JP2002250203A - System for monitoring damage to turbine and deterioration of internal efficiency - Google Patents

Abstract

PROBLEM TO BE SOLVED: To promote quick exchange or repair of a component of equipment and confirmation of soundness or treatment for implementing the soundness, by issuing an alarm in a state the equipment cannot keep required performance or in a state an unexpected trouble will be exploded. SOLUTION: Working fluid flows into and works at each stage in a turbine. Reduction in velocity energy of the working fluid caused by change in injection angle of the working fluid resulted from damage of a nozzle plate 11 is monitored during operating the turbine. As monitoring elements, a relation between pressure difference between in front of and behind a nozzle 12 and a erosion rate of the nozzle plate 11 of the nozzle, and an alarm point P of reduction in mechanical strength of the nozzle plate 11 based on the erosion rate are calculated in advance. Further, an alarm value is set to have a certain amount of room for breaking strength of the nozzle plate 11 calculated from a nozzle erosion rate in design, and the damage to the turbine and deterioration of internal efficiency during the operation of the turbine are monitored and treated based on the alarm value.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a steam turbine damage and internal efficiency decrease monitoring system for monitoring, for example, a steam turbine for power generation and a decrease in internal efficiency (performance).

[0002]

2. Description of the Related Art A steam turbine of a thermal power plant is subjected to severe operation such as frequent start / stop and load change for load adjustment in combination with a base-load operation of a nuclear power plant. .

On the other hand, due to recent deregulation and social needs, power generation facilities are required to have high reliability, high efficiency, and low maintenance costs. In particular, with regard to steam turbines, with the extension of regular inspection intervals (from the legal inspection once every two years to a voluntary inspection once every eight years), monitoring of equipment operation has been strengthened more than ever. That stable operation and high efficiency can be maintained over a long period of time, and so-called periodic inspection work or simple inspection work that disassembles, inspects, cares for, and replaces components at the optimal timing can be performed. Monitoring methods have been developed and demanded to be applied.

In a thermal power plant, high-temperature, high-pressure steam generated in a boiler, that is, heat energy is guided to a steam turbine and converted into mechanical energy, which is further converted into electric energy by a generator to generate power. However, the steam sent from the boiler to the steam turbine contains many so-called scales mainly composed of iron oxide and the like.

During operation of the steam turbine, operational and structural considerations are taken to prevent the scale from being carried into the steam turbine as much as possible.

[0006] One of them is operational considerations, that is, scale blow operation of the main steam piping system prior to startup. In particular, at the time of start-up after the plant is stopped, a relatively large particle size scale is easily brought into the steam turbine from the boiler and the main steam pipe. Therefore, before ventilating the steam turbine, the scale flow line of the boiler (also called turbine bypass line)
In addition, a relatively large particle size scale is blown by directing steam from the main steam pipe drain line to the condenser. In addition,
In normal operation, these two lines are closed and generally used only when the plant is started / stopped and also in an emergency.

Second, there is a structural consideration for preventing the inflow of scale and foreign matter during the normal operation of the steam turbine. This is a strainer installed at the main steam stop valve at the inlet of the steam turbine, and this strainer prevents relatively large particle size scale and foreign matter from flowing into the steam turbine.

This strainer has a diameter of 40 to 50 mmΦ.
It is general to adopt a structure in which a wire mesh of about 5 mesh is attached to a perforated plate having about holes. Therefore, a scale having a size smaller than the mesh of the wire mesh flows into the steam turbine as it is. As a result, erosion of steam turbine components due to scale contained in steam
Damage has become unavoidable.

The flow rate of steam into the steam turbine is 15
It is a high-speed flow of about 0 m / s to 200 m / s,
The high-pressure turbine nozzle box (first-stage high-pressure nozzle) and the first-stage bucket at the inlet of the steam turbine undergo particularly significant erosion due to collision with scale contained in the steam. Usually, this erosion is due to solid particle erosion (SPE; Solid Particle Er) due to oxide scale.
Osion).

For the material of the high-pressure first stage nozzle, forged or rolled nickel steel, stainless steel, nickel-chromium-molybdenum steel is used depending on the pressure and temperature of steam. Has been severe, and repairs such as welding repairs have been conventionally required at regular inspections. Recently, for the purpose of alleviating this, a hardening treatment of the surface with, for example, boron, ceramic or the like has been performed.

As is well known, a steam turbine is a fluid device composed of a number of paragraphs, ie, a nozzle and a moving blade. The nozzle is composed of a nozzle ring and a nozzle plate, and forms a flow passage with a reduced cross section for blowing out the fluid to convert the energy of the fluid into mechanical energy.In the case of an impulse turbine, the pressure of steam is Lowers the steam to give speed. The moving blade is a row of rotating blades attached to an impeller that converts heat energy held by steam into mechanical work, and receives the velocity energy of the nozzle and converts it into rotational energy.

The nozzles are also referred to as stationary blades and are arranged so as to obtain a steam injection angle of a specified angle (generally about 15 to 25 degrees) with respect to the plane of rotation of the moving blades. Has a structure that effectively utilizes the velocity energy of the steam injected from the preceding rotor blades.

[0013]

Erosion of the high pressure first stage nozzle due to collision with scale in the steam lowers the internal efficiency (performance) of the steam turbine.

The internal efficiency of a steam turbine is determined by how much the energy of the steam flowing into the turbine works in each stage composed of nozzles and moving blades inside the turbine, and is exchanged for output as a total of each stage. Although it is to be evaluated, the output values shared by the nozzles and blades for each paragraph are determined by design.

As the erosion of the nozzle plate progresses due to the scale contained in the steam, the jet angle of the steam jetted to the moving blade at the nozzle outlet changes. That is, as the steam speed triangle at the nozzle outlet changes in design, the speed energy given to the rotor blade decreases, and the output assigned to that paragraph decreases. This is a so-called decrease in the internal efficiency (performance) of the steam turbine. Even if given the planned steam energy, the planned work is not performed and the planned output cannot be obtained.

Further, when the erosion of the nozzle plate is extremely advanced by the steam flow, the nozzle plate may be damaged or bent. As a result, the rotor blades located downstream of the nozzle caused a backlash phenomenon of the rotor blade due to the non-uniform flow of the steam flow at the nozzle outlet, and there was no effect on the steam flow without erosion of the nozzle. A relatively small scale collides with the rotor blade,
This causes erosion of the rotor blade. In addition, the relative impact speed of a large scale is increased, and scale erosion of the rotor blade is promoted. In addition, there is an adverse effect such as an increase in the repetitively fluctuating stress on the blade / shroud portion.

