WO2009147873A1

WO2009147873A1 - Steam system

Info

Publication number: WO2009147873A1
Application number: PCT/JP2009/052790
Authority: WO
Inventors: 康夫越智; 大輔森; 靖国田中; 裕介岡本
Original assignee: 三浦工業株式会社
Priority date: 2008-06-05
Filing date: 2009-02-18
Publication date: 2009-12-10
Also published as: JP2009293502A; JP4329875B1

Abstract

When an air compressor is driven using a steam engine, the air compressor is controlled while taking account of a load for using steam as well as a load for using compressed air. Energy is saved by recovering heat from the steam engine and the air compressor. An air compressor (4) is driven by a steam engine (3) which generates power by using steam from a boiler (2). A load for using steam is monitored by a pressure sensor (25) provided in a steam header (21). A load for using compressed air is monitored by a pressure sensor (27) provided in a compressed air passage (26). Steam supply to the steam engine (3) is controlled based on pressures detected by pressure sensors (25, 27). Steam and drain leaking from the shaft seal portion of the steam engine (3), and drain generated from the steam engine (3) are supplied to a water supply tank (5) via recovery passages (28, 29). Supply water to the water supply tank (5) is supplied through the compressor (4).

Description

Steam system

The present invention relates to a steam system that uses a steam to drive a compressor or the like to reduce power consumption.
This application claims priority based on Japanese Patent Application No. 2008-147545 filed in Japan on June 5, 2008, the contents of which are incorporated herein by reference.

In Patent Document 1 below, an air compressor (2) is driven by a screw expander (1), and when the load of the air compressor (2) varies, the steam flowing into the screw expander (1) is controlled. (10) is controlled and responded, and by controlling the bypass valve (9) provided between the steam inflow side and the steam outflow side of the screw expander (1), the steam is controlled regardless of the load fluctuation. A method of keeping the back pressure of steam on the outflow side constant is disclosed. Here, the bypass valve (9) is controlled by detecting the back pressure of the steam outlet pipe (5) from the screw expander (1) by the detector (20). Further, the control of the adjusting valve (10) is performed by detecting the rotational speed of the drive shaft of the screw expander (1) by the detector (23).
JP-A-63-45403 (Claims, FIG. 1, page 2, lower left column, lines 1-5)

In the case of the invention disclosed in Patent Document 1, the amount of steam supplied to the screw type expander is controlled by adjusting the adjusting valve in order to keep the rotation constant despite the load fluctuation of the air compressor. However, the capacity control of the air compressor is performed by an unloader (gazette page 2, lower right column, line 18-page 3, upper left column, line 5). Alternatively, the capacity control of the air compressor is performed by changing the rotation speed of the screw expander by controlling the amount of steam supplied to the screw expander by an adjusting valve (see the upper left column, page 5-5- 9). However, it is not intended to detect a load change of the air compressor and to respond quickly and accurately to the load change.

In the case of the invention disclosed in Patent Document 1, steam supply to the screw expander cannot be controlled in consideration of the use load of steam. That is, in the case of the invention disclosed in Patent Document 1, control cannot be performed based on both the use load of steam and the use load of fluid discharged from the compressor.

Furthermore, in the case of the invention disclosed in Patent Document 1, the capacity control of the air compressor is performed by an unloader. Therefore, the screw expander has an unnecessary operation at the time of unloading, and thus heat loss occurs, and heat generated at that time is not recovered, so that it is not possible to save energy.

The problem to be solved by the present invention is to control not only the fluid load but also the steam load with a simple configuration and control, and to save energy by heat recovery.

The present invention has been made to solve the above problems, and the invention according to claim 1 is a motor that generates power using steam from a boiler, and is driven by the motor to discharge or inhale a fluid. A bypass path for supplying steam to the location where the steam after use in the prime mover is supplied without going through the prime mover, a bypass valve provided in the bypass path, the steam from the prime mover, and the A controller that controls steaming to the prime mover based on a steam load at a location where steam from the bypass passage is supplied and a fluid load in a space where fluid is discharged or sucked by the driven machine; and The water supply to the boiler is stored and the steam or drain leaking from the shaft seal of the prime mover, the drain generated by the prime mover, or the heat generated by the driven machine, is stored or replenished. A steam system, characterized in that it comprises a water supply tank is warmed.

