JP2010196473A - Electric power plant water supply device, and method for controlling the same - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a water supply device and a method for controlling the same, safely operating a plant even during an emergency such as a plant trip and load cutoff while improving the thermal efficiency and power generation efficiency of the whole electric power plant because in the past, when a compressor is provided to improve efficiency, a load condition for plant operation and the operation of the water supply device are excluded from consideration. <P>SOLUTION: This electric power plant water supply device includes: a steam turbine driven by using steam; a water supply heater heating water supply with exhaust steam from the steam turbine condensed by a condenser; a steam compressor compressing and heating extracted steam or exhaust steam from the steam turbine and supplying it to the water supply heater; a compressor motor driving the steam compressor; a blow pipe for delivering saturated steam inside of the water supply heater to the condenser; and a pressure regulating valve for regulating a saturated steam flow in the blow pipe. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to a water supply device for a power plant having a steam turbine and a control method for the water supply device.

  In Japanese Utility Model Laid-Open No. 1-123001, steam supplied from a condenser is compressed by a single compressor, and the compressed steam is supplied to four water heaters from a plurality of locations in the axial direction of the compressor. The thermal power plant to be described is described.

Japanese Utility Model Publication No. 1-123001

  In Japanese Utility Model Laid-Open No. 1-123001, when a compressor is provided to improve efficiency, the load state of the plant operation is not considered, and the operation of the water supply apparatus is not considered.

  The objective of this invention is providing the water supply apparatus which can operate a plant safely in emergency, such as a plant trip and load interruption | blocking, etc., and its control method, improving the thermal efficiency and power generation efficiency of the whole power plant.

  In order to achieve the above object, a power plant water supply apparatus of the present invention includes a steam turbine driven using steam, a feed water heater for heating feed water obtained by condensing exhaust steam from the steam turbine with a condenser, and a steam turbine. A steam compressor for compressing and heating the bleed steam or exhaust steam from the steam and supplying the steam to the feed water heater, a compressor motor for driving the steam compressor, and saturated steam inside the feed water heater to the condenser And a pressure control valve for adjusting the flow of saturated steam in the blow piping.

  According to the present invention, it is possible to provide a water supply apparatus that can increase the heat utilization rate of low-temperature and low-pressure steam and improve plant thermal efficiency, and can safely operate and control the steam compressor and the water supply apparatus even when the load is interrupted.

BRIEF DESCRIPTION OF THE DRAWINGS Schematic of the power plant water supply apparatus and control apparatus by 1st Example of this invention. The driving | running characteristic of the power plant water supply apparatus by 1st Example of this invention. The schematic of the power plant water supply apparatus and control apparatus by 2nd Example of this invention. Fig. 3 shows operating characteristics of a steam compressor according to a second embodiment of the present invention. The flowchart of the control apparatus by 2nd Example of this invention.

  Embodiments will be described below with reference to the drawings.

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

  In this figure, the extraction steam of the low-pressure steam turbine 2, which is low energy, is used as a heat source for feed water preheating. The low-pressure steam turbine 2 includes a low-pressure steam turbine inlet shut-off valve 4 on the upstream side and a condenser 5 on the downstream side, and obtains driving force using low-temperature and low-pressure steam as a working fluid. The steam at the outlet of the low-pressure turbine flows into the condenser 5 and is stored as feed water at the bottom of the apparatus after being reduced in temperature and condensed. The feed water stored in the lower part of the condenser is pressurized by the condensate pump 7 through the feed water pipe 6 and then heated by the low pressure feed water heater 8 and the high pressure feed water heater 10 and supplied to the boiler or the nuclear reactor. The Steam for heating the feed water to the low pressure feed water heater 8 and the high pressure feed water heater 10 is supplied through a low pressure bleed pipe 11 and a high pressure bleed pipe 12. In addition, although it demonstrates as an example using the extraction steam from a steam turbine here, you may use the exhaust steam of a steam turbine. Moreover, the blow piping 15 which conveys the saturated steam in the high-pressure feed water heater 10 to the condenser 5, and the pressure control valve 16 which adjusts the saturated steam flow which passes the blow piping 15 are provided.

