Method for regulating a valve

Abstract

A method for regulating a steam bypass valve is provided. The bypass valve is arranged in a steam line and the steam line includes a device for spraying water. The equation,

Description

FIELD OF INVENTION

The invention relates to a method for regulating a valve, wherein the valve is arranged in a steam line, wherein the steam line has a device for spraying water.

BACKGROUND OF INVENTION

During starting or ramping up of a fossil-fired power plant, a boiler of the power plant, which is designed for producing steam, is initially operated at minimum load, which usually lies between 30% and 40% load. The live steam which is produced during this ramping-up phase is in this case customarily initially routed past the steam turbine directly to the condenser in so-called bypass mode. In the case of plants with a reheater, the live steam in this case is conducted via a high-pressure bypass station, spray-cooled to a low temperature level, and then directed into the cold line of the reheater. The steam which leaves the hot line of the reheater is conducted via an intermediate-pressure bypass station and cooled by means of spraying with water, and directed into the condenser. As a result of a high pressure level in the reheater, which customarily lies between about 20 bar and 30 bar, effective cooling of the reheater tubes, which are impinged upon by flue gas, is ensured.

For the operation of steam turbine plants, high demands are to be placed upon the purity of the steam. In particular, it is necessary to avoid particulate solids being entrained in the steam. Such solid body particles can lead to damage to the steam turbine and other plant components. Damage is incurred especially on the blading of the turbine.

In order to achieve slight superheating, it is necessary that the steam volume which is conducted via the intermediate-pressure bypass steam line is cooled to a low temperature level. This means that the bypass steam in the bypass steam line has to be spray-cooled with water. However, this requires a reliable and direct availability of the volume of water which is to be sprayed. Furthermore, a fast-acting spray water valve and a reliable measuring technique are required.

If the water which is to be sprayed is totally absent, precautions have to be taken so that no damage occurs. At present, the existing water spray protection devices are designed in such a way that only a total absence of spray water is taken into consideration.

Even temporarily falling short of the necessary volume of water is considered to be a malfunction, which in the worst case can lead to a total closing of the bypass steam line and could even lead to a trip, that is to say a shutdown of the entire power plant would be the consequence.

An initiated emergency shutdown of the bypass station can lead to repercussions upon the inspection interval or upon the service life of the gas turbine in the event of a gas turbine trip.

With the present precautions, it is quite possible that an emergency shutdown of the bypass station is carried out, even though a volume of water of more than 90% of the desired value has already been achieved and an emergency shutdown as such would not be necessary.

SUMMARY OF INVENTION

The invention comes in at this point, the object of which invention is to disclose a method for regulating a valve, with which method an emergency shutdown of the bypass station is executed in such a way that a premature closing of the valve is avoided.

This object is achieved by a method for regulating a valve according to the claims. In this case, the valve is arranged in a steam line, wherein the steam line has a device for spraying water, wherein an actual volume of water {dot over (m)}_W,IST and a desired volume of water {dot over (m)}_W,SOLL and a maximum water-volume deficiency FB_max are determined, and a quotient t_Rest,0 between the maximum water volume deficiency FB_max and the difference between the desired water volume {dot over (m)}_W,SOLL and the actual volume of water {dot over (m)}_W,IST is formed according to the equation

$t_{\mathrm{Rest},0}=\frac{{\mathrm{FB}}_{\max }}{{\stackrel{.}{m}}_{W,\mathrm{SOLL}}-{\stackrel{.}{m}}_{W,\mathrm{IST}}}$

and the valve closes if t_Rest,0 is smaller than a value Δt.

The invention is based on the idea that the currently existing precautions allow an operation of the bypass station without sufficient volumes of spray water for a specific time t_max. The aforesaid precaution applies independently of the steam volume and the volume of spray water in the bypass station, i.e. that even for the maximum steam volume and totally absent volumes of spray water, the precautions are possible.

If a volume of spray water is absent as a result of a malfunction, this results in a lack of cooling. The lack of cooling is referred to as deficiency (FB) with regard to the enthalpy difference of the evaporating water and is produced by an integration of a deficient quantity over time, which is specified by the following equation: {dot over (m)}_W,SOLL−{dot over (m)}_W,IST. In this case, {dot over (m)}_W,SOLL refers to the water flow rate and {dot over (m)}_W,IST refers to the actual volumes of water.

