CN116291791A - Bypass system control system of turbine unit - Google Patents
Bypass system control system of turbine unit Download PDFInfo
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- CN116291791A CN116291791A CN202310449708.4A CN202310449708A CN116291791A CN 116291791 A CN116291791 A CN 116291791A CN 202310449708 A CN202310449708 A CN 202310449708A CN 116291791 A CN116291791 A CN 116291791A
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
- F01K13/00—General layout or general methods of operation of complete plants
- F01K13/02—Controlling, e.g. stopping or starting
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
- F01K11/00—Plants characterised by the engines being structurally combined with boilers or condensers
- F01K11/02—Plants characterised by the engines being structurally combined with boilers or condensers the engines being turbines
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Abstract
The application provides a bypass system control system of steam turbine unit, including: the high-pressure cylinder (1), the medium-pressure cylinder (2), the boiler (3), a high-side desuperheater and a high-side desuperheater (7) arranged on a high-side desuperheater pipeline (19), a first low-side desuperheater and a first low-side desuperheater (11) arranged on a first low-side desuperheater pipeline (21), a second low-side desuperheater and a second low-side desuperheater (14) arranged on a second low-side desuperheater pipeline (23), a high-side desuperheater (4) arranged on a high-side pipeline (20), a first low-side desuperheater (8) arranged on a first low-side pipeline (22) and a second low-side desuperheater (9) arranged on a second low-side pipeline (24). The method has higher automation level, avoids the problem of overtemperature of the high and low side pipelines, and ensures that the unit has higher reliability.
Description
Technical Field
The application relates to the field of steam turbine sets, in particular to a bypass system control system of a steam turbine set.
Background
The thermal generator set converts water into high-pressure steam through a boiler, and then the high-pressure steam is conveyed to a high-pressure cylinder, a medium-pressure cylinder and a low-pressure cylinder of a steam turbine to push the steam turbine to rotate for power generation. The bypass system can stably promote the parameters of steam inlet steam of the steam turbine in the cold state, the warm state, the hot state and the extremely hot state starting process of the unit until the requirements of the steam turbine are met, so that the starting time of the unit is shortened.
The existing bypass control system of the steam turbine has low automation degree, cannot control the water temperature of high and low bypass attemperation water, and has the problem of overtemperature of high and low bypass pipelines. And the operation of each control valve is needed to be carried out manually, so that the operation is inconvenient and error is easy to occur, and the safe operation of the unit is influenced.
Disclosure of Invention
The purpose of the application is to provide a bypass system control system of a turbine unit, so that the unit has a higher automation level. Meanwhile, the method comprises the corresponding control of the high-side and low-side temperature reduction water, so that the problem of overtemperature of the high-side pipeline and the low-side pipeline is avoided, and the unit has higher reliability.
To achieve the above object, one aspect of the present application discloses a bypass system control system of a steam turbine set, comprising:
a bypass system control system for a steam turbine set, comprising: a high pressure cylinder 1, a medium pressure cylinder 2, a boiler 3, a high-side desuperheater and a high- side desuperheater 6 and 7 arranged on a high-side desuperheater pipeline 19, a first low-side desuperheater and a first low- side desuperheater 11 and 12 arranged on a first low-side desuperheater pipeline 21, a second low-side desuperheater and a second low- side desuperheater 14 and 13 arranged on a second low-side desuperheater pipeline 23, a high-side pressure reducing valve 4 arranged on a high-side pipeline 20, a first low-side pressure reducing valve 8 arranged on a first low-side pipeline 22, and a second low-side pressure reducing valve 9 arranged on a second low-side pipeline 24;
the main steam generated in the boiler 3 enters the high pressure cylinder 1 through a main steam pipe 16; steam generated by working of the high-pressure cylinder 1 enters the boiler 3 through a reheating cold end pipeline 17 to be heated, then generates reheating steam and enters the medium-pressure cylinder 2 through a reheating steam pipeline 18;
both ends of the Gao Bangguan channel 20 are respectively connected with the main steam pipeline 16 and the reheating cold-end pipeline 17; two ends of the high-side temperature reduction water pipeline 19 are respectively connected with a water supply pump and the Gao Bangguan channel 20; the two ends of the first low-side pipeline 22 are respectively connected with the reheat steam pipeline 18 and the condenser 25, and the two ends of the first low-side desuperheating water pipeline 21 are respectively connected with a condensate pump and the first low-side pipeline 22; the two ends of the second low-side pipeline 24 are respectively connected with the reheat steam pipeline 18 and the condenser 25, and the two ends of the second low-side desuperheating water pipeline 23 are respectively connected with a condensate pump and the second low-side pipeline 24.