  In the low-pressure feed water heater 8, the feed water is heated using the low-temperature and low-pressure extraction steam obtained by the low-pressure steam turbine 2. The heated steam is condensed and liquefied by heat exchange with the feed water and is stored as drainage at the bottom of the low-pressure feed water heater. This drain is returned to the condenser 5.

  In the high-pressure feed water heater 10, the feed water is heated with the low-temperature / low-pressure extraction steam obtained in the low-pressure steam turbine 2 as high-temperature / high-pressure steam in the steam compressor 13. In addition to the extracted steam, exhaust steam from the low-pressure steam turbine 2 may be used. A compressor motor 14 is used to drive the steam compressor 13. The driving force of the compressor motor is a part of the electric power generated in the plant. The steam after heating the feed water is condensed and liquefied by heat exchange with the feed water and stored as a drain at the bottom of the high-pressure feed water heater. This drain joins with water supply in the deaerator 9. The number of feed water heaters installed and the method of connecting drain pipes vary depending on the power plant, but all have the purpose of improving the thermal efficiency of the power plant as a whole by collecting part of the heat from the steam turbine with the feed water. .

  In this embodiment, the drain at the bottom of the high-pressure feed water heater is reused as feed water in the deaerator 9, but the drain is supplied to the low-pressure feed water heater 8 and reused for heating the feed water. Good. In addition, when the drain temperature is low enough to be unsuitable for heating the feed water, the drain may be returned to the condenser 5.

In this embodiment, the high-temperature / high-pressure extraction steam extracted from the conventional high-pressure steam turbine is not used, and the low-temperature / low-pressure extraction steam extracted from the low-pressure steam turbine is pressurized and heated by the steam compressor 13 to heat the feed water. The source. ΔE _HPST (kW) is the increase in output due to the stop of extraction from the high-pressure steam turbine, the increase in output caused by the increase in steam flow to the low-pressure steam turbine due to the stop of extraction from the high-pressure steam turbine, and the decrease in output due to the increase in the amount of extraction from the low-pressure steam turbine _Assuming that the output fluctuation total is ΔE _LPST (kW) and the driving force of the compressor motor that drives the steam compressor 13 is E _m (kW), the power generation output increase ΔE _total (kW) of the entire plant is Can be sought.

Bleed position from the low-pressure steam turbine 2 so that the total value of Delta] E _HPST and Delta] E _{LP ST} does not exceed E _m (bleed temperature) extraction steam flow rate by designing the pressure ratio and efficiency of the compressor, an increase in plant output Expected. When the fuel flow rate to the boiler or reactor is constant, the power generation efficiency and power transmission efficiency of the plant increase. _Assuming that the fuel flow rate is G _fuel (kg / s) and the fuel heating value is H _fuel (kJ / kg), the increase Δη _total (−) of the plant power generation end efficiency can be obtained by the following equation.

From equation 2, when the plant output is constant and the fuel flow to the boiler or reactor is decreased, the power generation end efficiency and the power transmission end efficiency are also increased, but the boiler or nuclear reactor must be partially loaded. Thus, when evaluating the power generation end efficiency and the power transmission end efficiency, changes in the steam turbine inlet steam temperature and steam flow rate in the partial load operation are added to ΔE _HPST and ΔE _LPST .

  The pressure regulating valve 16 does not operate during normal load operation, and is an operation end for special operation that operates during plant special operation such as load interruption and boiler trip. The operation will be described below.

  First, FIG. 2 summarizes time transitions of various state quantities of the low-pressure steam turbine 2 and the like during plant special operations such as load interruption and boiler trip. The horizontal axis represents time.

  The top diagram in FIG. 2 is a diagram showing a change in the opening degree of the low-pressure steam turbine inlet cutoff valve 4. When load interruption occurs at time t0, the low-pressure steam turbine inlet shut-off valve becomes the opening degree from 100% to 0% based on the control sequence of the conventional power plant control device, and stops the supply of steam to the low-pressure steam turbine.

  The middle diagram of FIG. 2 is a diagram showing the flow rate change at the low-pressure steam turbine outlet. As the shut-off valve opening is closed, the low-pressure steam turbine inlet steam flow rate also decreases from 1.0 to 0.0. From time t1 to t2, the shut-off valve opens at a constant opening, and cooling steam flows in. After the time t2, the steam supply becomes zero.

