CN105865220A - Double backpressure condenser optimized operation device and operation method thereof - Google Patents
Double backpressure condenser optimized operation device and operation method thereof Download PDFInfo
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- CN105865220A CN105865220A CN201610373287.1A CN201610373287A CN105865220A CN 105865220 A CN105865220 A CN 105865220A CN 201610373287 A CN201610373287 A CN 201610373287A CN 105865220 A CN105865220 A CN 105865220A
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28B—STEAM OR VAPOUR CONDENSERS
- F28B11/00—Controlling arrangements with features specially adapted for condensers
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- General Engineering & Computer Science (AREA)
- Control Of Turbines (AREA)
Abstract
The invention discloses a double backpressure condenser optimized operation device and an operation method thereof. The double backpressure condenser optimized operation device comprises a high backpressure condenser, a lower backpressure condenser and a circulating water pipeline, wherein two bypasses and a control valve are arranged on the circulating water pipeline, the bypasses are connected with the two ends of the low backpressure condenser in a crossing manner, and a plurality of temperature measuring points and flow meters are arranged. Compared with the prior art, the double backpressure condenser optimized operation device has the advantages that circulating water flow rate of the low backpressure condenser is independently controlled, the circulating water flow rate of the high backpressure condenser is not influenced; by virtue of a calculation formula provided by the invention as well as the measuring points and a valve control system, the low backpressure side condenser is vacuum and does not enter a blockage backpressure region, and heat rate of a steam turbine is reduced; and due to influence of the circulating water bypasses, water inlet temperature of circulating water at the high backpressure side condenser is relatively low, and high backpressure side exhaust temperature is indirectly lowered, so that the heat rate of the steam turbine is further reduced.
Description
Technical field
The present invention relates to steam turbine control technical field, the most double back pressure turbine condenser optimizations run
Method and control system.
Background technology
Steam turbine is blocked back pressure and is referred to that the steam flow rate in steam turbine exhaust stage blade exit is close to the velocity of sound level (Mach at this
Several about 0.95) back pressure time, under normal conditions, it is relevant to steam turbine throttle flow, and different throttle flows has different obstruction
Back pressure value, steam turbine throttle flow is the least, and it is the lowest that steam turbine blocks back pressure.
After turbine back pressure is less than blocking back pressure, under same Steam Turbine generated energy, thermal loss of steam turbine rate raises.
The double back pressure turbine back pressure of thermal power plant is only in winter, when circulating cooling coolant-temperature gage is relatively low, and low back pressure side steam turbine
Back pressure just can be less than blocking back pressure.
After thermal power plant operations staff finds that turbine back pressure is less than obstruction back pressure at present, two kinds of measures are used to improve steam turbine
Back pressure:
(1) change water circulating pump operation number of units maybe will be followed pump and change low cruise into, reduce circulating water flow, low back pressure be coagulated
Vapour device back pressure raises.
This measure can make low back pressure back pressure of condenser higher than blocking back pressure, reduces thermal loss of steam turbine rate, but also makes originally
Just being not less than the high back pressure back pressure of condenser rising blocking back pressure, increase units consumption, synthesis result, this operation not necessarily saves
Energy.
(2) double pressure condenser pumped vacuum systems water ring vacuum pump only runs 1, high and low back pressure condenser evacuation system
System uses series model.
This measure can make low back pressure back pressure of condenser higher than blocking back pressure, reduces thermal loss of steam turbine rate.If but due to outward
Cause low back pressure side Vacuum System Tightness of Steam Turbines in reason to reduce, owing to pumped vacuum systems uses series model, and run
One vacuum pump, then can make low back pressure side back pressure of condenser raise, and thermal loss of steam turbine rate increases, and be difficult to be run personnel and send out
Feel.
Summary of the invention
It is an object of the invention to overcome the deficiencies in the prior art, it is provided that a kind of double pressure condenser optimized operating device
And operation method.
