HF: Outward header, HB: Return header, B: Bypass, p: Pump, m1a: Gas turbine cogeneration, m2a: Low pressure boiler, m3a: Absorption type refrigerator, m3b: Turbo refrigerator, m1a1: Exhaust heat boiler

Claims (8)

A plurality of heat source devices for producing a heat medium used by a heat load side device group, a plurality of pumps corresponding to each heat source device, the plurality of heat source devices, and the plurality of pumps are connected in parallel and the heat load side. Load of each heat source device in a heat source facility including a forward header and a return header for circulating the heat medium between the device group and the plurality of heat source devices, and a bypass connecting the forward header and the return header. It is a method of determining the load factor of heat source equipment that determines the rate.
The plurality of pumps include at least one constant flow rate pump and one variable flow rate pump.
The required flow rate of the heat medium used by the heat load side equipment group was calculated, and the total constant flow rate of the constant flow pump was calculated.
The total variable flow rate of the variable flow pump is calculated by subtracting the total constant flow rate from the sum of the required flow rate and the bypass flow rate of the bypass.
Until the total flow rate of the variable flow rate becomes larger than 0, the constant flow rate pump having a low operation priority is changed to the variable flow rate pump, and the total flow rate of the variable flow rate is repeatedly calculated.
By dividing the total flow rate of the variable flow rate by the total rated flow rate of the variable flow rate pump, the variable flow rate load factor of the variable flow rate pump is obtained.
When the variable flow rate load factor is smaller than the preset operating lower limit load factor of the variable flow rate pump, the variable flow rate load factor is replaced with the operating lower limit load factor, and the replaced variable flow rate load factor is used. Calculate the bypass flow rate and
The average outlet temperature of the plurality of heat source devices is calculated, and the inlet temperature of each heat source device is calculated.
The load factor of each heat source device is obtained from the outlet temperature of each heat source device, the inlet temperature, the design temperature difference, the variable flow rate load factor, and the preset constant flow rate load factor of the constant flow rate pump.
When the load factor exceeds the maximum load factor of each heat source device, the outlet temperature of the heat source device is set to the maximum load factor of the device until all the load factors of each heat source device are equal to or less than the maximum load factor. The load factor was repeatedly calculated by obtaining the average outlet temperature and the inlet temperature while changing to the outlet temperature when operating in.
A method for determining a load factor of a heat source device, wherein the calculated load factor is the load factor of each heat source device.
The method for determining a load factor of a heat source device according to claim 1, wherein the variable flow rate load factor is the same value in a plurality of variable flow rate pumps. The method for determining the load factor of the heat source device according to claim 1 or 2, wherein the calculation of the bypass flow rate is performed based on the following formula (4).

The plurality of heat source devices are any of cold water devices, hot water devices, and low cold water devices, and the heat medium is any of cold water, hot water, and low cold water, according to any one of claims 1 to 3. The method for determining the load factor of the heat source equipment described. A plurality of heat source devices for producing a heat medium used by a heat load side device group, a plurality of pumps corresponding to each heat source device, the plurality of heat source devices, and the plurality of pumps are connected in parallel and the heat load side. In a heat source facility including a forward header and a return header for circulating the heat medium between the device group and the plurality of heat source devices, and a bypass connecting the forward header and the return header, at least the plurality of heat sources. A simulation system in a heat source facility that finds the relationship between the operating conditions of the equipment and the amount of heat used or manufactured.
The plurality of pumps include at least one constant flow rate pump and one variable flow rate pump.
A heat load amount setting unit that sets the heat load amount of the heat medium required by the heat load side equipment group for each time zone on a daily basis.
An operation condition setting unit that sets the operation availability and operation priority for each of the heat source devices for each time zone, and
A calculation unit that calculates at least the production amount of the heat medium among the results of operating the heat source equipment according to the operating conditions of the operating condition setting unit.
A first flow rate calculation unit that calculates the required flow rate of the heat medium used by the heat load side equipment group and also calculates the total constant flow rate of the constant flow rate pump.
A second flow rate calculation unit that calculates the total flow rate of the variable flow rate pump by subtracting the total flow rate of the constant flow rate from the sum of the required flow rate and the bypass flow rate of the bypass.
A flow rate load factor calculation unit that obtains the variable flow rate load factor of the variable flow rate pump by dividing the total flow rate of the variable flow rate by the rated total flow rate of the variable flow rate pump.
A temperature calculation unit that calculates the average outlet temperature of the plurality of heat source devices and the inlet temperature of each heat source device,
With a load factor calculation unit that obtains the load factor of each heat source device from the outlet temperature of each heat source device, the inlet temperature, the design temperature difference, the variable flow rate load factor, and the preset constant flow rate load factor of the constant flow rate pump. With
The second flow rate calculation unit repeatedly calculates the total flow rate of the variable flow rate by changing the constant flow rate pump having a low operation priority to the variable flow rate pump until the total flow rate of the variable flow rate becomes larger than 0.
When the variable flow rate load factor is smaller than the preset operating lower limit load factor of the variable flow rate pump, the flow rate load factor calculation unit replaces the variable flow rate load factor with the operating lower limit load factor. The bypass flow rate is calculated from the replaced variable flow rate, and the bypass flow rate is calculated.
When the load factor exceeds the maximum load factor of each heat source device, the load factor calculation unit determines the outlet temperature of the heat source device until all the load factors of each heat source device become equal to or less than the maximum load factor. Is changed to the outlet temperature when operating at the device upper limit load factor of the device, and the average outlet temperature and the inlet temperature are obtained and the load factor is repeatedly calculated.
The calculation unit is a simulation system in a heat source facility that calculates the production amount of the heat medium based on the calculated load factor. The plurality of heat source equipment includes at least one of a cold water system equipment, a hot water system equipment, and a low cold water system equipment, and the heat source equipment is a power source used in the plurality of heat source equipment and / or the heat load side equipment group. Further includes a power generation system equipment for supplying heat and a boiler system equipment for supplying steam used in the heat load side equipment group, and the calculation unit determines the amount of power used or manufactured based on the load factor. The simulation system in the heat source equipment according to claim 5, wherein the amount of steam used or the amount of production is calculated before the calculation, and the amount of heat medium produced is calculated before the amount of steam used or the amount of production is calculated. .. A computer program for executing a simulation system in the heat source equipment according to claim 5 or 6. A recording medium on which the computer program according to claim 7 is recorded.

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