  At time t0, since the low pressure steam turbine 2 continues to rotate due to inertia, a steam flow is continuously generated at the outlet of the low pressure steam turbine, and the steam inside the low pressure steam turbine is forcibly exhausted to the extraction pipe or the condenser. The In addition, steam inflow from the extraction pipe to the condenser is also observed.

  The bottom diagram in FIG. 2 is a diagram showing a change in pressure at the inlet of the steam compressor. Due to the forced exhaust of the steam, the pressure rapidly decreases at the inlet of the steam compressor. Further, from time t1 to t2, the cooling steam flows into the low-pressure steam turbine 2, so the pressure at the steam compressor inlet increases. After time t2, since the steam supply becomes zero, the pressure decreases again.

  Although the steam compressor outlet pressure decreases due to load shut-off, etc., the high pressure feed water heater has the effect of a steam pool (buffer), so the rate of pressure drop is gradual. Therefore, if the compressor motor rotation speed N is continuously set at 100% without taking any countermeasures, the compressor pressure ratio Pco / Pci increases, causing the compressor to surge, and in the worst case, the compressor to be damaged. It arrives.

  The plant operator operates the pressure adjustment valve to adjust the flow of saturated steam in the blow pipe when load interruption or trip occurs, so that the saturated steam inside the feed water heater is condensed into the condensate through the blow pipe. Carry to vessel. Thereby, the pressure difference at the inlet and outlet of the compressor can be reduced, and the plant can be operated safely.

  In this way, the steam turbine driven using steam, the feed water heater for heating the feed water obtained by condensing the exhaust steam from the steam turbine with the condenser, and the extracted steam or the exhaust steam from the steam turbine are compressed and heated. A steam compressor for supplying to the feed water heater, a compressor motor for driving the steam compressor, a blow pipe for carrying saturated steam inside the feed water heater to the condenser, and saturation of the blow pipe The plant water supply device with a pressure regulating valve for adjusting the flow of steam improves the thermal efficiency and power generation efficiency of the entire power plant, and can operate the plant safely even in the event of an emergency such as a plant trip or load interruption It is.

  In addition, a steam turbine driven using steam, a feed water heater for heating feed water obtained by condensing exhaust steam from the steam turbine with a condenser, and extraction steam or exhaust steam from the steam turbine are compressed and heated to supply water A steam compressor for supplying to the heater, a compressor motor for driving the steam compressor, a blow pipe for carrying saturated steam in the feed water heater to the condenser, and a flow of saturated steam in the blow pipe The operation method of the plant water supply apparatus having a pressure regulating valve for adjusting the pressure when the steam supply to the steam turbine is stopped or reduced when the plant load is interrupted or the boiler trips, the pressure regulating valve is The open operation method improves the thermal efficiency and power generation efficiency of the entire power plant, and can operate the plant safely even in an emergency such as a plant trip or load interruption. It is.

  Further, the operation of the pressure regulating valve may be automatic opening / closing control by a control device other than the operator operating the pressure regulating valve after the operator recognizes the load cutoff. In this case, when receiving the input of the load cutoff switch SW, it can be operated by providing a control device that outputs the pressure adjustment valve opening degree command Cv0 to the pressure adjustment valve.

  In the above-described embodiment, the steam of the low-pressure steam turbine 2 is boosted by the compressor and supplied to the high-pressure feed water heater 10. However, the high-pressure steam turbine may be used instead of the low-pressure steam turbine 2.

  A second embodiment of the present invention will be described with reference to FIG.

  FIG. 3 shows a pressure gauge 19 for measuring the steam compressor inlet pressure Pci on the inlet side of the steam compressor 13 and a steam compressor for the high pressure feed water heater 10 with respect to the water supply apparatus shown in the first embodiment of the present invention. The pressure gauge 17 for measuring the outlet pressure Pco, the rotation shaft 18 for measuring the motor rotation speed N on the drive shaft of the compressor motor 14, and the measurement values Pci, Pco, N and the load cut-off switch SW are input, and the compressor A control device 100 is provided that outputs a motor output command Em0 and a pressure adjustment valve opening command Cv0.

  FIG. 4 shows the compressor operating characteristics when the steam compressor inlet pressure is lowered, together with the compressor operating characteristics when the plant water supply system controller according to the present invention is applied.