According to the first aspect of the present invention, steam supply to the motor is controlled in consideration of not only fluid load but also steam load, steam or drain leaking from the shaft seal of the motor, drain generated by the motor, Alternatively, it is possible to save energy by using the heat generated by the driven machine to warm the water stored in the water supply tank or the makeup water to the water supply tank.

According to a second aspect of the present invention, the steam leaking from the shaft seal portion of the prime mover and / or the drain leaking from the shaft seal portion of the prime mover are supplied to the water supply tank, and the stored water in the water supply tank is The steam system according to claim 1, wherein the steam system is warmed.

According to the second aspect of the present invention, the stored water in the water supply tank is warmed by the steam leaking from the shaft seal portion of the prime mover and / or the drain leaking from the shaft seal portion of the prime mover, so that heat loss can be prevented. .

The invention according to claim 3 is characterized in that the drain generated in the prime mover is supplied to the water supply tank, and the stored water in the water supply tank is warmed. System.

According to the third aspect of the present invention, since the water stored in the water supply tank is warmed by the drain generated by the prime mover, heat recovery from the prime mover can be effectively achieved.

Invention of Claim 4 performs cooling of the said driven machine using the stored water in the said water supply tank, or the replenishment water to the said water supply tank, so that the stored water in the said water supply tank or the said water supply tank is supplied. The steam system according to any one of claims 1 to 3, wherein the makeup water is warmed.

According to the fourth aspect of the present invention, the stored water in the water supply tank or the makeup water to the water supply tank is warmed by the heat of the driven machine, so that energy saving can be achieved.

Furthermore, the invention described in claim 5 is further provided with a second driven machine that is driven by an electric motor and discharges or sucks fluid, and is provided at a location where steam from the prime mover and steam from the bypass path are supplied. Steam supply to the prime mover is controlled based on the steam load and the fluid load in the space where the fluid is discharged or sucked by each driven machine, and in the space where the fluid is discharged or sucked by each driven machine Based on the fluid load, the electric motor is controlled, and the second driven machine is cooled using the stored water in the water supply tank or the makeup water to the water supply tank, so that the stored water in the water supply tank or The steam system according to any one of claims 1 to 4, wherein makeup water to the water supply tank is warmed.

According to the fifth aspect of the invention, the heat stored in the water supply tank or the makeup water to the water supply tank is warmed by the heat of the second driven machine, so that energy saving can be achieved. In addition to the prime mover that generates power using steam from the boiler, an electric motor that drives the second driven machine is provided, so that fluid can be discharged or sucked stably regardless of the steam load.

According to the steam system of the present invention, it is possible to control not only the fluid load but also the steam load with a simple configuration and control, and to save energy by heat recovery.

It is the schematic which shows one Example of the steam system of this invention. It is a schematic structure figure of an example of the screw type steam engine of the steam system of Drawing 1, and shows a part in section.

Explanation of symbols

1 Steam system 2 Boiler 3 Steam engine (motor)
4 Compressor (driven machine)
5 Water Supply Tank 16 Electric Motor 18 First Steam Header 19 Steam Supply Valve 21 Second Steam Header 22 Bypass Path 23 Bypass Valve 24 Controller 25 First Pressure Sensor 26 Compressed Air Path 27 Second Pressure Sensor 28 Leakage Heat Recovery Path 29 Drain Recovery Road 31 water supply channel

Next, an embodiment of the present invention will be described.
The steam system of the present invention includes a prime mover that generates power using steam from a boiler, and a driven machine such as a compressor or a vacuum pump that is driven by the prime mover.

As is well known, a boiler heats water supplied from a water supply tank and vaporizes it. Then, the steam can be supplied to steam utilization equipment such as a prime mover.

The prime mover is a steam engine that generates power using steam. The steam engine may be a steam turbine, but is preferably a screw steam engine. A screw-type steam engine is an apparatus in which steam is introduced between screw rotors that mesh with each other, and the steam is expanded and decompressed while rotating the screw rotor by the steam, and power is obtained by rotation of the screw rotor at that time.