The maximum permissible deficiency is produced by the following equation:

FB_max={dot over (m)}_W,max×t_max,0, wherein {dot over (m)}_W,max represents the maximum volume of spray water and t_max,0 represents the maximum time without water spraying. The deficiency which is accumulated until initiation of an emergency shutdown is calculated according to the following:

${\mathrm{FB}}_{\max }={\int }_0^{t_{\max }}({\stackrel{.}{m}}_{W,\mathrm{SOLL}}-{\stackrel{.}{m}}_{W,\mathrm{IST}})t.$

It is necessary that the maximum time allowed for reaching the maximum permissible deficiency is reached when the integrally determined deficiency is equal to the maximum permissible deficiency. This is achieved if the following equation is satisfied:

${\int }_0^{t_{\max }}({\stackrel{.}{m}}_{W,\mathrm{SOLL}}-{\stackrel{.}{m}}_{W,\mathrm{IST}})t={\stackrel{.}{m}}_{W,\max }\times t_{\max ,0}.$

If this equation is solved according to t_max,0, the maximum time allowed can be determined. However, in this case the precondition must be fulfilled that the determined volumes of water m_W,SOLL and m_W,IST are in compliance with the following equation:

$\frac{m_{W,\mathrm{SOLL}}}{m_{W,\mathrm{IST}}}>1,$

which means that the actual volume of water is too low. According to the invention, the currently absent volume of spray water m_W,SOLL−m_W,IST is calculated within specified time intervals Δt and with the last accumulated deficiency is converted into a permissible residual time. If this calculated residual time falls below a cycle rate Δt, the valve is closed.

Advantageous developments are disclosed in the dependent claims.

In a first advantageous development, the maximum water-volume deficiency FB_max is formed from a multiplication between a maximum volume of spray water and a maximum time according to the equation FB_max={dot over (m)}_W,max×t_max.

In a further advantageous development, the actual volume of water {dot over (m)}_W,IST and the desired volume of water {dot over (m)}_W,SOLL are determined according to each cycle rate Δt. This cycle rate can be optionally selected according to the invention, which leads to more accurate control than control with a longer cycle rate Δt.

According to an advantageous development, according to each cycle rate Δt a residual time is determined and the valve is closed if the residual time t_Rest,i is less than the value Δt, wherein i is to represent a counting of a loop, starting at zero, according to which the residual time t_Rest,i is calculated in each case. This has the advantage that an integration is carried out, which integration leads to not just a criterion having to be fulfilled in order to achieve closing of the valve.

According to the invention, the residual time t_Rest,i is determined according to the trapezoid rule.

BRIEF DESCRIPTION OF THE DRAWINGS

The invention is explained in more detail with reference to the schematic drawings. An exemplary embodiment of the invention is explained in more detail with reference to a drawing. In the drawing:

FIG. 1 shows a construction of a steam power plant,

FIG. 2 shows a schematic representation of a flow diagram

FIGS. 3, 4 show graphic representations on the time base.

DETAILED DESCRIPTION OF INVENTION

FIG. 1 schematically shows the construction of a steam power plant 10 according to the invention. The steam power plant 10 comprises inter alia a boiler 12, a high-pressure turbine 14, an intermediate-pressure turbine 16, a low-pressure turbine 18, a generator which is not shown in more detail, a condenser 22 and a live steam line 28. Live steam which is produced in the boiler 12 is conducted via the live steam line 28 and via a live steam valve 30 to the high-pressure turbine section 14.

Downstream of the high-pressure turbine 14, the outflowing steam makes its way to a reheater 32 and from there into an intermediate-pressure turbine section 16. The outlet of the intermediate-pressure turbine section 16 is fluidically connected to an inlet of a low-pressure turbine section 18. The steam which discharges from the low-pressure turbine section 18 is fluidically connected via a low-pressure line 34 to the condenser 22.

In the condenser 22, the steam condenses, forming water, and via a pump 36 is directed again to the boiler 12, as a result of which a water-steam cycle is completed.

During starting or during shutting down of the steam power plant 10, the live steam is routed via a bypass line 38 past the high-pressure turbine 14 and conducted directly into the cold reheater line 40. The hot reheater line 42 which is constructed downstream of the reheater 32 is fluidically connected via an IP bypass station 44 to the condenser 22. Formed in this IP bypass station 44 are an IP bypass valve 46 and a device 48 for spraying water into the IP bypass station 44.

During starting or ramping up of the steam power plant 10, the boiler 12 is initially operated at minimum load (in most cases 30% to 40% load), wherein the steam which is produced is customarily initially routed past the high-pressure turbine 14 (bypass mode). The bypass mode is realized in this case by closing the emergency stop valve 31 which is arranged in the steam inflow section of the high-pressure turbine 14, wherein the live steam is conducted via a high-pressure bypass station 38 or bypass line 38, spray-cooled to a lower temperature level and then fed to a reheater 32, in fact initially to the cold line 40 of the reheater. The steam which leaves the hot line 42 of the reheater is conducted via an intermediate-pressure bypass station 44 and after cooling by means of sprayed water is directed into the condenser 22. As a result of a high pressure level in the reheater 32, effective cooling of the reheater tubes, which are impinged upon by flue gas, is ensured in the process.

The controlling of the valve 46 is carried out as described in the following: Initially, a cycle rate Δt in seconds is predetermined or preset and a maximum permissible deficiency FB_max (in kilograms) is also calculated, which deficiency can be determined in a first approximation by the following equation:

FB _max ={dot over (m)} _W,max ×t _max,0.

In a subsequent step, as shown in FIG. 2, a time t₀ equal to 0 is set if the condition of {dot over (m)}_W,IST being less than {dot over (m)}_W,SOLL is fulfilled. This means that as soon as the required volume of water in the device 48, which is conducted into the IP bypass station 44, is less than the desired volume of water, an integration begins. Initially, a volume of water is determined from a characteristic curve. Then, via a measurement, the actual volume of water is determined. A calculation of the residual time

$t_{\mathrm{Rest},0}=\frac{{\mathrm{FB}}_{\max }}{{\stackrel{.}{m}}_{W,\mathrm{SOLL},0}-{\stackrel{.}{m}}_{W,\mathrm{IST},0}}$

is then carried out.

For further integration, the number variable i is set to zero. It is then determined whether the residual time is greater than the cycle rate. If the residual time is greater than the cycle rate, this case with “yes” is led to a further calculation loop, as shown in FIG. 2. This means that the index i is increased by 1 and a residual time is recalculated according to the trapezoid rule. To this end, the formula which is presented in the box 50 is used.

FIGS. 3 and 4 show different characteristic curves of the individual variables.

FIG. 3 shows the characteristic curve of the desired value 54 and the maximum deficiency FB_max 56 on a time scale 52.

For the time t less than t₀, no spray water is available, which means that in the time period up to t₀ the absence of spray water 55 prevails. After the time point t₀, the integration begins, which is represented by the curve 58 and leads to an emergency shutdown at time point t_max. The initiation of the bypass emergency shutdown is represented by the curve 60. FIG. 3 represents the situation that there is 100% deficiency of the volume of water. This means, for example, that the valve remains in the “closed” position despite demand.

FIG. 4 shows a repetitive absence of spray water within a short time interval. At the time point t₀, the start of the integration 62 begins. The integrator 64 initially starts steeply and then runs back. During this time, the actual value 66 lies above the desired value. This means that during this time an emergency shutdown is not necessary. As soon as the actual value at the time point t₂ drops below the desired value again, the integration is continued, which is represented by the linear rise of the integrator 64. If the actual value at the time point t₃ is again greater than the desired value, the integrator runs back again, which is represented by the stepped line. At the time point t₄, the actual value is again below the desired value, which again leads to a rise of the integrator. However, the integrator rises to the value FB_max 70, which leads to an emergency shutdown 72 being executed at the time point t_max.

Claims

1-8. (canceled)

9. A method for regulating a valve, comprising: arranging the valve in a steam line wherein the steam line has a device for spraying water;determining an actual volume of water {dot over (m)}W,IST, a desired volume of water {dot over (m)}W,SOLL and a maximum water-volume deficiency FBmax;forming a quotient, tRest,0 between the maximum water-volume deficiency FBmax and the difference of the desired volume of water {dot over (m)}W,SOLL and the actual volume of water {dot over (m)}W,IST according to the equation:

10. The method as claimed in claim 9, wherein the maximum water-volume deficiency FBmax is formed from a multiplication between a maximum volume of spray water {dot over (m)}W,max and a maximum time tmax,0 according to the equation FBmax={dot over (m)}W,max×tmax,0.

11. The method as claimed in claim 9, wherein the value Δt is a cycle rate and the actual volume of water {dot over (m)}W,IST and the desired volume of water {dot over (m)}W,SOLL are determined according to each cycle rate Δt.

12. The method as claimed in claim 11, wherein according to each cycle rate Δt, a residual time tRest,i is determined and the valve closes when the residual time tRest,i is less than the value Δt, andwherein i represents a counting of a loop, starting at zero, according to which the residual time tRest,i is calculated in each case.

13. The method as claimed in claim 12, wherein the residual time tRest,i is determined according to a loop according to the following formula: tRest,i=(({dot over (m)}W,SOLL−{dot over (m)}W,IST)i-1×tREST,i-1−0.5×(({dot over (m)}W,SOLL−{dot over (m)}W,IST)i-1+({dot over (m)}W,SOLL−{dot over (m)}W,IST)i)×Δt)/.({dot over (m)}W,SOLL−{dot over (m)}W,IST)i.

14. The method as claimed in claim 12, wherein the residual time tRest,i is determined according to the trapezoid rule.

15. The method as claimed in claim 9, wherein the water which is sprayed into the steam line is provided for cooling steam which flows in the steam line.

16. The method as claimed in claim 9, wherein the maximum deficiency FBmax represents a deficient maximum volume of water which is sprayed into the steam line for cooling and is determined according to the following equation: FBmax={dot over (m)}W,max×tmax,0,wherein {dot over (m)}W,max represents a maximum volume of sprayed water and tmax,0 represents a maximum time without water spraying.