Further, the method further comprises the following steps: a first pressure sensor 26 is provided on the main steam line 16 between the boiler 3 and the Gao Bangguan duct 20.
Further, the method further comprises the following steps: a second pressure sensor 27 is provided on the high side conduit 20 between the high side desuperheating water conduit 19 and the reheat cold end conduit 17.
Further, the method further comprises the following steps: a third pressure sensor 28 is arranged on the reheat steam line 18 and is located between the boiler 3 and the first low side line 22.
Further, the method further comprises the following steps: a first temperature sensor 29 is provided on the high side conduit 20 and is located between the second pressure sensor 27 and the reheat cold end conduit 17.
Further, the method further comprises the following steps: the second temperature sensor 30 is disposed on the first low-side pipeline 22 and is located between the first low-side desuperheating pipeline 21 and the condenser 25.
Further, the method further comprises the following steps: a third temperature sensor 31 is disposed on the second low-side conduit 24 and is located between the second low-side desuperheating conduit 23 and the condenser 25.
Further, the method further comprises the following steps: a high-side isolation valve 5 is arranged on the high-side temperature-reducing water pipeline 19.
Further, the method further comprises the following steps: a first low-side isolation valve 10 is provided on the first low-side desuperheating water pipe 21.
Further, the method further comprises the following steps: a second low-side isolation valve 15 is provided on the second low-side desuperheating water pipe 23.
The bypass system control system of the turbine unit realizes automatic control of the bypass pressure building, bypass pressure stabilizing, bypass grid connection and other processes, and the method is flexible, simple and convenient to operate, easy to implement and high in automation level; meanwhile, the method comprises the corresponding control of the high-side and low-side temperature reduction water, so that the problem of overtemperature of a high-side pipeline and a low-side pipeline is avoided, and the unit has higher reliability; the method is suitable for the high-medium pressure combined starting unit and the medium-pressure cylinder starting unit, and has a wide application range.
Drawings
In order to more clearly illustrate the embodiments of the invention or the technical solutions in the prior art, the drawings that are required in the embodiments or the description of the prior art will be briefly described, it being obvious that the drawings in the following description are only some embodiments of the invention, and that other drawings may be obtained according to these drawings without inventive effort for a person skilled in the art. In the drawings:
FIG. 1 is a block diagram of a bypass system control system of a turbine unit of the present application;
fig. 2 is a graph of the main vapor pressure as a function of the mapping of the high-side pressure relief valve 4 of the present application.
Detailed Description
The following description of the embodiments of the present application will be made clearly and fully with reference to the accompanying drawings, in which it is evident that the embodiments described are only some, but not all, of the embodiments of the present application. All other embodiments, which can be made by one of ordinary skill in the art without undue burden from the present disclosure, are within the scope of the present disclosure.
It should be noted that, the bypass system control system of the steam turbine unit disclosed in the application may be used in the field of steam turbines, and may also be used in any field other than the field of steam turbines, and the application field of the bypass system control system of the steam turbine unit disclosed in the application is not limited.