  In FIG. 4, the horizontal axis represents the compressor intake flow rate (that is, the extracted steam flow rate), and the vertical axis represents the pressure ratio at the compressor inlet and outlet. The relationship between the pressure ratio with respect to the compressor motor rotational speed N and the compressor intake flow rate is shown by a solid line.

  At the time of rating, the compressor motor speed N is set to 100%, and operation is performed at point A. Although the operating point varies depending on the load of the steam turbine, it is usually necessary to operate in the lower right region of the surge line so that the steam compressor does not surge. As shown in FIG. 2, when the load is shut off, the steam compressor inlet pressure rapidly decreases. Therefore, when the compressor motor rotation speed N is kept constant at 100%, the compressor pressure ratio Pco / Pci increases to increase the path. It reaches the surge line through (a), and the compressor reaches a surge, and in the worst case, the compressor is damaged.

  The increase in the compressor pressure ratio Pco / Pci is caused by a rapid decrease in the inlet pressure with respect to the steam compressor outlet pressure. Although the outlet pressure of the steam compressor is reduced by rapidly reducing the compressor motor speed, the high pressure feed water heater has the effect of a steam pool (buffer), so the rate of pressure drop is gradual. It reaches the surge line through path (b).

  In this embodiment, as a means for rapidly decreasing the steam compressor outlet pressure, a pipe for blowing saturated steam is installed from the steam side of the high-pressure feed water heater to the condenser, and a pressure adjusting valve is installed in the pipe. During special operations such as load shut-off and boiler trip, the pressure adjustment valve is opened to depressurize the high-pressure feed water heater. The drainage stored in the lower portion of the feed water heater is also flushed by the pressure reduction in the feed water heater, but this flushing vapor is also exhausted to the condenser through the blow pipe. When cooling steam flows into the low-pressure steam turbine 2, the pressure adjustment valve is throttled to pressurize the high-pressure feed water heater. By the blow from the high pressure feed water heater, the steam compressor is safely shifted to the stop state in the path (c). In this embodiment, a pressure ratio set value for safely stopping the compressor is set from the rated output, and the pressure adjustment valve opening is controlled to follow this pressure ratio set value when the compressor motor is stopped.

  FIG. 5 is a flowchart showing a method for controlling the compressor motor and the pressure adjustment valve opening.

  When the supply of steam to the steam turbine stops due to load interruption or boiler trip, the value of the load interruption switch SW changes from OFF to ON. When the switch SW is turned on, in a process 101, a compressor motor output command Em0 is output and a compressor motor stop operation is executed. In addition, since the inertia force accompanying rotation acts on the steam compressor and the compressor motor, the motor does not stop instantaneously by this command, and the steam compressor and the compressor motor stop according to the inertia moment.

  Next, in process 102, the compressor rotational speed N is input, and the pressure ratio set value is calculated according to the pressure ratio set value of FIG. In the process 103, the extraction steam pressure Pci and the feed water heater Pco are input, and the pressure adjustment valve opening Cv0 at which the compressor pressure ratio Pco / Pci becomes the pressure ratio set value obtained previously is calculated.

  As described above, when the steam supply to the steam turbine is stopped or reduced when the plant load is cut off or the boiler trip occurs, the rotation speed of the compressor motor is reduced to stop the steam supply to the feed water heater, or Based on the measured value of the steam pressure at the inlet of the steam compressor, the measured value of the feed water heater pressure at the outlet of the steam compressor or in the feed water heater, and the measured value of the compressor motor speed The compressor can be safely stopped in accordance with the characteristics of the compressor by the control device of the plant water supply system that controls the opening of the pressure regulating valve or the operation method thereof.

  In addition, when the steam supply to the steam turbine is stopped or reduced when the plant load is cut off or the boiler trips, and the steam supply increases due to the inflow of cooling steam, the rotation speed of the compressor motor is increased to heat the feed water. The steam supply at the steam compressor, the measured value of the steam pressure at the inlet of the steam compressor, the measured value of the pressure of the feed water heater provided in the outlet of the steam compressor or in the feed water heater, and the rotation speed of the compressor motor The plant can be operated safely even when cooling steam flows in, by the control device of the plant water supply system that controls the opening of the pressure regulating valve based on the measured value of this or the operation method thereof.