The present invention is achieved by the following technical solutions: a kind of double pressure condenser optimized operating device, including highback
Pressure condenser, low back pressure condenser and circulating water line, circulating water line is divided into the first circulating water line and the second recirculated water
Pipeline, the first circulating water line and the second circulating water line all flow to high back pressure condenser from low back pressure condenser, and its feature exists
In: being provided with the first bypass on the first circulation waterway, the first bypass cross-over connection is at the two ends of low back pressure condenser, in the second circulation
Being provided with the second bypass on water route, the second bypass is also connected across the two ends of low back pressure condenser, and the first bypass is provided with first
Control valve, the second bypass is provided with the second control valve.
As further improvement of these options, the first circulating water line is provided with the first temperature point,
Being provided with the second temperature point on two-cycle pipeline, the first temperature point is arranged on the outlet upstream of the first bypass, and second
Temperature point is arranged on the outlet upstream of the second bypass.
As further improvement of these options, the first circulating water line is provided with the 3rd temperature point,
Be provided with the 4th temperature point on two-cycle pipeline, the 3rd temperature point be arranged on the first bypass with the first circulating water line
The upstream of point, the second temperature point is arranged on the upstream of the second bypass and the second circulating water line.
As further improvement of these options, the first bypass is additionally provided with first-class gauge, in the second bypass
On be provided with second gauge.
As further improvement of these options, the first circulating water line is provided with the 3rd effusion meter, second
Be provided with the 4th effusion meter on circulating water line, the 3rd effusion meter be arranged on the first bypass with the first circulating water line point
Downstream, second gauge is arranged on the downstream of the second bypass and the second circulating water line.
As further improvement of these options, first-class gauge, second gauge, the 3rd effusion meter and the 4th flow
Meter is all ultrasonic flowmeter, and the outer diameter tube of the first bypass and the second bypass is the first circulating water line and the second circulating water pipe
The 1/3 of road external diameter, the external diameter of the first circulating water line and the second circulating water line is identical, the first circulating water line, the second circulation
Water lines, the first bypass are the most identical with wall thickness with the pipe material of the second bypass, and it is equal that the first control valve and second controls valve
It it is autocontrol valve；First-class gauge, second gauge, the 3rd effusion meter, the 4th effusion meter, the first temperature point, second
Temperature point, the 3rd temperature point and the 4th temperature point are all electrically connected with the DCS control system of steam turbine.
The present invention also provides for the operation method of a kind of above-mentioned double pressure condenser optimized operating device, it is characterised in that include
Following steps:
Step one, calculating steam turbine block back pressure value Pz,
Pz=f (Gms)------formula (1)
Wherein GmsBeing steam turbine main steam flow, unit is kg/s, the DCS system of steam turbine obtain；
Step 2, calculating steam turbine block exhaust temperature tz, block back pressure value according to the calculated steam turbine of step one
Pz, calculating corresponding saturated-steam temperature according to IF-97 water vapour formula is i.e. that steam turbine blocks exhaust temperature tz；
Step 3, calculating bypass adjust front low back pressure side condenser duty QCond1,
QCond1=△ t1×Gw1×Cp-------formula (2)
Wherein CpIt is recirculated cooling water specific heat capacity, takes 4.2kJ/kg DEG C, △ t1=(t31-t1+t41-t2)/2, t1、t2、t31With
t41It is that bypass adjusts front first temperature point, the second temperature point, the 3rd temperature point and the temperature of the 4th temperature point respectively,
Gw1It is circulating cooling water flow before bypass adjusts, Gw1=G31+G41-G11-G21, G11、G21、G31And G41It is by bypass respectively to adjust
Whole front first-class gauge, second gauge, the 3rd effusion meter and the data of the 4th flowmeter survey；
Step 4, calculating bypass adjust front condenser overall heat-transfer coefficient K1,
δt1=ts1-(t31+t41)/2, ts1It is low back pressure side condenser exhaust temperature before bypass adjusts, by unit DCS system
Data acquisition, A is effective heat transfer area of condenser；
Step 5, correction condenser overall heat-transfer coefficient also calculate the circulating cooling water flow upper limit,
Gw2Being the circulating cooling water flow upper limit, T represents the low back pressure side condenser exhaust temperature set higher than blocking back pressure
To the numerical value answering saturated-steam temperature；
Step 6, bypass adjust, and regulation the first control valve and second controls valve, makes G12、G22、G32And G42Meet
Gw2=G32+G42-G12-G22-----formula (5)
G12、G22、G32And G42It is by first-class gauge after bypass adjusts, second gauge, the 3rd effusion meter and the respectively
The data of four flowmeter surveys.