The application discloses a bypass system control system of turboset, as shown in fig. 1, this bypass system control system of turboset includes: a high pressure cylinder 1, a medium pressure cylinder 2, a boiler 3, a high-side desuperheater and a high- side desuperheater 6 and 7 arranged on a high-side desuperheater pipeline 19, a first low-side desuperheater and a first low- side desuperheater 11 and 12 arranged on a first low-side desuperheater pipeline 21, a second low-side desuperheater and a second low- side desuperheater 14 and 13 arranged on a second low-side desuperheater pipeline 23, a high-side pressure reducing valve 4 arranged on a high-side pipeline 20, a first low-side pressure reducing valve 8 arranged on a first low-side pipeline 22, and a second low-side pressure reducing valve 9 arranged on a second low-side pipeline 24;
the main steam generated in the boiler 3 enters the high pressure cylinder 1 through the main steam pipe 16; steam generated by working of the high-pressure cylinder 1 enters the boiler 3 through a reheating cold end pipeline 17 to be heated, then reheat steam is generated, and the reheat steam enters the medium-pressure cylinder 2 through a reheat steam pipeline 18;
the two ends of the high side pipeline 20 are respectively connected with the main steam pipeline 16 and the reheating cold end pipeline 17; both ends of the high-side desuperheating water pipe 19 are respectively connected with a water feed pump (which is positioned at the left end of the high-side desuperheating water pipe 19 in fig. 1 and is not shown in the figure) and a high-side pipe 20; the two ends of the first low-side pipeline 22 are respectively connected with the reheat steam pipeline 18 and the condenser 25, and the two ends of the first low-side temperature reduction water pipeline 21 are respectively connected with a condensate pump (which is positioned at the left end of the first low-side temperature reduction water pipeline 21 in fig. 1 and is not shown) and the first low-side pipeline 22; the two ends of the second low-side pipeline 24 are respectively connected with the reheat steam pipeline 18 and the condenser 25, and the two ends of the second low-side attemperation water pipeline 23 are respectively connected with a condensate pump (which is positioned at the left end of the second low-side attemperation water pipeline 23 in fig. 1 and is not shown) and the second low-side pipeline 24.
As can be seen from the structure shown in fig. 1, the main steam generated by the boiler 3 enters the high-pressure cylinder 1 through the main steam pipeline 16 to do work, the steam after the high-pressure cylinder 1 does work enters the boiler 3 again through the reheating cold end pipeline 17 to heat, and the steam after the boiler 3 heats enters the medium-pressure cylinder 2 through the reheating steam pipeline 18 to continuously do work. Part of the main steam is converged into the reheating cold-end pipeline through the high-side pipeline 20, and part of the reheating steam enters the condenser 25 through the first low-side pipeline 22 and the second low-side pipeline 24.
Each component is explained in detail below:
in one embodiment, the bypass system control system of the steam turbine set further comprises: a high-side isolation valve 5, a high-side desuperheater regulating valve 6 and a high-side desuperheater 7. The high side isolation valve 5, the high side desuperheater 6 and the high side desuperheater 7 are arranged on the high side desuperheater pipeline 19, the high side desuperheater 6 is arranged between the high side isolation valve 5 and the high side desuperheater 7, the high side isolation valve 5 is arranged at one end of the high side desuperheater pipeline 19, which is close to a water feeding pump, the high side desuperheater 7 is arranged at one end of the high side desuperheater pipeline 19, which is close to the high side pipeline 20, the high side isolation valve 5 is used for controlling the partition and the passage of the high side desuperheater pipeline 19, the high side desuperheater 6 is used for adjusting the flow of the desuperheater in the high side desuperheater pipeline 19, the high side desuperheater 7 is used for atomizing the desuperheater in the high side desuperheater pipeline 19, and the steam temperature of the high side desuperheater pipeline 19 can be effectively reduced.
In one embodiment, the bypass system control system of the steam turbine set further comprises: the first low-side isolation valve 10, the first low-side desuperheater 11 and the first low-side desuperheater 12 are arranged on the first low-side desuperheater pipeline 21, the first low-side desuperheater 11 is arranged between the first low-side isolation valve 10 and the first low-side desuperheater 12, the first low-side isolation valve 10 is arranged at one end, close to a condensate pump, of the first low-side desuperheater pipeline 21, the first low-side desuperheater 12 is arranged at one end, close to the first low-side pipeline 22, of the first low-side desuperheater pipeline 21, the first low-side isolation valve 10 is used for controlling partition and passage of the first low-side desuperheater pipeline 21, the first low-side desuperheater 11 is used for adjusting the flow of the desuperheater in the first low-side desuperheater pipeline 21, the first low-side desuperheater 12 is used for atomizing the desuperheater in the first low-temperature pipeline 21, and the steam temperature of the first low-side desuperheater pipeline 21 can be effectively reduced.