  It can be applied to steam-driven equipment such as boilers and nuclear power generation. Further, it can be used for a two-shaft gas turbine and its control device.

2 Low-pressure steam turbine 4 Low-pressure steam turbine inlet shut-off valve 5 Condenser 6 Feed water pipe 7 Condensate pump 8 Low-pressure feed water heater 9 Deaerator 10 High-pressure feed water heater 11 Low-pressure bleed pipe 12 High-pressure bleed pipe 13 Steam compressor 14 Compression Machine motor 15 Blow piping 16 Pressure adjusting valve 17, 19 Pressure gauge 18 Tachometer 100 Controller 101, 102, 103 Processing

Claims (6)

A steam turbine driven by steam;
A feed water heater for heating feed water obtained by condensing exhaust steam from the steam turbine with a condenser;
A steam compressor for compressing and heating extracted steam or exhaust steam from the steam turbine, and supplying the compressed steam to the feed water heater;
A compressor motor for driving the steam compressor;
A blow pipe for carrying saturated steam inside the feed water heater to a condenser;
A plant water supply apparatus comprising a pressure adjusting valve for adjusting a flow of saturated steam in the blow pipe. It is a plant water supply apparatus of Claim 1, Comprising:
When the steam supply to the steam turbine is stopped or reduced at the time of plant load interruption or boiler trip, the rotation speed of the compressor motor is decreased to stop or reduce the steam supply to the feed water heater. With
Based on the measured value of the steam pressure at the inlet of the steam compressor, the measured value of the feed water heater pressure provided in the outlet of the steam compressor or in the feed water heater, and the measured value of the rotation speed of the compressor motor A plant water supply apparatus having a control device for controlling an opening degree of a pressure regulating valve. The plant water supply device according to claim 2,
When the steam supply to the steam turbine is stopped or reduced at the time of plant load interruption or boiler trip, and the steam supply increases due to the inflow of cooling steam, the rotation speed of the compressor motor is increased to increase the supply water While increasing the extraction steam supply to the heater,
Based on the measured value of the steam pressure at the inlet of the steam compressor, the measured value of the pressure of the feed water heater provided in the outlet of the steam compressor or in the feed water heater, and the measured value of the rotation speed of the compressor motor A plant water supply device comprising a control device for controlling an opening degree of the pressure regulating valve. A steam turbine driven using steam; a feed water heater that heats feed water obtained by condensing exhaust steam from the steam turbine in a condenser; and the extracted water or exhaust steam from the steam turbine is compressed and heated to supply water A steam compressor for supplying to the heater, a compressor motor for driving the steam compressor, a blow pipe for carrying saturated steam inside the feed water heater to the condenser, and saturation of the blow pipe A method for operating a plant water supply apparatus comprising a pressure regulating valve for regulating the flow of steam,
A method for operating a plant water supply apparatus, wherein when the supply of steam to a steam turbine is stopped or reduced during a plant load interruption or a boiler trip, the pressure regulating valve is opened. It is a driving | operation method of the plant water supply apparatus of Claim 4, Comprising:
A controller, and when the steam supply to the steam turbine is stopped or reduced when the plant load is interrupted or the boiler trips, the rotation speed of the compressor motor is decreased to heat the feed water. Stop or reduce the steam supply to the steam generator, measure the steam pressure at the steam compressor inlet, and measure the feed water heater pressure in the steam compressor outlet or feed water heater, An operation method of a plant water supply apparatus, wherein the opening of the pressure regulating valve is controlled based on a measured value of the compressor motor rotation speed. A method for operating the plant water supply device according to claim 5,
When the steam supply is increased due to the inflow of cooling steam after the steam supply to the steam turbine is stopped or reduced at the time of plant load interruption or boiler trip, the control device sets the rotation speed of the compressor motor. To increase the extraction steam supply to the feed water heater,
Based on the measured value of the steam pressure at the inlet of the steam compressor, the measured value of the pressure of the feed water heater provided in the outlet of the steam compressor or in the feed water heater, and the measured value of the rotation speed of the compressor motor A method for operating a plant water supply apparatus, wherein the opening of the pressure regulating valve is controlled.

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