JP2016217552A - Cooperation steam system - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a cooperation steam system which prevents system efficiency from deteriorating by a load factor of one part of steam boosting devices deteriorates.SOLUTION: A cooperation steam system 100 includes a plurality of steam systems 1A, 1B, 1C and a unit number control device 400. The plurality of steam systems 1A, 1B, 1C include: steam generating devices 10A, 10B, 10C; steam boosting devices 20A, 20B, 20C; and flow regulating valves 19A, 19B, 19C for adjusting a flow rate of a heat source fluid supplied to the steam generating devices 10A, 10B, 10C respectively. The unit number control device 400 includes: an average load rate calculation unit 420 for calculating an average value of load factors of the plurality of steam boosting devices 20, in the case where a difference of the load factors between the steam boosting device 20 whose load factor is the highest and the steam boosting device 20 whose load factor is the lowest exceeds a first threshold value; and a load factor control unit 430 for controlling an opening of the flow regulating valve 19 so that the load factors of the plurality of steam boosting devices become the average value.SELECTED DRAWING: Figure 3

Description

  The present invention relates to a steam generator that generates steam using a heat source fluid such as hot water as a heat source, and a cooperative steam system that includes a plurality of steam systems each having a steam booster that boosts the steam generated by the steam generator.

  Conventionally, a steam system including a steam generator that generates steam using a heat source fluid such as hot water as a heat source, and a steam booster that boosts the steam generated by the steam generator has been proposed (for example, Patent Documents). 1). In such a steam system, the low-pressure steam generated by the steam generator is boosted by the steam booster and then supplied to the steam-using device.

JP 2008-138924 A

By the way, when the temperature of the heat source fluid is high or when the circulation amount of the heat source fluid is large, that is, when the amount of heat recoverable from the heat source fluid is large, a plurality of the steam systems described above are arranged, and the plurality of steam systems. By performing heat recovery in cooperation with each other, the heat of the heat source fluid can be used more effectively. Here, when a plurality of steam systems are operated in cooperation, it is preferable that the operating states of the plurality of steam systems are leveled.
That is, the steam booster boosts the low-pressure steam by rotating the compressor using energy (electric power). The energy efficiency of the steam booster decreases as the compressor rotational speed is lower (load factor is lower) and the amount of energy used is greater than the amount of steam that is compressed. Therefore, when a plurality of steam systems are operating, if the state of low load factor of some of the steam boosters continues, the steam boost is more effective than the energy saving effect of heat recovery from the heat source fluid. In some cases, the energy cost becomes excessive, and the cost merit for operating the steam system may decrease.

  Therefore, an object of this invention is to provide the cooperation steam system which can prevent that the efficiency of a system falls by reducing the load factor of some steam pressurization apparatuses.

  The present invention is a cooperative steam system including a plurality of steam systems and a number control device that controls the plurality of steam systems, and each of the plurality of steam systems generates low-pressure steam using a heat source fluid as a heat source. The steam generator, a steam booster that boosts the low-pressure steam generated in the steam generator, and a flow rate adjustment valve that adjusts the flow rate of the heat source fluid supplied to the steam generator, the number control The apparatus includes a load factor acquisition unit that acquires a load factor of a plurality of the steam boosters, a load factor of the steam booster having the highest load factor among the steam boosters in operation, and a load factor of the highest When the difference between the low steam pressure booster and the load factor of the steam booster exceeds a first threshold value, the average value of the load factors of the plurality of operating steam boosters acquired by the load factor acquisition unit is calculated. A load factor control for controlling the opening degree of the flow rate adjustment valve so that the load factor of the plurality of steam boosting devices in operation is equal to the average value calculated by the average load factor calculator A cooperative steam system.

  Further, the cooperative steam system is configured such that the load factor control is performed when load factors of the plurality of steam boosters that are operating converge within a first range including an average value calculated by the average load factor calculator. It is preferable to further include a load factor control stop unit that terminates the control by the unit.