In one embodiment, the bypass system control system of the steam turbine set further comprises: the second low-side isolation valve 15, the second low-side desuperheater 14 and the second low-side desuperheater 13 are arranged on the second low-side desuperheater pipeline 23, the second low-side desuperheater 14 is arranged between the second low-side isolation valve 15 and the second low-side desuperheater 13, the second low-side isolation valve 15 is arranged at one end, close to a condensate pump, of the second low-side desuperheater pipeline 23, the second low-side desuperheater 13 is arranged at one end, close to the second low-side pipeline 24, of the second low-side desuperheater pipeline 23, the second low-side isolation valve 15 is used for controlling the partition and the passage of the second low-side desuperheater pipeline 23, the second low-side desuperheater 14 is used for adjusting the flow of the desuperheater in the second low-side desuperheater pipeline 23, the second low-side desuperheater 13 is used for atomizing the desuperheater in the second low-side desuperheater pipeline 23, and the steam temperature of the second low-side desuperheater pipeline 23 can be effectively lowered.
The high-side pipeline 20 is provided with a high-side pressure reducing valve 4, the high-side pressure reducing valve 4 is arranged between the high-side temperature reducing water pipeline 19 and the main steam pipeline 16, and the high-side pressure reducing valve 4 is used for adjusting the steam pressure on the high-side pipeline 20.
The first low-side pressure reducing valve 8 is arranged on the first low-side pipeline 22, the first low-side pressure reducing valve 8 is arranged between the first low-side desuperheating water pipeline 21 and the reheating cold-end pipeline 17, and the first low-side pressure reducing valve 8 is used for adjusting the steam pressure on the first low-side pipeline 22.
The second low-side pressure reducing valve 9 is arranged on the second low-side pipeline 24, the second low-side pressure reducing valve 9 is arranged between the second low-side temperature reducing water pipeline 23 and the reheating cold-end pipeline 17, and the second low-side pressure reducing valve 9 is used for adjusting the steam pressure on the second low-side pipeline 24.
In one embodiment, the condenser 25 is disposed at one end of the first low side pipe 22 and the second low side pipe 24, and is used for condensing the steam in the first low side pipe 22 and the second low side pipe 24 into water.
In an embodiment, a first pressure sensor 26 is arranged on the main steam line 16 between the boiler 3 and the high side line 20 for detecting the steam pressure on the main steam line 16.
In one embodiment, a second pressure sensor 27 is provided on the high side conduit 20 between the high side desuperheater conduit 19 and the reheat cold end conduit 17 for sensing the vapor pressure on the high side conduit 20.
In an embodiment, a third pressure sensor 28 is arranged on the reheat steam line 18 between the boiler 3 and the first low side line 22 for the steam pressure on the reheat steam line 18.
In one embodiment, a first temperature sensor 29 is disposed on the high side conduit 20 between the second pressure sensor 28 and the reheat cold end conduit 17 for sensing the steam temperature on the high side conduit 20.
In one embodiment, the second temperature sensor 30 is disposed on the first low-side pipeline 22 and located between the first low-side desuperheating water pipeline 21 and the condenser 25, for detecting the temperature of the steam on the first low-side pipeline 22.
In one embodiment, a third temperature sensor 31 is disposed on the second low-side conduit 24 and located between the second low-side desuperheating water conduit 23 and the condenser 25 for detecting the temperature of steam on the second low-side conduit 24.
In one embodiment, the input permission conditions of the bypass system control system of the turbine unit are as follows: the boiler has a combustion memory delay of 600s and the unit is not connected with the power grid, wherein the combustion memory means that any coal feeder operates and the corresponding coal mill operates, and the delay is 180s.
The whole-course bypass automatic control flow of the high-medium voltage combined starting unit is as follows: the boiler 3 is heated to generate main steam, the main steam is transmitted to the high-pressure cylinder 1 through the main steam pipeline 16, when the main steam pressure detected by the first pressure sensor 26 on the main steam pipeline 16 is greater than 0.5Mpa, according to a preset opening curve of the high-side pressure reducing valve 4 and a target main steam pressure value, the valve opening of the high-side pressure reducing valve 4 is adjusted to a target valve position, and the valve opening of the first low-side pressure reducing valve 8 and the second low-side pressure reducing valve 9 is adjusted to 20% according to a speed of 2.5%/s. As shown in fig. 2, the preset opening curve of the high-side pressure reducing valve 4 is a function curve related to the mapping relationship between the main steam pressure and the high-side pressure reducing valve 4, where the relationship curve is X: (0.5,1,2,3,4,5,6,7,8), Y: (5, 15, 25, 35, 45, 55, 65, 65, 65, 65).