As further improvement of these options, T value is 2.
The present invention has the advantage that compared to existing technology and the invention belongs to individually control low back pressure condenser circulating water flow
Amount, on high back pressure side condenser circulating water flow without impact；The computing formula provided by the present invention and measuring point and valve control
System processed, so that low back pressure side condenser vacuum does not enter obstruction back pressure district, reduces thermal loss of steam turbine rate；Due to recirculated water
The impact of bypass, high back pressure side condenser recirculated water inflow temperature relative reduction, indirectly reduce high back pressure side exhaust temperature, thus
Reduce thermal loss of steam turbine rate.
Accompanying drawing explanation
Fig. 1 is schematic diagram of the present invention.
Fig. 2 is implementing procedure figure of the present invention.
Detailed description of the invention
Elaborating embodiments of the invention below, the present embodiment is carried out under premised on technical solution of the present invention
Implement, give detailed embodiment and concrete operating process, but protection scope of the present invention is not limited to following enforcement
Example.
Embodiment 1
A kind of double pressure condenser optimized operating device, including high back pressure condenser 2, low back pressure condenser 1 and circulation
Water lines, circulating water line is divided into the first circulating water line 11 and the second circulating water line 12, the first circulating water line 11 and
Two-cycle pipeline 12 all flows to high back pressure condenser 2 from low back pressure condenser 1, it is characterised in that: on the first circulation waterway
Being provided with the first bypass, the first bypass cross-over connection, at the two ends of low back pressure condenser 1, is provided with second other on the second circulation waterway
Road, the second bypass is also connected across the two ends of low back pressure condenser 1, and the first bypass is provided with the second control valve 41, and second is other
The second control valve 42 it is provided with on road.When, in unit operation, low back pressure side condenser vacuum enters after blocking back pressure district, this
The bright middle purpose arranging bypath system is to adjust low back pressure side condenser circulating water flow, thus rises height back pressure side condenser and follow
Ring water temperature rises and end is poor, final liter height back pressure side exhaust temperature, makes low back pressure side condenser vacuum not enter obstruction back pressure district.
First circulating water line 11 is provided with the first temperature point 21, the second circulating water line 12 is provided with
Two temperature points 22, the first temperature point 21 is arranged on the outlet upstream of the first bypass, and the second temperature point 22 is arranged on
The outlet upstream of two bypasses.
First circulating water line 11 is provided with the 3rd temperature point 23, the second circulating water line 12 is provided with
Four temperature points 24, the 3rd temperature point 23 is arranged on the first bypass with the first circulating water line 11 point upstream, and
Two temperature points 22 are arranged on the upstream of the second bypass and the second circulating water line 12.
First bypass is additionally provided with first-class gauge 31, the second bypass is provided with second gauge 32.
First circulating water line 11 is provided with the 3rd effusion meter 33, the second circulating water line 12 is provided with the 4th
Effusion meter 34, the 3rd effusion meter 33 is arranged on the first bypass with the first circulating water line 11 point downstream, second flow
Meter 32 is arranged on the downstream of the second bypass and the second circulating water line 12.