The driven machine is a device driven by a steam engine to discharge or suck fluid. Specifically, the driven machine is a pump, a blower, a compressor, a vacuum pump, or the like. In the case of a pump, a blower, or a compressor, the driven machine discharges a fluid, and in the case of a vacuum pump, the driven machine sucks the fluid.

The driven machine is, for example, an air compressor. The type of the air compressor is not particularly limited, such as a reciprocating type or a rotary type, but is preferably a screw type compressor. A screw compressor is a device that sucks gas between screw rotors that mesh with each other and rotate, and compresses and discharges the gas by rotation of the screw rotor.

Steam is supplied to the steam engine from the boiler via the steam supply path. Steam from the boiler may be supplied to a steam header (referred to as a first steam header), and the steam in the steam header may be supplied to the steam engine via a steam supply path.

Steam after use in the steam engine is discharged through the exhaust steam path. Since the steam engine depressurizes steam, it also functions as a pressure reducing valve. Therefore, the steam after use in the steam engine can be used in the same manner as the steam after passing through the conventional pressure reducing valve. That is, conventionally, the steam from the boiler is supplied to the steam using device via the pressure reducing valve. Similarly, the steam after use in the steam engine can be supplied to the steam using device. At this time, the steam from the steam engine may be supplied to the steam header (referred to as the second steam header) via the exhaust steam path, and the steam in the steam header may be supplied to the steam utilization device.

Steam can be supplied to the steam-utilizing equipment via a bypass without going through a steam engine. Typically, the steam from the boiler can be supplied to the exhaust steam path or the second steam header even via the bypass path. At this time, the steam supply path and the exhaust steam path for the steam engine may be connected by a bypass path, or the first steam header and the second steam header may be connected by a bypass path. Moreover, it is good also as supply of a vapor | steam to a waste steam path or a 2nd steam header from a location different from the said boiler via a bypass path. In any case, a bypass valve is provided in the bypass path. The bypass valve may be an electromagnetic valve or an electric valve, but may be a self-reducing pressure reducing valve.

The steam engine is controlled by controlling whether or not steam is supplied to the steam engine. Specifically, a steam supply valve is provided in the steam supply path to the steam engine, and the opening / closing or opening degree of the steam supply valve is controlled. Thereby, the presence / absence or amount of steam supply to the steam engine can be changed, and the presence / absence or output of the steam engine can be changed.

For example, when the steam engine is a steam turbine, the presence or absence of steam supply to the steam turbine may be switched by controlling the opening and closing of the steam supply valve. Thereby, the presence or absence of the action | operation of a steam turbine can be changed. On the other hand, when the steam engine is a screw-type steam engine, the opening / closing of the steam supply valve may be controlled as in the case of the steam turbine, or the opening of the steam supply valve may be controlled. When controlling the opening degree of the steam supply valve, the output of the screw steam engine can be changed by adjusting the amount of steam supply to the screw steam engine.

However, the control of the steam engine is not limited to the above configuration. That is, the steam engine only needs to be able to change the presence or amount of steaming, and it is not always necessary to provide a steaming valve in the steaming path and control the steaming valve. For example, as described above, the steam supply path and the exhaust steam path for the steam engine may be connected by a bypass path, and the opening / closing or opening degree of the bypass valve provided in the bypass path may be controlled. In addition to the steam supply valve, this bypass valve may be provided.

The steam engine is controlled for steam supply based on the fluid load in the space where the fluid is discharged or sucked by the driven machine and the steam load on the outlet side of the steam engine.

Here, the fluid load is a load of the fluid in the space where the fluid is discharged or sucked by the driven machine. Specifically, when the driven machine is a pump, a blower or a compressor, this is the amount of fluid used in the space discharged. When the driven machine is a vacuum pump, this is the amount of fluid in the space to be sucked. That is, when the driven machine is a vacuum pump, if the degree of vacuum is low, there is a fluid load. Any fluid load can be detected by the pressure in the space where the fluid is discharged or sucked by the driven machine.