[0017] Continuous operation for a long time under such a severe environment may cause a loss of a moving blade or a shroud scattering as an extreme case.

The occurrence of these events results in the generation of large vibrations in the steam turbine, leading to a state where continuous operation is impossible.

Conventionally, as a monitoring device during operation of a turbine, monitoring instruments such as shaft or bearing vibration, metal temperature of each part such as a vehicle room, vehicle room expansion / difference, vacuum degree, bearing temperature, bearing supply / drain oil temperature, etc. Or a surveillance protection system is in place. For example, regarding the monitoring of the bearing vibration value, an alarm is generated at 12.5 / 100 mm, an alarm is generated at 20.0 / 100 mm, and the turbine is automatically stopped (tripped) in addition to a recorder that displays and monitors the absolute value. An alarm / protection interlock circuit / monitoring / protection device is installed. Even when a large vibration occurs in the turbine bearing due to the above-mentioned unexpected event, the trip protection operation is performed as the final protection of the turbine.

However, conventionally, there has been no special monitoring during the normal operation related to the erosion of the nozzle, and the internal efficiency (performance) of the steam turbine described above has been reduced, the chipping and strength of the nozzle plate have been reduced, and the rotor blade has been reduced. Regarding the development of unforeseen accidents due to damage, reduced strength, shattering of the shroud, etc., there were many things that were left to the end.

The present invention has been made in view of such circumstances, and has been made to enhance monitoring of conditions during normal operation of a turbine, and when the equipment has become unable to maintain the specified performance, A warning is issued when a situation is anticipated to develop into an unexpected trouble due to a decrease in mechanical strength, an operator is notified, and a stop / open inspection of the steam turbine is performed to check the equipment component parts. It provides a monitoring system that prompts prompt replacement / repair and soundness confirmation / action.

[0022]

In order to achieve the above object, according to the first aspect of the present invention, a working fluid that flows into each stage constituted by a nozzle and a moving blade inside a turbine to perform work. A turbine damage and internal efficiency reduction monitoring system that monitors during operation of a turbine that a speed energy is reduced due to a change in the injection angle of the working fluid due to damage to a nozzle plate of the nozzle. The relationship between the pressure difference between the front and rear of the nozzle and the erosion rate of the nozzle plate, and the alarm point for mechanical strength reduction of the nozzle plate based on the erosion rate, and the destruction of the nozzle plate calculated from the designed nozzle erosion rate An alarm value with a certain margin in intensity is set, and based on this alarm value, turbine damage and decrease in internal efficiency during turbine operation are monitored and taken. Providing turbine damage and internal efficiency drop monitoring system, characterized in that.

According to the second aspect of the invention, the velocity energy of the working fluid flowing into each stage constituted by the nozzle and the moving blade inside the turbine and performing the work is reduced by the damage of the nozzle plate of the nozzle. It is a turbine damage and internal efficiency reduction monitoring system that monitors during operation of the turbine to reduce the change due to the change in the injection angle, and as the monitoring elements, a pressure difference between the front and rear of the nozzle and the erosion progress degree of the rotor blade in advance. And the alarm point for mechanical strength reduction of the moving blade based on the progress of the erosion, and set an alarm value with a certain margin in the breaking strength of the moving blade calculated from the moving blade erosion progress in the design. In addition, the turbine damage and the decrease in the internal efficiency during the operation of the turbine are monitored based on the alarm value and the countermeasures are taken. To provide a visual system.

According to the third aspect of the present invention, the velocity energy of the working fluid which flows into each stage constituted by the nozzle and the moving blade in the turbine and performs the work is changed by the damage of the nozzle plate of the nozzle. A turbine damage and internal efficiency decrease monitoring system that monitors during operation of the turbine that the decrease is caused by a change in the injection angle of the nozzle. And the relationship between the turbine internal efficiency, and the normal value and abnormal value of the front-rear pressure difference reduction rate of the nozzle corresponding to each of the operating loads, and the abnormal value of the front-rear pressure difference reduction rate of the nozzle as an alarm value Set it,
Provided is a turbine damage and internal efficiency reduction monitoring system that monitors and responds to turbine damage and internal efficiency decrease during turbine operation based on the alarm value.

According to a fourth aspect of the present invention, two or more alarm values selected from the turbine damage and internal efficiency reduction monitoring systems according to the first, second and third aspects are used as a composite reference. And a turbine damage and internal efficiency reduction monitoring system for monitoring and responding to turbine damage and internal efficiency decrease during turbine operation.

According to the fifth aspect of the present invention, the first to fourth aspects of the present invention are provided.
In the turbine damage and internal efficiency reduction monitoring system according to any one of the above, the means for monitoring turbine damage and internal efficiency reduction during turbine operation and corresponding means includes a visual alarm unit, an audible alarm unit, and an operation control unit. And a system for monitoring turbine damage and internal efficiency deterioration.

According to the sixth aspect of the present invention, the first to fifth aspects are described.
The monitoring elements, alarm values, their graphic processing data, and the command data to the means for monitoring the turbine damage and the internal efficiency decrease during the operation of the turbine and for corresponding means in the turbine damage and internal efficiency decrease monitoring system according to any of the above. A floppy disk, an optical disk, and other storage devices characterized by storing a storage device.

[0028]

DESCRIPTION OF THE PREFERRED EMBODIMENTS One embodiment of the present invention will be described below in detail with reference to the drawings.

In the following embodiment, basically, the front and rear pressures of the high-pressure first stage nozzle of the steam turbine are input to a steam turbine damage / internal efficiency reduction monitoring system constituted by a control device such as an electronic computer. "Pre- and post-nozzle pressure difference-high pressure first stage nozzle plate erosion rate monitoring curve" and "high pressure first stage nozzle pre- and post-pressure difference-high pressure first stage blade erosion progress monitoring" which are pre-produced and input as software in the monitoring system Curve and the "nozzle pressure difference before and after the nozzle-turbine internal efficiency (performance) decrease monitoring curve" in response to the plant state, the current operating state can be constantly displayed and monitored.
And, when the alarm value state set in advance is reached on the software of each of the three types of monitoring curves described above, ie,
Alarm setting value of nozzle plate strength decrease due to increase in high pressure first stage nozzle plate erosion rate, alarm set value of high pressure first stage blade blade strength decrease due to high pressure first stage blade erosion progression, and turbine internal efficiency due to high pressure first stage nozzle erosion When the lower alarm set value is reached, an alarm is issued to notify the operation monitoring staff of the abnormal condition of the steam turbine, and the steam turbine is immediately stopped and opened for inspection, and repair or replacement of the high-pressure first-stage nozzle is performed. The purpose of the present invention is to provide a monitoring system that prompts confirmation and treatment of the soundness of the high-pressure first-stage rotor blades.