First-class gauge 31, second gauge the 32, the 3rd effusion meter 33 and the 4th effusion meter 34 are all ultrasonic flowmeters,
The outer diameter tube of the first bypass and the second bypass is the first circulating water line 11 and the 1/3 of the second circulating water line 12 external diameter, the
One circulating water line 11 is identical with the external diameter of the second circulating water line 12, first circulating water line the 11, second circulating water line 12,
First bypass is the most identical with wall thickness with the pipe material of the second bypass, and the second control valve 41 and the second control valve 42 are all certainly
Brake control valve door；First-class gauge 31, second gauge the 32, the 3rd effusion meter the 33, the 4th effusion meter the 34, first temperature point
21, the second temperature point the 22, the 3rd temperature point 23 and the 4th temperature point 24 all DCS control systems with steam turbine electrically connect
Connect.
Embodiment 2
The operation method of a kind of above-mentioned double pressure condenser optimized operating device, it is characterised in that comprise the steps:
Step one, calculating steam turbine block back pressure value Pz,
Pz=f (Gms)------formula (1)
Wherein GmsBeing steam turbine main steam flow, unit is kg/s, the DCS system of steam turbine obtain；
Step 2, calculating steam turbine block exhaust temperature tz, block back pressure value according to the calculated steam turbine of step one
Pz, calculating corresponding saturated-steam temperature according to IF-97 water vapour formula is i.e. that steam turbine blocks exhaust temperature tz；Controlled by unit DCS
The steam turbine main steam flow G that system processed obtainsms, calculate correspondence according to formula (1) and block back pressure value, according to IF-97 water vapour
Formula calculates corresponding saturated-steam temperature tzAs long as guaranteeing that low back pressure side condenser exhaust temperature is saturated higher than blocking back pressure correspondence
Vapor (steam) temperature tz, low back pressure side back pressure of condenser is then not less than steam turbine and blocks back pressure.
Step 3, calculating bypass adjust front low back pressure side condenser duty QCond1,
QCond1=△ t1×Gw1×Cp-------formula (2)
Wherein CpIt is recirculated cooling water specific heat capacity, takes 4.2kJ/kg DEG C, △ t1=(t31-t1+t41-t2)/2, t1、t2、t31With
t41It is that bypass adjusts front first temperature point the 21, second temperature point the 22, the 3rd temperature point 23 and the 4th temperature point respectively
The temperature of 24, Gw1It is circulating cooling water flow before bypass adjusts, Gw1=G31+G41-G11-G21, G11、G21、G31And G41Enter respectively
Row bypass adjusts the data that front first-class gauge 31, second gauge the 32, the 3rd effusion meter 33 and the 4th effusion meter 34 are measured；
Step 4, calculating bypass adjust front condenser overall heat-transfer coefficient K1,
δt1=ts1-(t3-1+t4-1)/2, ts1It is low back pressure side condenser exhaust temperature before bypass adjusts, by unit DCS system
System data acquisition, A is effective heat transfer area of condenser；
Step 5, correction condenser overall heat-transfer coefficient also calculate the circulating cooling water flow upper limit,
Obtain after above-mentioned formula is deformed
Gw2Being the circulating cooling water flow upper limit, T is tolerance surplus, represents the low back pressure side condenser exhaust temperature set high
In blocking the back pressure numerical value to answering saturated-steam temperature；
With low back pressure side condenser exhaust temperature higher than block back pressure to answer saturated-steam temperature T DEG C as separation, when
Low back pressure side vacuum enters blocks back pressure region, is bypassed by recycling water formulation so that low back pressure side condenser exhaust temperature is high
In blocking back pressure correspondence saturated-steam temperature T DEG C, it is contemplated that low back pressure side condenser recirculated water inflow temperature before and after bypass adjustment
Constant, condenser heat transfer coefficient only needs to be corrected circulating water flow, and T preferred value is 2.