On the other hand, the steam load is the amount of steam used at the location where steam after use is supplied by the steam engine. This steam load can be detected by the steam pressure at the location where steam after use is supplied by the steam engine. For example, the use load (steam load) of steam can be detected based on the steam pressure in the exhaust steam path from the steam engine or in the second steam header provided at the end thereof. That is, when steam is used in the steam utilization device, the steam pressure in the exhaust steam passage or the second steam header is lowered, so that the steam load can be detected.

Thus, it is easy to detect both fluid load and steam load by pressure. Therefore, steam supply to the steam engine can be controlled based on the pressure in the space where the fluid is discharged or sucked by the driven machine and the steam pressure at the location where the steam after use in the steam engine is supplied. .

By the way, the water stored in the water supply tank or the replenishment water to the water supply tank is warmed by using steam or drain leaking from the shaft seal of the prime mover, drain generated by the prime mover, or heat generated by the driven machine. As the means, the following three embodiments can be mentioned. Of these three embodiments, a plurality of embodiments may be combined.

In the first embodiment, steam leaking from the shaft seal portion of the prime mover and / or drain leaking from the shaft seal portion of the prime mover are supplied to the water supply tank via the leakage heat recovery path. Thereby, the stored water in a water supply tank can be warmed.

In the second embodiment, the drain generated by the prime mover is supplied to the water supply tank via the drain recovery path. Thereby, the stored water in a water supply tank can be warmed. A steam trap is preferably provided in the middle of the drain recovery path.

In the third embodiment, the driven machine is cooled by water stored in the water supply tank or makeup water supplied to the water supply tank. When cooling a driven machine with the stored water in a water supply tank, the stored water in a water supply tank is circulated through the driven machine so that it may return into the water supply tank. On the other hand, when the driven machine is cooled by makeup water to the feed water tank, the makeup water to the feed water tank is supplied to the feed water tank via the driven machine. In either case, the driven machine may be cooled through a medium such as oil.

The steam system of the present invention may further include a second driven machine different from the driven machine (first driven machine) driven by the steam engine.

The second driven machine is a device that discharges or sucks fluid to the space where the fluid is discharged or sucked by the first driven machine, like the first driven machine. Therefore, the second driven machine has the same function as the first driven machine. For example, when the first driven machine is an air compressor, the second driven machine is also an air compressor. However, if the second driven machine has the same function as the first driven machine, the mechanism need not be the same. For example, when the first driven machine is a screw type air compressor, the second driven machine is not limited to the screw type but may be a reciprocating type as long as it is an air compressor.

The second driven machine can be driven by an electric motor. The electric motor is controlled based on a fluid load in a space in which fluid is discharged or sucked by each driven machine. The steam engine is controlled based on a steam load at a location where steam from the steam engine and steam from the bypass path are supplied, and a fluid load in a space where fluid is discharged or sucked by each driven machine. . When the steam engine and the electric motor controlled in this way are not enough to drive the steam engine, it is preferable that the electric motor is auxiliary driven. Further, when the steam engine is stopped, the electric motor can be driven and fluid can be discharged or sucked by the second driven machine.

In such a configuration, the second driven machine may be cooled by the water stored in the water supply tank or the makeup water supplied to the water supply tank. When the second driven machine is cooled by the stored water in the water supply tank, the stored water in the water supply tank is circulated back to the water supply tank via the second driven machine. On the other hand, when the second driven machine is cooled with makeup water to the feed water tank, the makeup water to the feed water tank is supplied to the feed water tank via the second driven machine. In any case, the second driven machine may be cooled through a medium such as oil.

Hereinafter, specific embodiments of the present invention will be described in detail with reference to the drawings.
FIG. 1 is a schematic view showing an embodiment of the steam system of the present invention. The steam system 1 of the present embodiment includes a prime mover 3 that generates power using steam from a boiler 2 and a driven machine 4 that is driven thereby.

As is well known, the boiler 2 heats and vaporizes the water supplied from the water supply tank 5. The water in the water supply tank 5 is supplied to the boiler 2 via the water supply pump 6 and is vaporized in the boiler 2.