When the valve position opening of the high-side pressure reducing valve 4 is more than 3%, the high-side isolation valve 5 is opened in an interlocking way; when the valve position opening of the first low-side pressure reducing valve 8 is more than 3%, the first low-side isolation valve 10 is opened in an interlocking manner; when the valve position opening of the second low-side pressure reducing valve 9 is greater than 3%, the second low-side isolation valve 15 is opened in an interlocking manner.
When the steam temperature detected by the first temperature sensor 29 on the high-side pipeline 20 is higher than 280 ℃, the high-side temperature-reducing water regulating valve 6 is automatically put into temperature automatic control, and the temperature setting value of the high-side temperature-reducing water regulating valve 6 is set to 295 ℃. Wherein, after the high side temperature-reducing water regulating valve 6 is put into temperature automatic control, the valve position opening is regulated according to the steam temperature detected by the first temperature sensor 29.
When the steam temperature detected by the second temperature sensor 30 on the first low-side pipeline 22 is higher than 60 ℃, the first low-side desuperheating water regulating valve 11 is automatically put into temperature automatic control, and the temperature control fixed value of the first low-side desuperheating water regulating valve 11 is set to be 70 ℃. Wherein, after the first low-side temperature-reducing water regulating valve 11 is put into temperature automatic control, the valve position opening is regulated according to the steam temperature detected by the second temperature sensor 30.
When the steam temperature detected by the third temperature sensor 31 on the second low-side pipe 24 is greater than 60 ℃, the second low-side desuperheating water regulating valve 14 is automatically put into temperature automatic control, and the temperature control fixed value of the second low-side desuperheating water regulating valve 14 is set to 70 ℃. Wherein, after the second low-side temperature-reducing water regulating valve 14 is put into temperature automatic control, the valve position opening is regulated according to the steam temperature detected by the third temperature sensor 31.
When the valve position opening of the high-side pressure reducing valve 4 is larger than 30%, and the main steam pressure detected by the first pressure sensor 26 is larger than a preset first pressure value, the high-side pressure reducing valve 4 is put into pressure automatic control, and the pressure control fixed value of the main steam is set to be the current main steam pressure value.
After the high-side pressure reducing valve 4 is automatically controlled, the opening degree of the high-side pressure reducing valve 4 is adjusted according to the main steam pressure detected by the first pressure sensor 26.
The preset first pressure value is a main steam pressure value of the washing machine set according to the starting state of the steam turbine. When the unit is started in a cold state, a first pressure value is preset to be 5MPa; when the unit is started in a temperature state, a first pressure value is preset to be 6MPa; when the unit is started in a hot state, a first pressure value is preset to be 7MPa; when the unit is started in an extremely hot state, a first pressure value is preset to be 8MPa.
When the reheat steam pressure detected by the third pressure sensor 28 on the reheat steam pipe 18 is greater than the preset second pressure value, the first low-side pressure reducing valve 8 is put into pressure automatic control, the second low-side pressure reducing valve 9 is put into pressure automatic control, and the pressure control fixed value of the reheat steam is set to be the current reheat steam pressure value.
In one embodiment, the predetermined second pressure value is 0.8MPa.
In an embodiment, the automatic pressure control of the high-side pressure reducing valve 4 has a valve position bias function, when the valve position opening of the high-side pressure reducing valve 4 is greater than 80%, the valve position of the high-side pressure reducing valve 4 is properly reduced by manually outputting the pressure bias, so that the valve position opening of the high-side pressure reducing valve 4 is not more than 80%, and vibration of the high-side pipeline 20 caused by overlarge valve position opening of the high-side pressure reducing valve 4 is avoided.
In an embodiment, the automatic pressure control of the first low-side pressure reducing valve 8 has a valve position bias function, and when the valve position opening of the first low-side pressure reducing valve 8 is greater than 80%, the valve position of the first low-side pressure reducing valve 8 is properly reduced by manually outputting the pressure bias, so that the first low-side pressure reducing valve 8 does not exceed 80%, thereby avoiding vibration of the first low-side pipeline 22 caused by excessive valve position opening of the first low-side pressure reducing valve 8.