Step 6, bypass adjust, and regulation the second control valve 41 and second controls valve 42, makes G12、G22、G32And G42's
Meet
Gw2=G32+G42-G12-G22-----formula (5)
G12、G22、G32And G42It is by first-class gauge 31, second gauge the 32, the 3rd effusion meter after bypass adjusts respectively
33 and the 4th effusion meter 34 measure data.
DCS automatic control system controls valve 42 aperture by increasing by the second control valve 41 and second simultaneously, until entirely
Open so that be G by low back pressure side condenser circulating cooling water floww2, adjustment terminates, and low back pressure side condenser vacuum is no longer located
In blocking back pressure district.
After first bypass valve and the second valve opening, if owing to unit load reduces, or follow the change of pump operation pattern
Increase to circulating water flow, or circulating water temperature raises so that low back pressure side condenser exhaust temperature is higher than blocking back pressure pair
Answer saturated-steam temperature more than 2 DEG C, then repetition step 3 is to step 6, and reduces the second control valve 41 and second in step 6
Control valve 42 so that circulating water flow meets requirement, until fully closed.
These are only presently preferred embodiments of the present invention, not in order to limit the present invention, all spirit in the present invention and
Any amendment, equivalent and the improvement etc. made within principle, should be included within the scope of the present invention.
Claims (8)
1. a double pressure condenser optimized operating device, including high back pressure condenser, low back pressure condenser and circulating water pipe
Road, described circulating water line is divided into the first circulating water line and the second circulating water line, described first circulating water line and second
Circulating water line all flows to high back pressure condenser from low back pressure condenser, it is characterised in that: it is provided with on the first circulation waterway
First bypass, described first bypass cross-over connection, at the two ends of low back pressure condenser, is provided with the second bypass on the second circulation waterway,
Described second bypass is also connected across the two ends of low back pressure condenser, and described first bypass is provided with the first control valve, described
It is provided with the second control valve in second bypass.
2. a kind of double pressure condenser optimized operating device, it is characterised in that: at the first circulating water line
On be provided with the first temperature point, the second circulating water line is provided with the second temperature point, described first temperature point sets
Putting the outlet upstream in the first bypass, described second temperature point is arranged on the outlet upstream of the second bypass.
3. a kind of double pressure condenser optimized operating device, it is characterised in that: at the first circulating water line
On be provided with the 3rd temperature point, the second circulating water line is provided with the 4th temperature point, described 3rd temperature point sets
Putting the upstream with the first circulating water line point in the first bypass, described second temperature point is arranged on the second bypass and the
The upstream of two-cycle pipeline.
4. a kind of double pressure condenser optimized operating device, it is characterised in that: also set in the first bypass
It is equipped with first-class gauge, the second bypass is provided with second gauge.
5. a kind of double pressure condenser optimized operating device, it is characterised in that: at the first circulating water line
On be provided with the 3rd effusion meter, the second circulating water line is provided with the 4th effusion meter, described 3rd effusion meter is arranged on
The downstream with the first circulating water line point of one bypass, described second gauge is arranged on the second bypass and the second recirculated water
The downstream of pipeline.
6. a kind of double pressure condenser optimized operating device, it is characterised in that: described first-class gauge,
Second gauge, the 3rd effusion meter and the 4th effusion meter are all ultrasonic flowmeters, described first bypass and the pipe of the second bypass
Road external diameter is the first circulating water line and the 1/3 of the second circulating water line external diameter, the first circulating water line and the second circulating water pipe
The external diameter on road is identical, described first circulating water line, the second circulating water line, first bypass and second bypass pipe material and
Wall thickness is the most identical, and described first control valve and second to control valve to be all autocontrol valve；Described first-class gauge, second
Effusion meter, the 3rd effusion meter, the 4th effusion meter, the first temperature point, the second temperature point, the 3rd temperature point and the 4th temperature
Measuring point is all electrically connected with the DCS control system of steam turbine.