The prime mover 3 is a steam engine that receives power from the boiler 2 and generates power. The steam engine 3 may be a steam turbine, but is preferably a screw-type steam engine. FIG. 2 is a schematic structural diagram of an example of a screw-type steam engine, and a part thereof is shown in cross section.

2, the screw steam engine 3 is configured by providing

screw rotors

8 and 8 in a hollow casing 7 so as to mesh with each other. At this time, both end shaft portions of each screw rotor 8 are rotatably held by the casing 7 via the bearings 9. Note that the shaft seal portion of the steam engine 3 is normally a non-contact seal (O-ring or the like) 10, and therefore steam and / or drain leak from the shaft seal portion.

The screw-type steam engine 3 expands steam while rotating the

screw rotors

8 and 8 by the steam introduced from the boiler 2 between the

screw rotors

8 and 8 meshing with each other through the suction port 11. And depressurize. And power can be obtained by rotation of the screw rotor 8 in that case. The decompressed steam is discharged from the steam engine 3 through the discharge port 12.

The driven machine 4 is a device that is driven by the steam engine 3 to discharge or suck a fluid. Specifically, the driven machine 4 is a pump, a blower, a compressor, a vacuum pump, or the like. The driven machine 4 of the present embodiment is an air compressor. The compressor 4 is not particularly limited in type, but is preferably a screw type compressor. A screw compressor is a device that sucks gas between screw rotors that mesh with each other and rotate, and compresses and discharges the gas by rotation of the screw rotor.

The compressor 4 is driven by the steam engine 3. Specifically, the screw rotor of the screw compressor 4 is rotated using the rotational driving force of the screw rotor 8 of the screw steam engine 3. At this time, the output shaft 13 of the steam engine 3 and the input shaft 14 of the compressor 4 are connected by a coupling 15 without a generator. However, the output shaft 13 and the input shaft 14 may be connected via a clutch. In this case, whether or not the compressor 4 is driven by the steam engine 3 can be switched by the clutch. Further, the clutch may include a transmission. In this case, the discharge pressure of the compressor 4 can be changed by changing the gear ratio. Furthermore, the output shaft 13 and the input shaft 14 may be connected via an electric motor (motor). In this case, the drive ratio of the compressor 4 can be changed so that it can be driven by one or both of the steam engine 3 and the electric motor. In the present embodiment, the compressor 4 is connected to the steam engine 3 and the electric motor 16 as shown in FIG. Thus, the compressor 4 can be driven by the steam engine 3 and can also be driven by the electric motor 16.

The steam from the boiler 2 is supplied to the steam engine 3 through the steam supply path 17. In the present embodiment, the steam from the boiler 2 is supplied to the first steam header 18, and the steam of the first steam header 18 is supplied to the steam engine 3 through the steam supply path 17. A steam supply valve 19 is provided in the steam supply path 17 from the first steam header 18 to the steam engine 3. By controlling the opening and closing of the steam supply valve 19, the presence or absence of the operation of the steam engine 3 is switched. However, the output of the steam engine 3 may be adjusted by controlling the opening of the steam supply valve 19.

The steam after being used in the steam engine 3 can be used in various steam utilization devices (not shown). In the present embodiment, the steam from the steam engine 3 is supplied to the second steam header 21 via the exhaust steam path 20, and the steam in the second steam header 21 is supplied to various steam utilizing devices. By the way, the steam engine 3 not only drives the compressor 4 but also functions as a pressure reducing valve. Therefore, the steam after use in the steam engine 3 can be used as it is in various steam utilizing devices as the steam after passing through the pressure reducing valve.

The first steam header 18 and the second steam header 21 are also connected via the bypass path 22. In the illustrated example, in the steam supply passage 17 from the first steam header 18 to the steam engine 3, an upstream portion from the steam supply valve 19 and a midway portion of the exhaust steam passage 20 from the steam engine 3 to the second steam header 21. Are connected by a bypass 22. A bypass valve 23 is provided in the middle of the bypass path 22. The bypass valve 23 may be an electromagnetic valve or an electric valve controlled by the controller 24, but is a self-powered pressure reducing valve in this embodiment. Specifically, the bypass valve 23 mechanically adjusts the opening degree by itself so as to maintain the steam pressure in the second steam header 21 at a predetermined level. In any case, steam supply via the steam engine 3 should be prioritized under conditions where steam may be supplied to the second steam header 21 via either the steam engine 3 or the bypass valve 23.