In an embodiment, the automatic pressure control of the second low-side pressure reducing valve 9 has a valve position bias function, and when the valve position opening of the second low-side pressure reducing valve 9 is greater than 80%, the valve position of the second low-side pressure reducing valve 9 is properly reduced by manually outputting the pressure bias, so that the second low-side pressure reducing valve 9 does not exceed 80%, thereby avoiding the vibration of the second low-side pipeline 24 caused by the excessive valve position opening of the second low-side pressure reducing valve 9.
When the high-medium voltage combined starting unit is connected with the grid, when the load of the high-medium voltage combined starting unit is larger than the preset first power, the valve position of the high-side pressure reducing valve is switched to manual control by automatic control, the valve position opening of the high-side pressure reducing valve 4 is closed to 0 at the preset first closing speed, the valve position of the first low-side pressure reducing valve 8 and the valve position of the second low-side pressure reducing valve 9 are switched to manual control by automatic control, the first low-side pressure reducing valve 8 and the second low-side pressure reducing valve 9 are closed to 0 at the preset second closing speed, and the whole-process bypass automatic control is cut off.
In one embodiment, the preset first power is 20MW, the preset first closing rate is 1.5%/s, and the preset second closing rate is 5%/s.
The full-range bypass automatic control flow of the medium-pressure cylinder starting unit is as follows: the boiler 3 is heated to generate main steam, the main steam is transmitted to the high-pressure cylinder 1 through the main steam pipeline 16, when the main steam pressure detected by the first pressure sensor 26 on the main steam pipeline 16 is greater than 0.5Mpa, according to a preset opening curve of the high-side pressure reducing valve 4 and a target main steam pressure value, the valve opening of the high-side pressure reducing valve 4 is adjusted to a target valve position, and the valve opening of the first low-side pressure reducing valve 8 and the second low-side pressure reducing valve 9 is adjusted to 20% according to a speed of 2.5%/s. As shown in fig. 2, the preset opening curve of the high-side pressure reducing valve 4 is a function curve related to the mapping relationship between the main steam pressure and the high-side pressure reducing valve 4, where the relationship curve is X: (0.5,1,2,3,4,5,6,7,8), Y: (5, 15, 25, 35, 45, 55, 65, 65, 65, 65).
When the valve position opening of the high-side pressure reducing valve 4 is more than 3%, the high-side isolation valve 5 is opened in an interlocking way; when the valve position opening of the first low-side pressure reducing valve 8 is more than 3%, the first low-side isolation valve 10 is opened in an interlocking manner; when the valve position opening of the second low-side pressure reducing valve 9 is greater than 3%, the second low-side isolation valve 15 is opened in an interlocking manner.
When the steam temperature detected by the first temperature sensor 29 on the high-side pipeline 20 is higher than 280 ℃, the high-side temperature-reducing water regulating valve 6 is automatically put into temperature automatic control, and the temperature setting value of the high-side temperature-reducing water regulating valve 6 is set to 295 ℃. Wherein, after the high side temperature-reducing water regulating valve 6 is put into temperature automatic control, the valve position opening is regulated according to the steam temperature detected by the first temperature sensor 29.
When the steam temperature detected by the second temperature sensor 30 on the first low-side pipeline 22 is higher than 60 ℃, the first low-side desuperheating water regulating valve 11 is automatically put into temperature automatic control, and the temperature control fixed value of the first low-side desuperheating water regulating valve 11 is set to be 70 ℃. Wherein, after the first low-side temperature-reducing water regulating valve 11 is put into temperature automatic control, the valve position opening is regulated according to the steam temperature detected by the second temperature sensor 30.
When the steam temperature detected by the third temperature sensor 31 on the second low-side pipe 24 is greater than 60 ℃, the second low-side desuperheating water regulating valve 14 is automatically put into temperature automatic control, and the temperature control fixed value of the second low-side desuperheating water regulating valve 14 is set to 70 ℃. Wherein, after the second low-side temperature-reducing water regulating valve 14 is put into temperature automatic control, the valve position opening is regulated according to the steam temperature detected by the third temperature sensor 31.