The provision of the steam turbine damage / internal efficiency reduction monitoring system according to the present embodiment contributes to the maintenance and improvement of the efficiency of the thermal power plant, that is, the saving of fuel resources, and the occurrence of a serious accident of the steam turbine. Prevention enables stable operation of the plant and meets social needs. Hereinafter, a specific description will be given.

FIG. 1 is an assembled sectional view of a high-to-medium pressure integrated steam turbine, and FIGS. 2 to 4 show the arrangement and structure of a nozzle box installed in the turbine shown in FIG. It is a figure explaining a structure. In addition, in this embodiment, in order to explain the structure of a steam turbine, description will be made using an example of a high-to-medium pressure integrated steam turbine. However, the present invention is not limited to the type of turbine and can be applied to any type.

As shown in FIG. 1, the high-intermediate-pressure integrated steam turbine 1 applied in the present embodiment is obtained by disposing a high-pressure stage rotor blade 3 and an intermediate-pressure stage rotor blade 4 in the same casing 2. , A high-pressure turbine 5 and an intermediate-pressure turbine 6. Then, as shown by arrows a in FIGS. 2 and 3, the main steam having passed through a main steam stop valve and a steam control valve (not shown) installed on the inlet side of the steam turbine is connected to four upper and lower sleeves 7 of the high-pressure turbine 5. Then, it flows into the steam chamber 9 of the nozzle box 8. The steam chamber 9 of the nozzle box 8 has a ring shape around the entire upper and lower sides of the high-pressure turbine, and a nozzle ring 10 and a nozzle plate (stationary vane) 11 are provided on the downstream side of the nozzle box steam chamber 9. A high-pressure first-stage nozzle 12 is provided.

The nozzle plate 11 is arranged so as to obtain a steam injection angle of a specified angle (about 15 to 25 °) with respect to a rotation plane of a high-pressure first-stage moving blade (also referred to as a high-pressure first-stage moving blade) 13. The main steam is injected to the high-pressure first-stage bucket 13 shown in FIG. 4 to give velocity energy. High pressure rotor blade 1
Numeral 3 receives the velocity energy from the high pressure first stage nozzle 12 and converts it into rotational energy.

In this embodiment, as will be described below, the "pressure before and after the high-pressure first-stage nozzle" is detected. The "pressure before the high-pressure first-stage nozzle" is defined as the inlet of the high-pressure turbine, that is, the nozzle box steam chamber. 9 means the steam pressure (P1). The “pressure after the high-pressure first-stage nozzle” refers to the steam pressure (P2) after the nozzle plate 11 exits.

FIGS. 5 to 7 are diagrams illustrating the structure of the high-pressure first-stage nozzle 12 and an example of the erosion state of the nozzle plate 11 of the high-pressure first-stage nozzle 12 due to the scale flowing into the high-pressure turbine 5.

The steam flowing into the nozzle box steam chamber 9 of the high pressure turbine 5 from the upper and lower four places via the main steam stop valve and the steam control valve installed on the steam turbine inlet side described above passes through the high pressure first stage nozzle 12. The high pressure first stage rotor blades 13 on the downstream side are jetted.

As shown in FIGS. 5 and 6, the nozzle plate 11
The erosion 14 usually occurs near the rear edge near the steam outlet side and near the abdomen, and cracks and the like may occur due to the impact due to collision with the scale 15. Erosion 14 is particularly likely to occur at the nozzle throat 16. The nozzle throat portion refers to the narrowest portion in the nozzle vapor passage portion, and the portion shown by oblique lines in FIG. 7 is referred to as the throat area. If the erosion 14 progresses due to scale erosion or further cracks grow, in extreme cases, an event that leads to an unexpected situation, that is, the material strength of the nozzle plate 11 against the steam flow is insufficient and the nozzle plate 11 Damaged and blown away, the collision with the high-pressure first-stage moving blade 13 and other moving blades located downstream causes damage to the moving blade,
This leads to the occurrence of large vibration and the like, which is not preferable.

FIG. 8 is a graph showing “the pressure before the high pressure first stage nozzle (pressure on the inlet side) (P1) and the pressure after the high pressure first stage nozzle (pressure on the outlet side).
The pressure difference (Ps) from (P2): kPa ”is represented on the vertical axis, and the“ erosion rate of the nozzle plate 11 of the high-pressure initial stage nozzle 12:
% Is shown on the horizontal axis, and shows a relationship curve between the two, that is, "high-pressure first-stage nozzle high-pressure first-stage nozzle pressure difference (differential pressure) -high-pressure first-stage nozzle plate erosion rate monitoring curve A". This curve A (hereinafter also referred to as “monitoring curve A”)
As will be described in detail later, the present invention is applied to the present invention, and is produced and input as software to a monitoring system for monitoring the damage and internal efficiency (performance) of a steam turbine.

As shown in FIG. 8, the high pressure first stage nozzle 1
With the erosion of the second nozzle plate 11, the mechanical strength of the second nozzle plate 11 decreases. At the same time, the high pressure first stage rotor blade 13 is adversely affected. As the erosion of the nozzle plate 11 progresses,
The steam pressure at the nozzle outlet gradually increases. That is, the pressure difference Ps between the pressure before the high-pressure first-stage nozzle (pressure on the inlet side) (P1) and the pressure after the high-pressure first-stage nozzle (pressure on the outlet side) (P2) (hereinafter, also referred to as “difference before and after the nozzle (Ps)”). ) Will gradually decrease. The pressure difference before and after this nozzle (P
When s) reaches a certain value (point P in FIG. 8), the erosion 14 of the nozzle plate 11 greatly proceeds, and the mechanical strength decreases (hereinafter, referred to as “P”).
This point P is also referred to as “high pressure first stage nozzle plate mechanical strength decrease warning point P”).

In such an operating state, it is not preferable to continue driving, and it is determined that there is a possibility of causing an accident. Therefore, in this embodiment,
The pressure difference (Ps) before and after the nozzle corresponding to the point P on the “monitoring curve A”, that is, the point X (hereinafter, the pressure difference (differential pressure) X before and after the high-pressure first stage nozzle plate mechanical strength reduction warning point nozzle )), An alert is issued to urge the operator to immediately stop, open, and inspect the turbine to repair the high pressure first stage nozzle 12 or replace parts. In addition,
This “monitoring curve A” is always displayed on a display device described later so that the current device state can be checked during operation.

An example of the concept of setting an alarm value in the “monitoring curve A” will be described below. That is, the setting of the “alarm issuing point” for the nozzle plate 11 of the high-pressure first-stage nozzle 12, that is, the “alarm value” for issuing a warning of a decrease in the mechanical strength of the nozzle plate 11 is basically a design high-pressure first-stage nozzle. The breaking strength of the nozzle plate 11 calculated from the plate erosion rate is set with a margin. For example, when the erosion 14 progresses from the state where the nozzle plate 11 is not eroded and the erosion rate of the high pressure first stage nozzle plate 5% is set as the alarm value, the pressure before and after the nozzle at the point P on the “monitoring curve A” is set. An alarm is issued at a difference (differential pressure) of XkPa.

FIG. 9 is a graph showing “pressure before high-pressure first stage nozzle (P1)”.
Pressure difference (Ps) between the pressure after the high pressure first stage nozzle (P2):
kPa "on the vertical axis, and" High pressure first stage blade erosion progress:
% Is shown on the horizontal axis to show a relationship curve between the two, that is, "pressure difference before and after the high pressure first stage nozzle (differential pressure) -high pressure first stage blade erosion progress monitoring curve B". This curve B is also applied to the present invention, and is produced and input as software to the damage / internal efficiency (performance) reduction monitoring system of the steam turbine.

As described above, the erosion 14 of the high-pressure first-stage blade 13 (which may be damaged in some cases) is correlated with the erosion of the nozzle plate 11 of the high-pressure first-stage nozzle 12. The damage taken by the moving blades increases as the ship progresses.

As the erosion of the nozzle plate 11 of the high-pressure first-stage nozzle 12 progresses, the pressure after the high-pressure first-stage nozzle (steam pressure on the outlet side) P2 gradually increases. That is, the pressure before the high pressure first stage nozzle (steam pressure on the inlet side) P1 and the pressure after the high pressure first stage nozzle P
2, the pressure difference (differential pressure) Ps gradually decreases. When the pressure difference (Ps) before and after the nozzle reaches a certain value (point Q in FIG. 9), the erosion 14 of the nozzle plate 11 greatly proceeds, and the mechanical strength decreases (hereinafter, this Q point is referred to as “high pressure”). First stage rotor blade mechanical strength reduction warning point Q ”).

As the erosion 14 of the nozzle plate 11 of the high-pressure first-stage nozzle 12 proceeds, the high-pressure first-stage moving blade 13 located on the downstream side of the nozzle
The backlash phenomenon due to the unbalanced flow occurs remarkably, and the following problems (a), (b) and (c) occur.

(A) A braking force acts on the rotating high-pressure first-stage moving blade 13, and an excessively repeated forced external force acts on the high-pressure first-stage moving blade 13 and its shroud 17. Repeated superposition of stress by forced external force leads to fatigue failure.

(B) Due to an increase in the nozzle throat area (see FIG. 2), the pressure at the nozzle outlet side of the high-pressure first stage nozzle 12, ie, the pressure at the moving blade inlet increases. As a result, the high-pressure first-stage blade 13
The pressure difference of the pressure increases. (Difference between the pressure at the inlet and outlet of the bucket; the pressure at the outlet side of the bucket does not change to the left and becomes higher at the inlet side, so the pressure difference covered by the bucket will increase).

As a result, the repeated bending stress acting on the shroud 17 increases. Repeated bending stresses lead to fatigue failure.

(C) Due to the erosion of the nozzle plate 11, when the high-pressure first stage nozzle 12 is not eroded, the high-pressure first-stage moving blade 1 has a relatively small scale which is not affected by the steam flow.
3, the erosion of the high-pressure first-stage bucket 13 progresses. In addition, the relative impact speed of the large scale is increased to promote erosion (scale erosion) of the high-pressure first-stage bucket 13.

When such an operating state is reached, that is, as the erosion of the high-pressure first-stage moving blades 13 progresses, the mechanical strength of the high-pressure first-stage moving blades 13 decreases, and it is not preferable to continue the operation. The pressure difference (differential pressure) R before and after the nozzle at point Q on the monitoring curve B (high pressure first stage moving blade mechanical strength decrease warning point Q) on the monitoring curve B is determined.
A warning is issued at the point (high-pressure first-stage rotor blade mechanical strength reduction warning point pressure difference before and after the nozzle (differential pressure)), and the operator immediately stops, opens, and inspects the turbine to check the high-pressure first-stage blade 13
To check the soundness and take measures. The monitoring curve B is always displayed on the display device during operation so that the current state can be checked.

An example of the concept of setting the alarm value in the “monitoring curve B” will be described below. In other words, the setting of the “alarm issuing point” for the high-pressure first-stage rotor blades 13, that is, the “alarm value” for giving an alarm of a decrease in mechanical strength of the high-pressure first-stage rotor blades 13 basically depends on the design of the blade erosion progress. The breaking strength of the high-pressure first-stage bucket 13 calculated from the degree is set with a margin. For example, when erosion progresses from a state in which the high-pressure first-stage blade 13 is not eroded and a blade erosion progress degree of 5% is set as an alarm value, the pressure difference before and after the nozzle at the point Q on the monitoring curve B ( An alarm is issued at (differential pressure) RkPa.

Nozzle for the operating time of the steam turbine,
The amount of erosion of the rotor blades depends on various conditions such as the storage conditions and operation time when the power plant is stopped, the procedure for blowing out the boiler and main steam pipe system, and the structure of the header (header) of the boiler. If the above-described alarm value is set with reference to the operation results of the power plant, the setting can be made with higher accuracy.

Next, the internal efficiency (performance) of the high-pressure turbine 5 due to the erosion of the high-pressure first-stage nozzle 12 will be described with reference to FIGS. Here, the process of lowering the internal efficiency (FIGS. 10 to 12) and the “high pressure first stage nozzle front / rear pressure difference (differential pressure) -turbine internal efficiency lowering state monitoring curve C” (FIG. 13) applied in the present invention will be described. I do.

FIGS. 10 and 11 show the flow of steam a from the high-pressure first-stage nozzle 12 to the high-pressure first-stage blade 13 and the change of the velocity triangle due to the nozzle erosion. FIG. 10 (a),
(B) is a state explanatory diagram in the case where the high-pressure first stage nozzle 12 has no erosion. In this case, as shown in FIG.
The flow of steam a at the nozzle outlet has a specified steam injection angle with respect to the rotation plane of the high-pressure first-stage bucket 13,
Due to the smooth flow along the airfoil, the acting force on the high-pressure first-stage bucket 13 has a large component in the rotation direction, and the velocity energy is converted into the rotation energy as planned. Figure 1
As shown in FIG. 0 (b), when considering the speed triangle of the steam absolute speed C, the blade peripheral speed U, and the steam relative speed W, the vector of the steam relative speed W acts as a rotation direction component.

On the other hand, FIGS. 11A and 11B are explanatory diagrams showing a state in which the high-pressure first stage nozzle 12 has significant erosion 14. In the case where the erosion 14 exists, as shown in FIG. 11A, the flow of the steam a at the nozzle outlet does not reach the specified steam injection angle with respect to the rotation plane of the high-pressure first-stage blade 13 and the airfoil A smooth flow along the route cannot be obtained.
That is, the flow of the steam a becomes a deviated flow in the axial direction, and a separation flow a0 is generated at the back and antinodes of the moving blade, and the acting force on the high-pressure first-stage moving blade 13 has a large axial component, so that it is planned. As a result, the conversion from the speed energy to the rotational energy is not performed. As shown in FIG. 11 (b), in the case of a speed triangle, the erosion causes a change in the absolute steam speed C from the normal state, which also changes the steam relative speed W.
The vector will act in the anti-rotational direction. This means that the planned work is not performed inside the turbine, and the internal efficiency is reduced.

Next, FIG. 12 is a steam diagram for explaining a change in the high pressure turbine expansion line and a change (decrease) in the internal efficiency of the high pressure turbine due to nozzle erosion.

As shown in FIG. 12, the end point of the high-pressure turbine exhaust when no erosion occurs in the high-pressure first-stage nozzle 12 is T1, but when the high-pressure first-stage nozzle 12 significantly erodes, the high-pressure first-stage nozzle outlet pressure increases. The enthalpy rises from E1 before nozzle erosion to E2 after nozzle erosion.
Therefore, the expansion line between the inlet and the outlet of the high pressure first stage nozzle has a gentler slope after the nozzle erosion than before the erosion.

On the other hand, the pressure of the high-pressure turbine exhaust is determined from the medium-pressure and low-pressure turbine inlet pressures, and shifts to T2 on the same pressure line before nozzle erosion. That is, the expansion line at the first stage of the high pressure turbine is changed from EX1 before erosion to EX2 after erosion.
Changes to

As a result, in the effective heat head, the effective heat head UE before erosion changes from the effective heat head UE before erosion to the effective heat head UE ′ after erosion.

(Equation 1) Becomes This means that the effective heat head is reduced and the internal efficiency of the turbine is reduced.

In addition, as a supplementary explanation, the internal efficiency of the turbine in each stage after the first stage of the high pressure is not particularly changed unless it undergoes significant erosion 14 like the first stage of the high pressure.
When the high pressure first stage nozzle 12 receives significant erosion 14, the pressure difference between before and after the high pressure first stage nozzle decreases, and the output of the entire turbine decreases. However, the steam control valve (not shown) is opened, and the amount of swallowed steam into the turbine is increased. It is possible to obtain an output before nozzle erosion by adopting an operation method that increases the pressure.

FIG. 13 is a diagram showing the relation between the pressure difference before and after the high-pressure first stage nozzle (differential pressure) -the internal efficiency of the turbine, which is produced and input to the steam turbine damage / internal efficiency (performance) deterioration monitoring system applied in the present invention. Drop monitoring curve ". The vertical axis in FIG. 13 indicates “high-pressure turbine internal efficiency (%)”, which is high in the upward direction and low in the downward direction. In addition, the horizontal axis indicates the “decrease rate (%) of pressure difference (differential pressure) before and after the high-pressure first stage nozzle”, where the right direction is large in the normal direction and the left direction is small in the abnormal direction. .

As described above, the erosion 14 caused by the scale of the high pressure first stage nozzle 12 causes a decrease in the internal efficiency of the high pressure turbine. In the monitoring curve D, the normal NO point where the erosion 14 is not present in the high-pressure first stage nozzle 12 is 25%, 50%, 75%, 1%.
Pressure difference before and after nozzle (differential pressure) at each load operating condition of 00%
Indicate large values of i, b, c, and d. As the erosion of the high pressure first stage nozzle 12 progresses, the pressure on the nozzle secondary side (outlet side) gradually increases, and the pressure difference (differential pressure) before and after the nozzle.
Becomes smaller accordingly. That is, the internal efficiency of the high-pressure turbine decreases.

The erosion 14 of the high-pressure first-stage nozzle 12 remarkably progresses, and the pressure difference (differential pressure) reduction rate before and after the high-pressure first-stage nozzle is normal at each operating load: NO point; Change, that is, a point at which the pressure difference (differential pressure) becomes small and becomes abnormal AB point; At point AB, an alarm is issued at points (e), (e), (d) and (c) to notify the operator of the abnormality, and the turbine is immediately stopped, opened, and inspected to repair or replace the high-pressure first-stage nozzle 12 or replace the high-pressure first-stage nozzle. The user is prompted to take action (repair or replacement, etc.) based on the inspection result of the wing 13.

In setting each monitoring point in the monitoring curve D, it goes without saying that operating conditions such as the degree of opening and closing of the steam control valve and the degree of vacuum at each operating load of the high-intermediate-pressure integrated steam turbine 1 are taken into consideration.

The present monitoring curve D is always displayed on the display device during operation so that the current state can be checked.

An example of the concept of the alarm value setting in the monitoring curve D applied to the present invention, that is, the “high-pressure first-stage nozzle front / rear pressure difference (differential pressure) -turbine internal efficiency (performance) deterioration state monitoring curve D”. Will be described below.

The warning value for issuing a warning of a decrease in the internal efficiency of the turbine is based on the rupture strength of the nozzle plate 11 calculated from the erosion rate of the nozzle plate 11 due to the erosion 14 of the nozzle plate 11 of the high-pressure first stage nozzle 12 and the erosion of the high-pressure first stage blade 13. Basically, a margin is given to the breaking strength of the high-pressure first-stage bucket 13 calculated from the degree of progress, and a point having no problem in strength is basically selected. In addition, when the nozzle plate 11 of the high-pressure first-stage nozzle 12 has no erosion at each operation load, the “pressure difference before and after the nozzle” due to the erosion of the nozzle plate from the “pressure difference before and after the high-pressure first stage nozzle (differential pressure)” From the calculation result of the turbine internal efficiency decrease value corresponding to the above, the turbine internal efficiency decrease value that is appropriate for the thermal management of the power plant is selected and set as an alarm value.

In the present invention, the classification of the operating load for issuing an alarm is 25%, 50%. Although they are 75% and 100%, the operation load can be arbitrarily determined.

FIG. 14 shows an example of a main pipe system of a typical thermal power plant.

As shown in FIG. 14, the feed water 21 is heated and pressurized by a pre-boiler system (not shown), and
2 which is further heated and pressurized to generate steam a
Enters the final superheater SH, where it is superheated, passes through the boiler outlet valve 23, the main steam pipe 24, the main steam stop valve 25, and the steam control valve 25a, and becomes the high-pressure turbine H as main steam.
P is supplied to the turbine for rotation.

The steam a1 that has worked in the high-pressure turbine HP is returned to the reheater RH of the boiler 22 via the low-temperature reheat steam pipe 26, where it is again heated and then passes through the high-temperature reheat steam pipe 27. To the medium pressure turbine IP. The steam a2 that has worked in the medium-pressure turbine IP is led to the low-pressure turbine LP, and the steam that has worked here is a cooling water 28 such as seawater.
Water is condensed in the condenser 29 that performs heat exchange with the water.

The condensate passes through a condensate pipe 30, and various devices of a pre-boiler system (not shown), for example, a condensate pump, a condensate booster pump, a condensate filtration device (pre-filter), a condensate desalination device, a low-pressure feed water heater , Deaerator, boiler feed pump,
The water is heated, degassed, and pressurized via a high-pressure feed water heater or the like, and sent to the boiler 22 again.

On the other hand, in the power plant, a main steam pipe drain pipe 31 and a scale blow pipe (or turbine bypass pipe) 32 are juxtaposed between the main steam pipe 24 and the condenser 29. A main steam drain valve 33 and a temperature reducer 34 are provided at 31, and a scale blow valve (or turbine bypass valve) 35 and a temperature reducer 36 are provided at the scale blow pipe 32.
And each is installed.

Before starting the turbine, that is, before opening the bypass valve (not shown) of the main steam stop valve 25 to ventilate the turbine, warming of the main steam pipe 24 is performed.
Perform a scale blow. The steam subjected to the warming and the scale blow is discharged to the condenser 29 after being cooled by the temperature reducers 34 and 36 through the main steam pipe drain pipe 31 and the scale blow pipe 32.

Normally, when the boiler 22 is ignited and the pressure of the main steam becomes a certain value or more, the main steam drain valve 33 and the scale blow valve 35 are opened, and the boiler 21 is heated and pressurized while condensing the scale. The blow to the container 29 is performed. Further, when the amount of mismatch between the turbine metal and the main steam temperature reaches an appropriate range and the main steam temperature at the boiler outlet tends to increase, ventilation to the turbine is performed.

The large-diameter scale mainly contained in the main steam is discharged to the condenser by the initial warming and scale flow before turbine ventilation.

After reaching a certain load after the turbine ventilation, the main steam drain valve 33 and the scale blow valve 8 are closed.

During normal load operation, the inflow of scale and foreign matter having a large particle diameter is prevented by the strainer of the main steam stop valve, but the scale and foreign matter smaller than the mesh of the strainer wire mesh flow into the steam turbine as it is.

FIG. 15 is a block diagram of a steam turbine damage / internal efficiency (performance) reduction monitoring system according to the present invention. The configuration and function will be described below.

This system is installed in the typical thermal power plant described with reference to FIG. 15 and used as a monitoring device during operation of the steam turbine.

The high pressure steam turbine HP has a pressure detector 41 (PX-1) for detecting the pressure P1 before the high pressure first stage nozzle and a pressure detector 42 for detecting the pressure P2 after the high pressure first stage nozzle.
(PX-2) is installed. The output signals S1 and S2 of these detectors 41 and 42 are input to a monitoring device 43 for monitoring damage and a decrease in internal efficiency (performance) of the steam turbine constituted by an electronic computer or the like. On the other hand, the monitoring device 43 includes “the pressure difference before and after the high-pressure first-stage nozzle (differential pressure) −the erosion rate monitoring curve A for the high-pressure first-stage nozzle plate” (see FIG. 8),
Post pressure difference (differential pressure) -High pressure first stage blade erosion progress monitoring curve B "(see FIG. 9)," Pressure difference before and after high pressure first stage nozzle (differential pressure) -turbine internal efficiency (performance) deterioration monitoring curve D " (See FIG. 13) and an "alarm set value" for issuing an alarm at each curve are produced and input as software in advance.

The monitoring device 43 executes the following function by the monitoring curve software produced and input.

1. Plant state signals, that is, pressure signals S1 and S2 before and after the high-pressure first-stage nozzle input to the system.
In response to each of the three types of monitoring curves A, B,
Create D. Then, in order to display the created monitoring curves A, B, and D on monitoring display devices (CRTs) 45, 46, and 47 installed on a control panel or an operator desk 44, the screen display signals S3, S4, and S5 are displayed. The output is performed, and the monitoring curves A, B, and D are displayed.

2. In addition, the three types of monitoring curves A,
According to the alarm set values respectively set in the softwares B and D, the input plant state signals S1,
When S2 reaches the alarm set value state, it is judged and the monitoring display devices 45, 46, 47 and the alarm display device 4 are determined.
The alarm display signals S6, S7, and S8 are output to 8, 49, and 50 to display an alarm, and the sound device 51 such as a buzzer generates an alarm sound.

The function of each software for such an alarm display and the like will be described below.

"Pressure difference before and after high pressure first stage nozzle (differential pressure)-
The software of the high-pressure first-stage nozzle plate erosion rate monitoring curve A is used when the erosion 14 of the nozzle plate 11 of the high-pressure first-stage nozzle 12 progresses and reaches the alarm setting value of the nozzle plate erosion rate, that is,
At the point X of the pressure difference before and after the nozzle at the point P in FIG. 8, an alarm display signal S6 is output to the monitoring display device 21 and the alarm display device 24 to perform an alarm display. For example, monitoring display device 4
5, a blinking display of a red character such as "nozzle plate erosion rate" and a blinking display of an alarm point on the monitoring curve A, and a display window in which "nozzle plate erosion rate" is also displayed on the alarm display device 48. Flash the lamp. At the same time, the sound device 51 such as a buzzer attached to the control panel or the operator desk 20 is sounded by the signal S6 to call attention to the operation supervisor.

The software of “pressure difference before and after high-pressure first-stage nozzle (differential pressure) −high-pressure first-stage moving blade erosion progress monitoring curve B” uses the software of high-pressure first-stage moving blade 13 erosion to progress and moving blade erosion progress. When the alarm set value is reached, that is, at the point R of pressure difference before and after the nozzle corresponding to the point Q in FIG.
6 and an alarm display device 49 to output an alarm display signal S7 to display an alarm. For example, the monitoring display device 46 has a blinking red display such as “high blade erosion progress” and a flashing display of an alarm point on the monitoring curve B, and the alarm display 49 also has characters “high blade erosion progress”. Blinks the lamp on the display window on which is described. At the same time, the sound device 51 such as a buzzer attached to the control panel or the operator desk 44 is sounded by the signal S7 to call attention to the operation supervisor.

The software of “pressure difference before and after high-pressure first-stage nozzle (differential pressure) -turbine internal efficiency (performance) reduction state monitoring curve D” shows that the erosion of the nozzle progresses and the operating load before the high-pressure first-stage nozzle at each operating load.・ After-pressure difference (differential pressure) decreases,
The monitor display device 47 and the alarm display device at the time when the alarm set values of E, H, G, and H are changed from the normal time to Z, E, G, and H in FIG. An alarm display signal S8 is output to 50 for display. For example, the monitor display 47 displays a blinking red character such as “lower turbine internal efficiency” and a flashing display of an alarm point on the monitoring curve D, and the alarm display 50 also displays a message “lower turbine internal efficiency”. Make the window lamp blink. At the same time, the sound device 51 such as a buzzer attached to the control panel or the operator desk 44 is sounded by the signal S8 to call attention to the operation supervisor.

The monitoring curve generation / display function of the monitoring device 43 and the alarm display function enable the erosion progress of the high-pressure first stage nozzle 12 during the operation of the steam turbine, the erosion progress of the high-pressure first stage rotor blades 13, and the reduction of the internal efficiency of the high-pressure turbine. The situation can be monitored and grasped.

Further, the warning of the abnormal state enables the steam turbine to be stopped immediately and the subsequent measures to be taken.

In the above description, the monitoring display device 4
Although the description has been made assuming that the number of installed alarm display devices 5, 46, 47 and the number of alarm display devices 48, 49, 50 are three for each purpose, the devices installed for each purpose can be arbitrarily switched and used. Needless to say, it is also possible to apply a method such as switching display and common use by installing only one or two of these devices.

As described above, by providing the steam turbine damage / internal efficiency (performance) deterioration monitoring system according to the present embodiment, it is possible to enhance monitoring during operation of the steam turbine in the power generation plant. In addition, since the status of equipment damage and performance degradation can always be ascertained, it contributes to the planning of construction work for disassembly, inspection, maintenance, and replacement of components, and construction can be performed at the optimal timing.

These are stable power plant operation,
It will help maintain high efficiency and prevent trouble before it meets social needs.

The present invention is not limited to the one shown in the above embodiment, but can be implemented with various modifications or applications.

For example, in the above-described embodiment, the high-pressure first-stage nozzle 12 and the high-pressure first-stage moving blade 13 in the high-pressure turbine 5 of the high-medium-pressure integrated steam turbine 1 have been described as an example. The same effect can be obtained even when applied in other paragraphs constituting a steam turbine regardless of the medium / low pressure.

In the above embodiment, the steam turbine is described as an example. However, the basic principle of the present invention can be applied to a gas turbine and a jet engine having the same structure as the steam turbine. The same effect as that of the turbine can be obtained.

Further, in the above-described embodiment, the alarm setting value for the decrease in the nozzle strength of the turbine, the alarm setting value for the rotor blade erosion progress, and the alarm setting value for the reduction in the internal efficiency (performance) are each set at one point. The alarm may be set in several stages, such as a pre-alarm and a trip alarm, and an alarm may be issued.

Furthermore, in the present invention, the "pressure difference before and after the nozzle-high pressure first stage nozzle plate erosion rate monitoring curve" and "the pressure difference before and after the high pressure first stage nozzle-high pressure first stage blade erosion" described in the above embodiment are described. The turbine operation can be performed by using any one of the progress monitoring curve, the high-pressure first stage nozzle front / rear pressure difference-turbine internal efficiency (performance) deterioration monitoring curve, or any combination of these elements as a reference. Turbine damage and reduced internal efficiency during operation may be monitored and addressed.

The means for monitoring the turbine damage and the decrease in the internal efficiency during the operation of the turbine and corresponding to it can be implemented as an operation control means in addition to a visual alarm means and an audible alarm means.

Further, monitoring elements in the turbine damage and internal efficiency reduction monitoring system described in the above embodiment,
Alarm values, graphic processing data such as those represented as curves, command data to the corresponding means for monitoring turbine damage and decrease in internal efficiency during turbine operation,
Procedures and the like are stored in a floppy disk, optical disk, or other storage device, and a general-purpose system using the same can be implemented.

[0101]

As described in detail above, according to the present invention, the maintenance and improvement of the efficiency of a thermal power plant, that is, the saving of fuel resources, is achieved by providing a system for monitoring the damage of a steam turbine and lowering the internal efficiency (performance). In addition to the above, the effects of preventing a serious accident of the steam turbine from occurring, enabling stable operation of the plant, and meeting social needs are exhibited.

[Brief description of the drawings]

FIG. 1 is an overall view for explaining an embodiment of the present invention and showing a configuration of a high-to-medium pressure integrated steam turbine.

FIG. 2 is a cross-sectional view illustrating an embodiment of the present invention and showing a nozzle box portion in an enlarged manner.

FIG. 3 is a perspective view illustrating one embodiment of the present invention and showing a nozzle box.

FIG. 4 is a perspective view illustrating one embodiment of the present invention and showing a high-pressure first-stage bucket;

FIG. 5 is an enlarged view for explaining one embodiment of the present invention and showing a nozzle plate portion.

FIG. 6 is an enlarged sectional view taken along the line AA of FIG. 5, for explaining one embodiment of the present invention;

FIG. 7 is an explanatory diagram of a nozzle throat area for explaining an embodiment of the present invention.

FIG. 8 is a characteristic diagram illustrating an embodiment of the present invention and showing a pressure difference before and after a high-pressure first-stage nozzle-erosion rate monitoring curve of a high-pressure first-stage nozzle plate.

FIG. 9 is a characteristic diagram illustrating an embodiment of the present invention and showing a pressure difference before and after a high-pressure first-stage nozzle—a high-pressure first-stage moving blade erosion progress monitoring curve.

FIG. 10 illustrates one embodiment of the present invention.
(A) is explanatory drawing which shows the steam flow in the state where there is no erosion in a nozzle plate, (b) is a figure which shows a speed triangle.

FIG. 11 illustrates one embodiment of the present invention.
(A) is an explanatory view showing a steam flow in a state where the nozzle plate has erosion, and (b) is a view showing a velocity triangle.

FIG. 12 is a steam diagram illustrating an embodiment of the present invention and showing a change in a high pressure turbine expansion line due to nozzle erosion and a change in a high pressure turbine internal efficiency.

FIG. 13 is a characteristic diagram illustrating an embodiment of the present invention and showing a pressure difference before and after a high-pressure first-stage nozzle and a monitoring curve for a state of reduced internal turbine efficiency.

FIG. 14 is a view for explaining one embodiment of the present invention and showing a main pipe system of a thermal power plant.

FIG. 15 is a view for explaining an embodiment of the present invention, and is a structural diagram of a steam turbine damage / performance degradation monitoring system.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 High-intermediate-pressure integrated steam turbine 2 Casing 3 High-pressure stage moving blade 4 Medium-pressure stage moving blade 5 High-pressure turbine 6 Medium-pressure turbine 7 Sleeve 8 Nozzle box 9 Nozzle box steam room 10 Nozzle ring 11 Nozzle plate 12 High-pressure first-stage nozzle 13 High-pressure first stage Blade 14 Erosion 15 Scale 16 Nozzle throat 17 Shroud 21 Water supply 22 Boiler 23 Boiler outlet valve 24 Main steam pipe 25 Main steam stop valve 26 Low temperature sound steam pipe 27 High temperature reheat steam pipe 28 Cooling water 29 Condenser 30 Condenser pipe 31 Main steam pipe drain pipe 32 Scale blow pipe 33 Main steam drain valve 34 Temperature reducer 35 Scale blow valve 36 Temperature reducer 41,42 Pressure detector 43 Monitoring device 44 Control panel or operator desk 45,46,47 Monitoring display Devices 48, 49, 50 Alarm display device 51 Sound device

Claims (6)

[Claims] 1. The velocity energy of a working fluid flowing into each stage constituted by a nozzle and a rotor blade inside a turbine and performing work is changed by a change in the injection angle of the working fluid due to damage to a nozzle plate of the nozzle. A system for monitoring a turbine damage and a decrease in internal efficiency during turbine operation, wherein the relationship between a pressure difference between the front and rear of the nozzle and an erosion rate of the nozzle plate and a erosion rate of the nozzle plate are monitored in advance. In addition to determining the alarm point for mechanical strength decrease of the nozzle plate based on the above, an alarm value with a certain margin is set for the breaking strength of the nozzle plate calculated from the designed nozzle erosion rate, and this alarm value is used as a reference. A turbine damage and internal efficiency decrease monitoring system for monitoring and responding to turbine damage and internal efficiency decrease during turbine operation. 2. The velocity energy of a working fluid flowing into each stage constituted by a nozzle and a rotor blade in a turbine and performing work is changed by a change in an injection angle of the working fluid due to damage to a nozzle plate of the nozzle. A turbine damage and internal efficiency reduction monitoring system that monitors a decrease in turbine operation during operation, and as a monitoring element, a relationship between a front-rear pressure difference between the nozzles and a progress degree of erosion of the blade in advance, and erosion thereof. In addition to obtaining the warning point for the decrease in mechanical strength of the moving blade based on the degree of progress, an alarm value with a certain margin is set for the breaking strength of the moving blade calculated from the degree of progress of moving blade erosion in design, and this warning is set. A turbine damage and internal efficiency reduction monitoring system that monitors and responds to turbine damage and internal efficiency reduction during turbine operation based on a value. 3. The velocity energy of a working fluid flowing into each stage constituted by a nozzle and a rotor blade inside a turbine and performing work is changed by a change in an injection angle of the working fluid due to damage to a nozzle plate of the nozzle. It is a turbine damage and internal efficiency reduction monitoring system that monitors the decrease during turbine operation, and as a monitoring element, a difference between a front-rear pressure difference reduction rate of the nozzle corresponding to a plurality of operation loads and a turbine internal efficiency in advance. The relationship and the normal value and abnormal value of the front-rear pressure difference reduction rate of the nozzle corresponding to each of the operating loads are determined, and the abnormal value of the front-rear pressure difference reduction rate of the nozzle is set as an alarm value, and A turbine damage and internal efficiency reduction monitor characterized by monitoring and responding to turbine damage and internal efficiency decrease during turbine operation based on the alarm value. Vision system. 4. The turbine during turbine operation by using two or more alarm values selected from the turbine damage and internal efficiency reduction monitoring systems according to claim 1, 2, and 3 as a reference. A turbine damage and internal efficiency reduction monitoring system for monitoring and responding to damage and internal efficiency reduction. 5. The system for monitoring turbine damage and internal efficiency deterioration according to claim 1, wherein:
Turbine damage and / or internal efficiency reduction, wherein the means for monitoring and responding to turbine damage and internal efficiency decrease during turbine operation is at least one of a visual alarm, an audible alarm, and an operation control. Monitoring system. 6. A turbine damage and internal efficiency reduction monitoring system according to claim 1, wherein the monitoring elements, alarm values, graphic processing data thereof, turbine damage and internal efficiency reduction during turbine operation are monitored. And
A floppy (registered trademark) disk, optical disk, or other storage device, wherein command data to corresponding means is stored.