As described above, the steam system 1 of the present embodiment includes the two

steam headers

18 and 21 having different pressures and temperatures. The steam in each of the

steam headers

18 and 21 can be supplied to a desired steam utilization device (not shown). Since the steam in each of the

steam headers

18 and 21 has a different temperature, it is possible to use the steam according to the application. That is, when a relatively high temperature steam is required, the steam may be supplied from the first steam header 18, and when a lower temperature steam is required, the second steam header 21 is supplied. Steam may be supplied from

Incidentally, the operation state of the boiler 2 of the present embodiment is controlled based on the steam pressure in the first steam header 18. Specifically, the burner combustion amount is controlled based on the steam pressure in the first steam header 18.

The first steam sensor 21 is provided with a first pressure sensor 25 in order to grasp the use load of the steam. The first pressure sensor 25 monitors the vapor pressure in the second vapor header 21. Therefore, whether or not there is a steam load can be detected based on whether or not the steam pressure is less than a predetermined value. That is, when steam is used, the steam pressure in the second steam header 21 is lowered, so that it is possible to detect the use load of steam depending on whether or not it is less than a predetermined value.

Compressed air from the compressor 4 can be supplied to one or a plurality of compressed air utilization devices (not shown) via the compressed air passage 26. A second pressure sensor 27 is provided in the compressed air passage 26 in order to grasp the usage load of the compressed air. The second pressure sensor 27 monitors the air pressure in the compressed air passage 26. Therefore, whether or not there is an air load can be detected based on whether or not the air pressure is less than the set value. That is, when compressed air is used, since the air pressure in the compressed air passage 26 decreases, the use load of the compressed air can be detected based on whether or not it is less than the set value. However, a hollow air tank (not shown) may be provided in the middle of the compressed air passage 26, and a second pressure sensor 27 may be provided in the air tank to detect the use load of the compressed air.

In the steam system 1 of the present embodiment, the controller 24 constantly monitors the detected pressures of the first pressure sensor 25 and the second pressure sensor 27, and controls the opening and closing of the steam supply valve 19 based on this, as will be described later. However, the opening degree of the steam supply valve 19 may be controlled as desired. Furthermore, the controller 24 may control the bypass valve 23, the clutch, and the like as desired. However, in this embodiment, the bypass valve 23 is a self-reducing pressure reducing valve as described above.

The controller 24 detects that there is an air load when the air pressure of the second pressure sensor 27 is less than a set value, and if there is a steam load when the vapor pressure of the first pressure sensor 25 is less than a predetermined value. When detecting, the steam supply valve 19 is opened and the steam engine 3 is operated.

Further, the controller 24 detects that there is no air load when the air pressure of the second pressure sensor 27 is equal to or higher than a set value, and the steam load is detected when the vapor pressure of the first pressure sensor 25 is equal to or higher than a predetermined value. When it is detected that the steam engine 3 is not present, the steam supply valve 19 is closed and the steam engine 3 is stopped.

The controller 24 detects that there is no air load when the air pressure of the second pressure sensor 27 is equal to or higher than the set value, and the steam load is detected when the vapor pressure of the first pressure sensor 25 is less than a predetermined value. When it is detected that there is, the steam supply valve 19 is closed and the steam engine 3 is stopped. In this case, the steam is supplied to the second steam header 21 and thus the steam using device via the bypass 22.

Furthermore, the controller 24 detects that there is an air load when the air pressure of the second pressure sensor 27 is less than the set value, and the steam load is detected when the vapor pressure of the first pressure sensor 25 is equal to or greater than a predetermined value. When it is detected that the compressor 4 is not present, the compressor 4 is driven by the electric motor 16. In this case, the electric motor 16 may be capable of driving the compressor 4 or a different compressor may be driven. In the latter case, the compressed air from the first compressor 4 driven by the steam engine 3 and the compressed air from the second compressor driven by the electric motor 16 have a common compressed air passage 26 or an air tank. Via the compressed air. The electric motor 16 that drives the second compressor is controlled based on the air pressure detected by the second pressure sensor 27.