When the valve position opening of the high-side pressure reducing valve 4 is larger than 30%, and the main steam pressure detected by the first pressure sensor 26 is larger than a preset first pressure value, the high-side pressure reducing valve 4 is put into pressure automatic control, and the pressure control fixed value of the main steam is set to be the current main steam pressure value.
After the high-side pressure reducing valve 4 is automatically controlled, the opening degree of the high-side pressure reducing valve 4 is adjusted according to the main steam pressure detected by the first pressure sensor 26.
The preset first pressure value is a main steam pressure value of the washing machine set according to the starting state of the steam turbine. When the unit is started in a cold state, a first pressure value is preset to be 5MPa; when the unit is started in a temperature state, a first pressure value is preset to be 6MPa; when the unit is started in a hot state, a first pressure value is preset to be 7MPa; when the unit is started in an extremely hot state, a first pressure value is preset to be 8MPa.
When the reheat steam pressure detected by the third pressure sensor 28 on the reheat steam pipe 18 is greater than the preset second pressure value, the first low-side pressure reducing valve 8 is put into pressure automatic control, the second low-side pressure reducing valve 9 is put into pressure automatic control, and the pressure control fixed value of the reheat steam is set to be the current reheat steam pressure value.
In one embodiment, the predetermined second pressure value is 0.8MPa.
In an embodiment, the automatic pressure control of the high-side pressure reducing valve 4 has a valve position bias function, when the valve position opening of the high-side pressure reducing valve 4 is greater than 80%, the valve position of the high-side pressure reducing valve 4 is properly reduced by manually outputting the pressure bias, so that the valve position opening of the high-side pressure reducing valve 4 is not more than 80%, and vibration of the high-side pipeline 20 caused by overlarge valve position opening of the high-side pressure reducing valve 4 is avoided.
In an embodiment, the automatic pressure control of the first low-side pressure reducing valve 8 has a valve position bias function, and when the valve position opening of the first low-side pressure reducing valve 8 is greater than 80%, the valve position of the first low-side pressure reducing valve 8 is properly reduced by manually outputting the pressure bias, so that the first low-side pressure reducing valve 8 does not exceed 80%, thereby avoiding vibration of the first low-side pipeline 22 caused by excessive valve position opening of the first low-side pressure reducing valve 8.
In an embodiment, the automatic pressure control of the second low-side pressure reducing valve 9 has a valve position bias function, and when the valve position opening of the second low-side pressure reducing valve 9 is greater than 80%, the valve position of the second low-side pressure reducing valve 9 is properly reduced by manually outputting the pressure bias, so that the second low-side pressure reducing valve 9 does not exceed 80%, thereby avoiding the vibration of the second low-side pipeline 24 caused by the excessive valve position opening of the second low-side pressure reducing valve 9.
When the medium pressure cylinder starts the machine set to be connected, when the cylinder is switched, the valve position of the high side pressure reducing valve 4 is switched to manual control by automatic control, the high side pressure reducing valve 4 is closed to 0 at a preset first closing speed, the valve position of the first low side pressure reducing valve 8 and the valve position of the second low side pressure reducing valve 9 are switched to manual control by automatic control, the valve positions of the first low side pressure reducing valve and the second low side pressure reducing valve are closed to 0 at a preset second closing speed, and the whole-process bypass automatic control is cut off.
Wherein, the first closing rate is preset to be 1.5%/s, and the second closing rate is preset to be 5%/s. The cylinder switching instruction is to switch the unit from a medium-pressure cylinder steam inlet mode to a high-pressure and medium-pressure cylinder combined steam inlet mode after the medium-pressure cylinder starts the unit to be connected.
By utilizing the method, the automatic control of the processes of bypass voltage establishment, bypass voltage stabilization, bypass grid connection and the like is realized, and the method is flexible and simple to operate and easy to implement, so that the unit has higher automation level; meanwhile, the method comprises the corresponding control of the high-side and low-side temperature reduction water, so that the problem of overtemperature of a high-side pipeline and a low-side pipeline is avoided, and the unit has higher reliability; the method is suitable for the high-medium pressure combined starting unit and the medium-pressure cylinder starting unit, and has a wide application range.
The foregoing description of the embodiments has been provided for the purpose of illustrating the general principles of the invention, and is not meant to limit the scope of the invention, but to limit the invention to the particular embodiments, and any modifications, equivalents, improvements, etc. that fall within the spirit and principles of the invention are intended to be included within the scope of the invention.
Claims (10)
1. A bypass system control system for a steam turbine set, comprising: a high pressure cylinder (1), a medium pressure cylinder (2), a boiler (3), a high-side desuperheater and a high-side desuperheater (7) arranged on a high-side desuperheater pipeline (19), a first low-side desuperheater and a first low-side desuperheater (11) arranged on a first low-side desuperheater pipeline (21), a second low-side desuperheater and a second low-side desuperheater (14) arranged on a second low-side desuperheater pipeline (23), a high-side desuperheater (4) arranged on a high-side pipeline (20), a first low-side desuperheater (8) arranged on a first low-side pipeline (22) and a second low-side desuperheater (9) arranged on a second low-side pipeline (24);
the main steam generated in the boiler (3) enters the high-pressure cylinder (1) through a main steam pipeline (16); steam generated by working of the high-pressure cylinder (1) enters the boiler (3) through a reheating cold end pipeline (17) to be heated, and then generates reheating steam which enters the medium-pressure cylinder (2) through a reheating steam pipeline (18);
two ends of the high side pipeline (20) are respectively connected with the main steam pipeline (16) and the reheating cold end pipeline (17); two ends of the high-side temperature reduction water pipeline (19) are respectively connected with a water supply pump and the high-side pipeline (20); two ends of the first low-side pipeline (22) are respectively connected with a reheat steam pipeline (18) and a condenser (25), and two ends of the first low-side desuperheating water pipeline (21) are respectively connected with a condensate pump and the first low-side pipeline (22); the two ends of the second low-side pipeline (24) are respectively connected with the reheat steam pipeline (18) and the condenser (25), and the two ends of the second low-side desuperheating water pipeline (23) are respectively connected with the condensate pump and the second low-side pipeline (24).
2. The turbine set bypass system control system of claim 1, further comprising: a first pressure sensor (26) is arranged on the main steam pipe (16) and is located between the boiler (3) and the high side pipe (20).
3. The turbine set bypass system control system of claim 1, further comprising: and a second pressure sensor (27) arranged on the high-side pipeline (20) and positioned between the high-side desuperheating water pipeline (19) and the reheating cold-end pipeline (17).
4. The turbine set bypass system control system of claim 1, further comprising: a third pressure sensor (28) is arranged on the reheat steam pipe (18) and is located between the boiler (3) and the first low side pipe (22).
5. A turbine unit bypass system control system according to claim 3, further comprising: a first temperature sensor (29) is provided on the high side conduit (20) and is located between the second pressure sensor (27) and the reheat cold end conduit (17).
6. The turbine set bypass system control system of claim 1, further comprising: and a second temperature sensor (30) which is arranged on the first low-side pipeline (22) and is positioned between the first low-side temperature-reducing water pipeline (21) and the condenser (25).
7. The turbine set bypass system control system of claim 1, further comprising: and a third temperature sensor (31) which is arranged on the second low-side pipeline (24) and is positioned between the second low-side temperature-reducing water pipeline (23) and the condenser (25).
8. The turbine set bypass system control system of claim 1, further comprising: the high-side isolation valve (5) is arranged on the high-side temperature reduction water pipeline (19).
9. The turbine set bypass system control system of claim 1, further comprising: a first low-side isolation valve (10) disposed on the first low-side desuperheating water pipe (21).
10. The turbine set bypass system control system of claim 1, further comprising: a second low-side isolation valve (15) is arranged on the second low-side desuperheating water pipeline (23).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202310449708.4A CN116291791A (en) | 2023-04-24 | 2023-04-24 | Bypass system control system of turbine unit |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202310449708.4A CN116291791A (en) | 2023-04-24 | 2023-04-24 | Bypass system control system of turbine unit |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN116291791A true CN116291791A (en) | 2023-06-23 |
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ID=86822475
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202310449708.4A Pending CN116291791A (en) | 2023-04-24 | 2023-04-24 | Bypass system control system of turbine unit |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN116291791A (en) |
-
2023
- 2023-04-24 CN CN202310449708.4A patent/CN116291791A/en active Pending
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