  ADVANTAGE OF THE INVENTION According to this invention, the cooperation steam system which can prevent that the efficiency of a system falls by reducing the load factor of some steam pressurization apparatuses can be provided.

It is a figure which shows the structure of the cooperation steam system which concerns on one Embodiment of this invention. It is a figure which shows the structure of the steam system which comprises a cooperation steam system. It is a functional block diagram which shows the structure of a number control apparatus.

  Hereinafter, a preferred embodiment of the cooperative steam system of the present invention will be described with reference to the drawings. The cooperative steam system 100 according to the present embodiment includes a plurality of steam systems 1 that generate steam by using a cooling water that cools the gas engine 200 as a waste heat source as a heat source fluid and pressurize the steam. More specifically, the cooperative steam system 100 includes a cooling water circulation line 210 through which cooling water for cooling the gas engine 200 circulates, a plurality of (in this embodiment, three) steam systems 1A, 1B, and 1C, A discharge steam line 40 through which the discharged steam discharged from the plurality of steam systems 1A, 1B, 1C flows, a steam header 300 in which the steam flowing through the discharge steam line 40 is gathered, and a plurality of steam systems 1A, And a unit number control device 400 for controlling 1B and 1C. The “line” is a general term for a line capable of flowing a fluid such as a flow path, a path, and a pipe line.

For example, the gas engine 200 is driven by using gas as fuel to generate electric power.
The cooling water circulation line 210 circulates cooling water that cools the gas engine 200. The cooling water circulation line 210 is discharged from the hot water supply line 211 that supplies the high-temperature cooling water (hot water) heat recovered in the gas engine 200 to the steam systems 1A, 1B, and 1C, and the steam systems 1A, 1B, and 1C. The hot water discharge line 212 for supplying the warm water to the gas engine 200, the bypass line 213 for bypassing the hot water supply line 211 and the hot water discharge line 212, and the second bypass line 214 for bypassing the hot water discharge line 212 are provided.

  The upstream side of the hot water supply line 211 is connected to the gas engine 200. The downstream side of the hot water supply line 211 branches into three and is connected to steam systems 1A, 1B, 1C (steam generators 10A, 10B, 10C described later), respectively.

The bypass line 213 connects the hot water supply line 211 and the hot water discharge line 212. A three-way valve 215 as a cooling water supercooling prevention valve is disposed at a connection portion between the hot water supply line 211 and the bypass line 213. This three-way valve 215 switches the flow path of the hot water led out from the gas engine 200 and flowing through the hot water supply line 211 to the steam system 1A, 1B, 1C side or the bypass line 213 side. More specifically, the three-way valve 215 is configured such that when the temperature of warm water flowing through the warm water supply line 211 falls below a preset first reference temperature (for example, 115 ° C.), the warm water flow path is on the bypass line 213 side. It is switched to become. Thereby, it is preventing that the temperature of a cooling water falls too much. In the present embodiment, the three-way valve 215 is configured by a motor valve.
The flow path of the three-way valve 215 is controlled by a control device (not shown) that controls the operation of the gas engine 200, for example.

  The upstream sides of the hot water discharge line 212 are connected to steam systems 1A, 1B, and 1C (steam generators 10A, 10B, and 10C described later), respectively. The hot water discharge lines 212 connected to the steam systems 1A, 1B, and 1C merge on the downstream side, and then connected to the gas engine 200.

A cooler 216, a first temperature sensor 217, a second temperature sensor 218, and a flow meter 219 are arranged in the hot water discharge line 212.
The cooler 216 performs heat recovery from the hot water flowing through the hot water discharge line 212.
The first temperature sensor 217 is disposed on the upstream side of the cooler 216 in the warm water discharge line 212 and measures the temperature of warm water before being introduced into the cooler 216.
The second temperature sensor 218 is arranged on the downstream side of the cooler 216 in the warm water discharge line 212 and measures the temperature of the warm water after heat recovery in the cooler 216.
The flow meter 219 is disposed on the downstream side of the second temperature sensor 218 and measures the flow rate of hot water flowing through the hot water discharge line 212.