However, the controller 24 detects that there is an air load when the air pressure of the second pressure sensor 27 is less than the set value, and the steam load is detected when the vapor pressure of the first pressure sensor 25 is equal to or greater than a predetermined value. Even when it is detected that the steam engine 3 is not present, the steam engine 3 may be operated by opening the steam supply valve 19. In this case, the electric motor 16 is not necessarily required. Further, for example, when it is desired to suppress the use of electricity as much as possible at the time of electric power peak in summer, in order to drive the compressor 4 without using an electric type with high power consumption even when there is no steam load, Steam can be supplied to the engine 3.

In addition, when there is an air load except when there is an air load but no steam load, the second compressor may be driven by the electric motor 16. At this time, the driving of the steam engine 3 is prioritized, and the electric motor 16 is auxiliary driven when the steam engine 3 alone cannot cover. Also in this case, the electric motor 16 that drives the second compressor is controlled based on the air pressure detected by the second pressure sensor 27.

Incidentally, since the shaft seal portion of the steam engine 3 is a non-contact seal 10, a small gap is generated between the shaft of the screw rotor 8 and the seal 10. As a result, the steam and / or drain reaches the shaft seal through the bearing 9 and leaks out of the casing 7 through the gap. The steam leaking from the shaft seal portion of the steam engine 3 and / or the drain leaking from the shaft seal portion of the steam engine 3 is supplied to the water supply tank 5 via the leak heat recovery path 28. Thereby, the stored water in the water supply tank 5 is warmed.

Further, drain generated in the steam engine 3 is supplied to the water supply tank 5 via the drain recovery path 29. Thereby, the stored water in the water supply tank 5 is warmed. A steam trap 30 is provided in the middle of the drain recovery path 29.

Furthermore, the water supply path 31 to the water supply tank 5 is connected to the water supply tank 5 via the compressor 4. As a result, the makeup water to the feed water tank 5 and the compressor 4 can exchange heat, so that the makeup water to the feed water tank 5 can be warmed and the compressor 4 can be cooled. The compressor 4 may be cooled via a medium such as oil, and the oil may be cooled with makeup water supplied to the water supply tank 5.

The steam system of the present invention is not limited to the configuration of the above embodiment, and can be changed as appropriate. For example, in the above embodiment, the steam engine 3 is a screw type, but may be a turbine type in some cases.

In the above embodiment, the compressor 4 is on / off controlled. However, the capacity may be controlled according to circumstances. In that case, it is easy to adjust the opening degree of the steam supply valve 19 to the steam engine 3 or to perform inverter control of the electric motor 16.

Moreover, in the said Example, although the use load of the steam was detected by the 1st pressure sensor 25 provided in the 2nd steam header 21, the 1st pressure sensor 25 is not the 2nd steam header 21, but the steam engine 3 from. You may provide in the pipe line after the confluence | merging with the exhaust steam path 20 and the bypass path 22. FIG. In that case, the installation of the second steam header 21 can be omitted.

In the above embodiment, a pump or a blower may be installed in place of the compressor 4. In such a case, the control may be performed in the same manner as in the above embodiment. Further, a vacuum pump may be installed in place of the compressor 4. In that case, the steam engine 3 or the electric motor 16 may be controlled based on the pressure in the space sucked by the vacuum pump driven by the steam engine 3 or the electric motor 16.