7. the operation method of a double pressure condenser optimized operating device as claimed in claim 5, it is characterised in that include as
Lower step:
Step one, calculating steam turbine block back pressure value Pz,
Pz=f (Gms)------formula (1)
Wherein GmsBeing steam turbine main steam flow, unit is kg/s, the DCS system of steam turbine obtain；
Step 2, calculating steam turbine block exhaust temperature tz, block back pressure value P according to the calculated steam turbine of step onez, root
Calculating corresponding saturated-steam temperature according to IF-97 water vapour formula is i.e. that steam turbine blocks exhaust temperature tz；
Step 3, calculating bypass adjust front low back pressure side condenser duty QCond1,
QCond1=Δ t1×Gw1×Cp-------formula (2)
Wherein CpIt is recirculated cooling water specific heat capacity, takes 4.2kJ/kg DEG C, Δ t1=(t31-t1+t41-t2)/2, t1、t2、t31And t41Point
It not that bypass adjusts front first temperature point, the second temperature point, the 3rd temperature point and the temperature of the 4th temperature point, Gw1It is
Bypass adjusts front circulating cooling water flow, Gw1=G31+G41-G11-G21, G11、G21、G31And G41Before being by bypass adjustment respectively
First-class gauge, second gauge, the 3rd effusion meter and the data of the 4th flowmeter survey；
Step 4, calculating bypass adjust front condenser overall heat-transfer coefficient K1,
δt1=ts1-(t31+t41)/2, ts1It is low back pressure side condenser exhaust temperature before bypass adjusts, by unit DCS system data
Obtaining, A is effective heat transfer area of condenser；
Step 5, correction condenser overall heat-transfer coefficient also calculate the circulating cooling water flow upper limit,
Gw2Being the circulating cooling water flow upper limit, T represents the low back pressure side condenser exhaust temperature set higher than blocking back pressure pair
Answer the numerical value of saturated-steam temperature；
Step 6, bypass adjust, and regulation the first control valve and second controls valve, makes G12、G22、G32And G42Meet
Gw2=G32+G42-G12-G22-----formula (5)
G12、G22、G32And G42It is by first-class gauge after bypass adjusts, second gauge, the 3rd effusion meter and the 4th stream respectively
The data of flowmeter measurement.
8. the operation method of double pressure condenser optimized operating device as claimed in claim 7, it is characterised in that: described T value
It is 2.
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| CN107421350A (en) * | 2017-07-18 | 2017-12-01 | 西安西热节能技术有限公司 | A kind of double pressure condenser takes out air SR matching intelligent adjusting method |
| CN111306956A (en) * | 2020-02-10 | 2020-06-19 | 山东电力工程咨询院有限公司 | System and method for controlling exhaust steam pressure of direct air cooling unit |
| CN113188341A (en) * | 2021-05-31 | 2021-07-30 | 华能威海发电有限责任公司 | Multi-dimensional online optimization control method for optimal vacuum of condenser |
| CN114440655A (en) * | 2021-11-08 | 2022-05-06 | 河北西柏坡第二发电有限责任公司 | Circulating water flow regulating system of double-backpressure steam turbine condenser |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN107421350A (en) * | 2017-07-18 | 2017-12-01 | 西安西热节能技术有限公司 | A kind of double pressure condenser takes out air SR matching intelligent adjusting method |
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| CN114440655A (en) * | 2021-11-08 | 2022-05-06 | 河北西柏坡第二发电有限责任公司 | Circulating water flow regulating system of double-backpressure steam turbine condenser |
| CN114440655B (en) * | 2021-11-08 | 2024-02-27 | 河北西柏坡第二发电有限责任公司 | Circulating water flow regulating system of condenser of double back pressure turbine |
Also Published As
| Publication number | Publication date |
|---|---|
| CN105865220B (en) | 2017-08-04 |
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