  The second bypass line 214 bypasses the upstream side and the downstream side of the cooler 216 in the hot water discharge line 212. In the present embodiment, the second bypass line 214 connects the upstream side of the first temperature sensor 217 and the downstream side of the flow meter 219 to bypass the cooler 216. A three-way valve 220 is disposed at a connection portion between the upstream side of the second bypass line 214 and the hot water discharge line 212. The three-way valve 220 switches the flow path of the hot water discharged from the steam systems 1A, 1B, 1C and flowing through the hot water discharge line 212 to the cooler 216 side or the second bypass line 214 side. More specifically, the three-way valve 220 is configured such that when the temperature of warm water flowing through the warm water discharge line 212 falls below a preset second reference temperature (for example, 118 ° C.), the warm water flow path becomes the second bypass line. It is switched so as to be on the 214 side. Thereby, it is preventing that the temperature of a cooling water falls too much. In the present embodiment, the three-way valve 220 includes a temperature sensor that measures the temperature of hot water and a switching mechanism (none of which is shown) that switches the flow path based on the temperature measured by the temperature sensor. Consists of.

The steam systems 1 </ b> A, 1 </ b> B, and 1 </ b> C are arranged in parallel to the cooling water circulation line 210. The steam systems 1A, 1B, and 1C include steam generators 10A, 10B, and 10C that generate steam, and steam boosters 20A, 20B, and 20C that boost the steam generated in the steam generators 10A, 10B, and 10C, respectively. And low-pressure steam supply lines 30A, 30B, and 30C that connect the steam generators 10A, 10B, and 10C and the steam boosters 20A, 20B, and 20C.
Since steam system 1A, 1B, 1C is provided with the same structure, the code | symbol of A, B, C is abbreviate | omitted in FIG. 2, and the specific structure of the steam system 1 is shown.

  The steam generator 10 generates steam using a relatively low-temperature heat source fluid such as waste heat from jacket cooling water of the gas engine 200. As shown in FIG. 2, the steam generator 10 includes a tank unit 11, a tube 12 and a spray nozzle 13 disposed inside the tank unit 11, a spray water supply line 16, a makeup water line 17, and hot water. A bypass line 18, a three-way valve 19 as a flow rate adjustment valve, and a steam control unit 50 are provided.

The tank part 11 constitutes a main body part in the steam generator 10. The inside of the tank unit 11 is maintained at a negative pressure or a low pressure (for example, about −0.05 MPaG to 0.1 MPaG), and steam is generated inside the tank unit 11. A base end portion of a low-pressure steam supply line 30 described later is connected to the upper portion of the tank portion 11.
The tank unit 11 is provided with a safety valve 32. When the pressure inside the tank unit 11 exceeds a predetermined pressure (set pressure), the safety valve 32 releases the steam to the outside and reduces the pressure inside the tank unit 11 (steam generating device 10).

  The tube 12 extends in the horizontal direction inside the tank portion 11. More specifically, a plurality of tubes 12 are arranged in the tank portion 11 with a predetermined interval in the horizontal direction, and a plurality of tubes 12 are also arranged in the height direction with a predetermined interval. The distal end side of the hot water supply line 211 is connected to one end side (inlet side) of the tube 12, and the proximal end side of the hot water discharge line 212 is connected to the other end side (outlet side). Thereby, warm water as a heat source fluid flows through the tube 12.

The spray nozzle 13 is disposed above the tube 12 inside the tank unit 11. The spray nozzle 13 sprays water toward the tube 12.
The spray water supply line 16 connects the lower part of the tank unit 11 and the spray nozzle 13, and supplies water stored in the lower part of the tank unit 11 to the spray nozzle 13 as spray water. A spray water pump 161 is disposed in the spray water supply line 16.
The spray water pump 161 pumps water stored in the tank unit 11 to the spray nozzle 13.

The makeup water line 17 connects the tank unit 11 and a storage tank or the like (not shown) that stores water. The makeup water line 17 supplies makeup water to the tank unit 11. A makeup water pump 171 is disposed in the makeup water line 17.
The makeup water pump 171 pressurizes water supplied from a storage tank or the like and supplies it to the inside of the tank unit 11.

The hot water bypass line 18 connects the upstream side of the inlet of the tube 12 and the downstream side of the outlet, and bypasses the hot water supply line 211 and the hot water discharge line 212.
The three-way valve 19 is disposed at a connection portion between the hot water supply line 211 and the hot water bypass line 18. The three-way valve 19 adjusts the amount of hot water flowing from the hot water supply line 211 to the steam generator 10 side and the flow rate of hot water flowing to the hot water bypass line 18 side. In the present embodiment, the three-way valve 19 is configured by a motor valve capable of adjusting the opening degree.

  The steam control unit 50 controls the amount of low-pressure steam generated by the steam generator 10 by adjusting the opening of the three-way valve 19. Specifically, the steam control unit 50 opens the three-way valve 19 according to the pressure of the discharge steam measured by the discharge steam pressure sensor 43 described later and the pressure of the low pressure steam measured by the low pressure steam pressure sensor 31. The amount of steam produced by the steam generator 10 is controlled.

According to the steam generator 10 described above, in a state where the flow path from the hot water supply line 211 to the hot water bypass line 18 is closed by the three-way valve 19, first, hot water (for example, about 90 ° C.) serving as a heat source from the gas engine 200. Is supplied to the tube 12 through the hot water supply line 211. The hot water supplied to the tube 12 is introduced into the tube 12 disposed inside the tank unit 11.
On the other hand, spray water is sprayed from the spray nozzle 13 toward the tube 12 inside the tank portion 11. Further, the inside of the tank unit 11 is maintained at a negative pressure or a low pressure (for example, about −0.05 MPaG to 0.1 MPaG). As a result, the hot water flowing through the tube 12 is deprived of heat by the spray water, drops to about 85 ° C., and is discharged through the hot water discharge line 212.

  In addition, a thin liquid film is formed on the surface of the tube 12 through which warm water flows by spraying water at about 80 ° C. from the spray nozzle 13. As described above, in a state where the inside of the tank unit 11 is maintained at a negative pressure, a thin liquid film is formed on the surface of the tube 12, so that it is sprayed by the hot water flowing through the inside of the tube 12 and the spray nozzle 13. Even when the temperature difference with water is relatively small (for example, about 10 ° C.), steam can be efficiently generated.

The steam generated inside the tank unit 11 is led out from the low-pressure steam supply line 30.
The water that has not become steam inside the tank unit 11 is stored in the lower part of the tank unit 11. The water stored in the lower part of the tank unit 11 is pumped up to the spray nozzle 13 by the spray water pump 161 through the spray water supply line 16 and sprayed on the tube 12 again.
When the water stored in the tank unit 11 is reduced, the supply water is supplied from the supply water line 17 to the tank unit 11.

  Further, the amount of steam generated inside the tank unit 11 can be adjusted by adjusting the flow rate of the hot water supplied to the tube 12 by adjusting the opening of the three-way valve 19.

The steam booster 20 sucks and compresses the low-pressure steam (for example, −0.05 MPaG to 0.1 MPaG) generated in the steam generator 10 to boost the pressure. The steam booster 20 includes a compression unit 21 that compresses low-pressure steam, and a compression control unit 22 that controls the operation of the compression unit 21.
The compression unit 21 is configured by, for example, a screw-type steam compressor, and boosts low-pressure steam to about 0.4 MpaG to 0.8 MPaG.
The compression control unit 22 controls the operation (load factor) of the compression unit 21 based on the pressure of the steam flowing through the low-pressure steam supply line 30 (the pressure of the steam introduced into the compression unit 21). More specifically, the compression control unit 22 sets the steam booster 20 so that the pressure of the steam flowing through the low-pressure steam supply line 30 becomes a set target pressure (for example, 0.04 MPa to 0.05 MPa). Control the load factor.

  That is, when the steam pressure in the low-pressure steam supply line 30 is higher than the target pressure, the compression control unit 22 sets the load factor to the maximum (load factor 100%) and the steam booster 20 (compression unit 21). Drive. As a result, an upper limit amount of steam is sucked into the steam pressure increasing device 20, and the steam pressure in the low pressure steam supply line 30 tends to decrease. Even when the steam booster 20 is driven at a load factor of 100%, the steam booster 20 operates at a load factor of 100% if the steam pressure in the low-pressure steam supply line 30 exceeds the target pressure. Continue.

On the other hand, when the steam pressure in the low-pressure steam supply line 30 falls below the target pressure, the compression control unit 22 decreases the load factor of the steam booster 20 (compression unit 21). Thereby, the amount of steam sucked into the steam booster 20 decreases, and the steam pressure of the low-pressure steam supply line 30 increases.
In this way, by controlling the steam pressure of the low-pressure steam supply line 30 to be the target pressure, the steam generator 10 can generate steam efficiently and stably.

The low pressure steam supply line 30 supplies the low pressure steam generated in the steam generator 10 to the steam booster 20. A low pressure steam pressure sensor 31 is disposed in the low pressure steam supply line 30.
The low pressure steam pressure sensor 31 measures the steam pressure (pressure of the low pressure steam) inside the low pressure steam supply line 30.

As shown in FIG. 1, the discharge steam line 40 includes a plurality of first discharge steam lines 41A, 41B, and 41C whose proximal ends are connected to the steam systems 1A, 1B, and 1C, respectively. And a collective steam line 42 connected to the front end side of the discharge steam lines 41 </ b> A, 41 </ b> B, 41 </ b> C and having the front end side connected to the steam header 300.
Discharge steam pressure sensors 43A, 43B, and 43C and on-off valves 44A, 44B, and 44C are disposed in the plurality of first discharge steam lines 41A, 41B, and 41C, respectively.
The discharge steam pressure sensors 43A, 43B, and 43C measure the vapor pressure (discharge steam pressure) inside the first discharge steam lines 41A, 41B, and 41C.
The on-off valves 44A, 44B, 44C open and close the flow paths of the first discharge steam lines 41A, 41B, 41C.

The collective steam line 42 collects steam flowing through the plurality of first discharge steam lines 41 </ b> A, 41 </ b> B, and 41 </ b> C and supplies the steam to the steam header 300.
The steam header 300 collects steam generated in the plurality of steam systems 1A, 1B, and 1C. The steam header 300 is generated by steam generated by an exhaust gas boiler (not shown) that generates steam using heat stored in the exhaust gas of the gas engine 200 or by another boiler (not shown). Steam is also collected.
A header pressure sensor 310 is disposed on the steam header 300. The header pressure sensor 310 measures the vapor pressure (header pressure) inside the vapor header 300.
The steam collected in the steam header 300 is supplied to steam use equipment (not shown).

The number control device 400 controls the operation of the cooperative steam system 100 (the operations of the plurality of steam systems 1A, 1B, 1C).
In the present embodiment, the number control device 400 includes the header pressure measured by the header pressure sensor 310, the load factor of the steam booster 20, and the temperature of hot water flowing through the hot water discharge line 212 measured by the first temperature sensor 217. The number of steam systems to be operated is controlled based on the above. For example, in the state where one steam system 1A is operating, the number control device 400 has a header pressure measured by the header pressure sensor 310 that is lower than a preset increase base reference pressure, and the load of the steam booster 20A The steam system 1B is activated when the rate exceeds the preset base addition load factor and the temperature of the hot water measured by the first temperature sensor 217 exceeds the preset base reference temperature; Increase the number of steam systems in operation.

Here, when operating the some steam system 1 in cooperation, it is preferable that the operating state of the some steam system 1 is equalized. Therefore, in the present embodiment, the number control device 400, when two or more steam systems 1 are operating, when the load factor difference of the operating steam booster 20 exceeds a predetermined threshold The operation of the plurality of steam systems 1 is controlled so as to reduce the difference in load factor, and the operation state of the plurality of steam systems 1 is leveled.
In order to realize such a function, as shown in FIG. 3, the number control device 400 includes a load factor acquisition unit 410, an average load factor calculation unit 420, a load factor control unit 430, and a load factor control stop unit. 440.

  The load factor acquisition unit 410 acquires the load factors of the plurality of steam boosters 20A, 20B, and 20C.

The average load factor calculation unit 420 has a difference between the load factor of the steam booster 20 having the highest load factor and the load factor of the steam booster 20 having the lowest load factor among the steam boosters 20 in operation. When a preset first threshold value (for example, 15%) is exceeded, the average value of the load factors of the plurality of operating steam boosters 20 acquired by the load factor acquisition unit 410 is calculated.
For example, in the cooperative steam system 100 in which the first threshold is set to 15%, the load factor of the steam booster 20A acquired by the load factor acquisition unit 410 in a state where the two steam systems 1A and 1B are operating. Is 90% and the load factor of the steam booster 20B is 70%, the average load factor calculation unit 420 calculates the average value of the load factors of the two steam boosters 20A, 20B as 80%.
If the number of operating steam systems 1 is three or more, the average load factor calculation unit 420 calculates the average value of the load factors of all the steam boosters 20 that are operating.

  The load factor control unit 430 controls the opening degree of the three-way valve 19 of the steam generating device 10 so that the load factors of the plurality of steam boosting devices 20 that are operating become the average value calculated by the average load factor calculating unit 420. To do. More specifically, in the above-described case, the load factor control unit 430 determines the opening of the three-way valve 19A of the steam generator 10A of the steam system 1A in which the load factor of the steam booster 20A is 90% on the tube 12 side. Control to reduce the amount of hot water flowing through In addition, the load factor control unit 430 increases the amount of hot water flowing to the tube 12 side through the opening of the three-way valve 19B of the steam generator 10B of the steam system 1B in which the load factor of the steam booster 20B is 70%. To control.

Thereby, in the steam generator 10A, the amount of steam generated is reduced by reducing the amount of hot water flowing to the tube 12 side. As a result, the amount of steam supplied to the low-pressure steam supply line 30A decreases, and the load factor of the steam booster 20A decreases. On the other hand, in the steam generator 10B, the amount of steam generated increases as the amount of hot water flowing to the tube 12 increases. As a result, the amount of steam supplied to the low pressure steam supply line 30B increases, and the load factor of the steam booster 20A increases.
In this way, both the load factor of the steam booster 20A and the load factor of the steam booster 20B are toward the average value.

  The load factor control stop unit 440 is within a first range in which the load factors of the plurality of steam boosters 20 that are in operation include the average value calculated by the average load factor calculation unit 420 (for example, an average value of ± 3%). When it converges to (range), the control by the load factor control unit 430 is terminated. Specifically, in the above-described case, when the load factor of the steam pressure increasing device 20A decreases to 83% and the load factor of the steam pressure increasing device 20B increases to 77%, the load factor control stop unit 440 includes the load factor control unit 430. The opening control of the three-way valve 19 is terminated. Thereby, after the load factors of the plurality of steam boosters 20 are leveled, the three-way valve 19 of the steam generator 10 can be returned to the normal control by the steam controller 50.

  According to the cooperation steam system 100 of this embodiment demonstrated above, there exist the following effects.

  (1) When operating several steam system 1A, 1B, 1C in cooperation, it is preferable that the operating state of several steam system 1A, 1B, 1C is equalized. Therefore, the cooperative steam system 100 includes a plurality of steam systems 1A, 1B, and 1C and a number control device 400 that controls the plurality of steam systems 1A, 1B, and 1C. And when the plurality of steam systems 1A, 1B, 1C are operating, the number control device 400 is operated when the difference in load factor between the respective steam boosters 20A, 20B, 20C exceeds the first threshold. An average load factor calculating unit 420 that calculates an average value of the load factor of the steam booster 20 that is in operation, and an average value that is calculated by the average load factor calculating unit 420. And a load factor control unit 430 for controlling the opening degree of the three-way valve 19 for supplying hot water to the steam generator 10. Thereby, when a large difference occurs in the load factor of the plurality of steam boosters 20A, 20B, and 20C in a state where the plurality of steam systems 1A, 1B, and 1C are operated, the steam generators 10A, 10B, and 10C are generated. By adjusting the flow rate of the hot water supplied to the steam generator, the amount of steam generated in the steam generators 10A, 10B, 10C can be adjusted, and the load factor of the plurality of steam boosters 20A, 20B, 20C can be leveled. Therefore, it can prevent that the efficiency of a system falls because the load factor of some vapor pressure | voltage rise apparatus 20A, 20B, 20C falls.

  (2) When the load factor of the plurality of steam boosters 20A, 20B, and 20C operating the number control device 400 converges within the first range including the average value calculated by the average load factor calculator 420 The load factor control stop unit 440 for terminating the control by the load factor control unit 430 is included. Thereby, when the load factor of the plurality of steam boosters 20A, 20B, and 20C converges within a certain range by the control of the load factor control unit 430, the control of the three-way valve 19 by the load factor control unit 430 can be terminated. Therefore, when the operating states of the plurality of steam systems 1A, 1B, and 1C are leveled, the control of the steam systems 1A, 1B, and C can be quickly returned to the normal control.

As mentioned above, although preferable one Embodiment of the cooperation steam system 100 of this invention was described, this invention is not restrict | limited to embodiment mentioned above, It can change suitably.
For example, in the present embodiment, the cooperative steam system 100 is configured by the three steam systems 1A, 1B, and 1C, but is not limited thereto. That is, a cooperation steam system may be constituted by two steam systems, and may be constituted by four or more steam systems.

  In the present embodiment, the low pressure steam pressure sensor 31 is disposed in the low pressure steam supply line 30 and the pressure of the steam flowing through the low pressure steam supply line 30 is measured. However, the present invention is not limited to this. That is, since the pressure of the steam flowing through the low-pressure steam supply line 30 is equal to the pressure of the steam in the steam generator 10 (tank part 11), the low-pressure steam pressure sensor may be arranged in the steam generator (tank part). .

  Moreover, in this embodiment, although the flow regulating valve was comprised by the three-way valve 19, it is not restricted to this. That is, the flow rate adjusting valve may be configured by combining a plurality of valves.

  Moreover, in this embodiment, although the gas engine 200 was used as a waste heat source, it is not restricted to this. That is, a diesel engine or a gasoline engine may be used as a waste heat source.

1A, 1B, 1C Steam system 10A, 10B, 10C Steam generator 19A, 19B, 19C Three-way valve (flow control valve)
20A, 20B, 20C Steam booster 100 Coordinate steam system 400 Number control device 410 Load factor acquisition unit 420 Average load factor calculation unit 430 Load factor control unit 440 Load factor control stop unit

Claims (2)

A cooperative steam system comprising a plurality of steam systems and a number control device for controlling the plurality of steam systems,
Each of the plurality of steam systems is
A steam generator that generates low-pressure steam using a heat source fluid as a heat source;
A steam booster that boosts the low-pressure steam generated in the steam generator;
A flow rate adjusting valve that adjusts the flow rate of the heat source fluid supplied to the steam generator,
The number controller is
A load factor acquisition unit for acquiring a load factor of a plurality of the steam boosters;
When the difference between the load factor of the steam booster with the highest load factor and the load factor of the steam booster with the lowest load factor among the steam boosters in operation exceeds the first threshold An average load factor calculating unit that calculates an average value of the load factors of the plurality of operating steam boosters acquired by the load factor acquiring unit;
A cooperative steam comprising: a load factor control unit that controls an opening degree of the flow rate adjusting valve so that a load factor of the plurality of steam boosters that are operating is an average value calculated by the average load factor calculation unit system.   Load that terminates control by the load factor control unit when load factors of the plurality of steam boosters that are operating converge within a first range that includes the average value calculated by the average load factor calculation unit The cooperative steam system according to claim 1, further comprising a rate control stop unit.

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