Further, in the above-described embodiment, in order to prevent the hunting of the opening and closing of the steam supply valve 19, the “set value” and / or “predetermined value” may each set an operation gap (differential). is there. For example, when the set lower limit pressure is reached due to the use of compressed air, the steam supply valve 19 is opened, and when the set upper limit pressure is reached, the steam supply valve 19 may be closed. Further, as the steam in the second steam header 21 is used, the steam supply valve 19 is opened when the predetermined lower limit pressure is reached, while the steam supply valve 19 is closed when the predetermined upper limit pressure is reached. Similarly, the controller 24 may control the opening degree of the steam supply valve 19 based on the pressure detected by the second pressure sensor 27 so as to maintain the air pressure in the set pressure range. Moreover, the controller 24 may control the opening degree of the steam supply valve 19 based on the detected pressure of the first pressure sensor 25 so as to maintain the vapor pressure in a predetermined pressure range.

In the above embodiment, the heat exchange between the supply water to the water supply tank 5 and the compressor 4 is performed. However, the heat exchange between the stored water in the water supply tank 5 and the compressor 4 may be performed. Specifically, the stored water in the water supply tank 5 can be circulated between the water supply tank 5 and the compressor 4. Thereby, the water stored in the water supply tank 5 can be warmed and the compressor 4 can be cooled. The compressor 4 may be cooled through a medium such as oil, and the oil may be cooled with circulating water between the water supply tank 5 and the compressor 4.

Moreover, in the said Example, the heating of the stored water by the steam which leaks from the shaft seal part of the steam engine 3, and / or the drain which leaks from the shaft seal part of the steam engine 3, the stored water by the drain which generate | occur | produces in the steam engine 3 Of the heating and heating of the makeup water by the compression heat of the compressor 4, one or more may be executed.

Further, in the above embodiment, when the compressor 4 driven by the steam engine 3 and the second compressor driven by the electric motor 16 are provided side by side, the stored water in the water supply tank 5 or the makeup water to the water supply tank And heat exchange may be performed between the second compressor and the second compressor. When heat is exchanged between the stored water in the water supply tank 5 and the second compressor, the stored water in the water supply tank 5 is circulated between the water supply tank 5 and the second compressor. Thereby, while being able to warm the stored water of the feed water tank 5, cooling of a 2nd compressor can be aimed at. On the other hand, when heat is exchanged between the makeup water to the feed water tank 5 and the second compressor, the makeup water to the feed water tank 5 is supplied to the feed water tank 5 via the second compressor. Thereby, while being able to warm the supplementary water to the water supply tank 5, cooling of a 2nd compressor can be aimed at. In any case, the second compressor may be cooled through a medium such as oil.

Claims

A prime mover that generates power using steam from the boiler;
A driven machine that is driven by this prime mover and discharges or sucks fluid;
A bypass for supplying steam to the location where steam after use in the prime mover is supplied without going through the prime mover;
A bypass valve provided in the bypass passage;
Based on the steam load at the location where the steam from the prime mover and the steam from the bypass passage are supplied, and the fluid load in the space where the fluid is discharged or sucked by the driven machine, steaming to the prime mover is performed. A controller to control;
A water supply tank in which water supplied to the boiler is stored and steam or drain leaking from a shaft seal of the prime mover, drain generated in the prime mover, or heat generated by the driven machine is used to warm the stored water or makeup water; A steam system comprising:
The steam leaking from the shaft seal portion of the prime mover and / or the drain leaking from the shaft seal portion of the prime mover are supplied to the water supply tank, and the stored water in the water supply tank is warmed. 2. The steam system according to 1.
3. The steam system according to claim 1, wherein drain generated in the prime mover is supplied to the water supply tank and the stored water in the water supply tank is warmed.
The stored water in the water supply tank or the supply water to the water supply tank is warmed by cooling the driven machine using the stored water in the water supply tank or the supply water to the water supply tank. The steam system according to any one of claims 1 to 3.
A second driven machine driven by an electric motor for discharging or sucking fluid;
Steam supply to the prime mover is based on the steam load at the location where the steam from the prime mover and the steam from the bypass passage are supplied and the fluid load in the space where the fluid is discharged or sucked by each driven machine. Is controlled,
Based on the fluid load in the space where fluid is discharged or sucked by each driven machine, the electric motor is controlled,
Cooling of the second driven machine using the stored water in the water supply tank or makeup water to the water supply tank warms the stored water in the water supply tank or the makeup water to the water supply tank. The steam system according to any one of claims 1 to 4, wherein: