CN114251135B - Low-flow low-load operation method of steam seal system of steam supplementing turbine unit - Google Patents
Low-flow low-load operation method of steam seal system of steam supplementing turbine unit Download PDFInfo
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- CN114251135B CN114251135B CN202011009639.8A CN202011009639A CN114251135B CN 114251135 B CN114251135 B CN 114251135B CN 202011009639 A CN202011009639 A CN 202011009639A CN 114251135 B CN114251135 B CN 114251135B
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- 230000001502 supplementing effect Effects 0.000 title claims abstract description 72
- 238000000034 method Methods 0.000 title claims abstract description 29
- 238000007789 sealing Methods 0.000 claims abstract description 76
- 239000013589 supplement Substances 0.000 claims abstract description 12
- 238000011144 upstream manufacturing Methods 0.000 claims abstract description 6
- 210000004907 gland Anatomy 0.000 claims description 32
- 230000001105 regulatory effect Effects 0.000 claims description 13
- 238000011010 flushing procedure Methods 0.000 claims description 5
- 238000013021 overheating Methods 0.000 description 4
- 230000002411 adverse Effects 0.000 description 3
- 230000000694 effects Effects 0.000 description 3
- 238000012986 modification Methods 0.000 description 3
- 230000004048 modification Effects 0.000 description 3
- 238000005422 blasting Methods 0.000 description 2
- 238000007664 blowing Methods 0.000 description 2
- 238000013461 design Methods 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 239000002699 waste material Substances 0.000 description 2
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 1
- 238000004891 communication Methods 0.000 description 1
- 230000002596 correlated effect Effects 0.000 description 1
- 230000007547 defect Effects 0.000 description 1
- 230000003993 interaction Effects 0.000 description 1
- 238000010248 power generation Methods 0.000 description 1
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
- F01D11/00—Preventing or minimising internal leakage of working-fluid, e.g. between stages
- F01D11/02—Preventing or minimising internal leakage of working-fluid, e.g. between stages by non-contact sealings, e.g. of labyrinth type
- F01D11/04—Preventing or minimising internal leakage of working-fluid, e.g. between stages by non-contact sealings, e.g. of labyrinth type using sealing fluid, e.g. steam
- F01D11/06—Control thereof
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Turbine Rotor Nozzle Sealing (AREA)
Abstract
The invention provides a low-flow low-load operation method of a steam seal system of a steam-supplementing turbine unit, which comprises the following steps: when the running load of the turbine unit reaches a load point and the steam sealing system of the steam supplementing turbine unit is in a self-sealing state, the steam supplementing pipe supplements redundant steam in the steam sealing main pipe into a through-flow structure of the turbine; when the operation load of the turbine unit is lower than the load point and the steam sealing system of the steam supplementing turbine unit is in a non-self-sealing state, the high-pressure steam source or the starting steam source supplies steam to the steam sealing main pipe so as to maintain the constant pressure of the steam sealing main pipe, and the steam supplementing pipe supplements the steam to the next-last-stage stator blade or the upstream side of the next-last-stage stator blade of the turbine. The invention not only can improve the operation efficiency of the turbine unit under the working condition of the load point, but also can avoid vortex blast and overheat phenomenon of the turbine unit under the working condition of low flow and low load, and improve the low load operation capacity of the turbine unit with low load operation safety.
Description
Technical Field
The invention relates to the technical field of power station turbines, in particular to a low-flow low-load operation method of a steam seal system of a steam-supplementing turbine unit.
Background
The low-load operation capability of the condensing steam turbine is always a hot topic concerned by steam turbine manufacturers and power plants, and is closely related to the deep peak regulation and wide low-load operation capability of the unit. Especially in the background environment that the traditional thermal power generation energy is required to be yielded for clean power energy, the low-load operation capability of the traditional power station steam turbine is more actively focused.
As shown in fig. 1, under rated conditions, the flow rate of the through-flow steam of the last stage blade 01 of the steam turbine reaches the rated value, and a stable ordered flow field 02 is formed inside the through-flow steam. As shown in fig. 2, when the unit runs under low load, the volume flow of steam at the last stage blade 01 is less than the design working condition, the streamline starts to twist, when the volume flow is reduced to a certain value, the root of the movable blade is subjected to flow removal, a negative speed component appears in a countercurrent region, the steam flows back to the movable blade, the steam outlet edge of the root of the movable blade is subjected to water rinsing, and the interaction of the steam flow in the negative speed direction and the main flow forms a circular vortex, namely a turbulent flow field 03 is formed in the circular vortex. The harm and adverse effect on the unit are as follows: (1) The vortex region causes strong vortex loss, so that the stage efficiency is reduced; (2) The movable vanes can generate strong vibration, so that dynamic stress is increased, and the safety of the unit is threatened; (3) The movable blades do friction work on the through-flow steam to generate air blast, so that the exhaust steam is overheated, and the safety of the movable blades and the condenser is not good. Studies have shown that the extent of the adverse effects on the above-mentioned problems is related to the volumetric flow rate of the steam in the last stage blade zone, the smaller the volumetric flow rate of the steam, the higher the adverse extent.
Disclosure of Invention
In view of the above-mentioned drawbacks of the prior art, the present invention is to provide a low-flow low-load operation method for a steam seal system of a steam turbine set of a steam supplementing type, which not only can improve the operation efficiency of the steam turbine set under a load point working condition, but also can avoid vortex blast and overheating phenomena of the steam turbine set under a low-flow low-load working condition, thereby improving the low-load operation capability of the low-load operation safety of the steam turbine set.
In order to solve the technical problems, the invention provides a low-flow low-load operation method of a steam seal system of a steam-supplementing turbine unit, which comprises the following steps:
when the running load of the turbine unit reaches a load point and the steam sealing system of the steam supplementing turbine unit is in a self-sealing state, the steam supplementing pipe supplements redundant steam in the steam sealing main pipe into a through-flow structure of the turbine;
when the operation load of the turbine unit is lower than the load point and the steam sealing system of the steam supplementing turbine unit is in a non-self-sealing state, the high-pressure steam source or the starting steam source supplies steam to the steam sealing main pipe so as to maintain the constant pressure of the steam sealing main pipe, and the steam supplementing pipe supplements the steam to the next-last-stage stator blade or the upstream side of the next-last-stage stator blade of the turbine.
Preferably, the method further comprises the following steps:
when the steam turbine unit is turned on, vacuumized and started, steam supplied by the starting steam source flows into the gland sealing main pipe through the auxiliary steam source control station, and the starting regulating valve of the auxiliary steam source control station regulates the pressure of the gland sealing main pipe to be 0.125-0.130 MPa.
Preferably, the method further comprises the following steps:
when the turbine unit starts the flushing rotation by adopting medium parameters and the pressure of main steam is increased to 3.5-5 MPa, the high-pressure steam source replaces the starting steam source to supply steam to the gland box main pipe, and the high-pressure regulating valve of the high-pressure steam source control station maintains the pressure of the gland box main pipe to be 0.125-0.130 MPa; or the starting steam source continuously supplies steam to the gland box main pipe through the auxiliary steam source control station.
Preferably, the method further comprises the following steps:
when the operation load of the turbine unit reaches 27% -33% of the rated load, the steam leakage amount at the high-pressure side of the turbine exceeds the steam supply amount required at the low-pressure side of the turbine; when the pressure of the gland sealing main pipe is increased to 0.130-0.135 MPa, the overflow valve is opened, the auxiliary steam source control station is closed, the gland sealing system of the steam supplementing turbine unit enters a self-sealing state, and the overflow valve maintains the pressure of the gland sealing main pipe to be 0.130-0.135 MPa.
Preferably, the temperature difference between the steam in the steam supplementing pipe and the steam in the steam turbine is 30 to 50 kelvin and the pressure difference is 0.05 to 0.2MPa.
Preferably, before the turbine unit is started, or in the processes of flushing and lifting load, the steam supplementing regulating valve arranged on the steam supplementing pipe is in a fully closed state.
Preferably, the steam sealing system of the steam turbine unit comprises:
the high-pressure side of the steam turbine is provided with a high-pressure side steam flow channel, and the low-pressure side of the steam turbine is provided with a low-pressure side steam flow channel;
the steam seal main pipe is communicated with the high-pressure side steam flow channel through the high-pressure side steam seal pipe, and is communicated with the low-pressure side steam flow channel through the low-pressure side steam seal pipe, and a first desuperheater and an overflow valve are arranged on the steam seal main pipe;
the steam supply system comprises a high-pressure steam source control station, an auxiliary steam source control station, a steam supply pipe, a high-pressure steam source and a starting steam source, wherein the high-pressure steam source control station and the auxiliary steam source control station are mutually connected in parallel and then are communicated with a steam seal main pipe through the steam supply pipe, a second desuperheater is arranged on the steam supply pipe, the high-pressure steam source is connected with the high-pressure steam source control station, and the starting steam source is connected with the auxiliary steam source control station;
one end of the steam supplementing pipe is communicated with the steam seal main pipe, the other end of the steam supplementing pipe is communicated with a steam supplementing port of the steam turbine, and a steam supplementing regulating valve is arranged on the steam supplementing pipe.
Preferably, the temperature of the steam in the low-pressure side steam seal pipe is 121-176 ℃.
Preferably, the steam seal system of the steam supplementing steam turbine unit further comprises a gas leakage pipeline, wherein the gas leakage pipeline is communicated with the high-pressure side steam flow channel through a high-pressure side gas leakage pipe, and the gas leakage pipeline is communicated with the low-pressure side steam flow channel through a low-pressure side gas leakage pipe.
Preferably, the steam sealing system of the steam supplementing turbine unit further comprises a condenser and a steam sealing cooler, wherein one of the condenser and the steam sealing cooler is arranged at one end of the steam sealing main pipe, and the other is arranged at one end of the air leakage pipeline.
As described above, the low-flow low-load operation method of the steam seal system of the steam turbine unit has the following beneficial effects: in the low-flow low-load operation method, one end of the steam supplementing pipe is communicated with the steam seal main pipe, and the other end of the steam supplementing pipe is communicated with a steam supplementing port of the steam turbine. When the running load of the turbine unit reaches a load point and the steam sealing system of the steam-supplementing turbine unit is in a self-sealing state, the steam supplementing pipe supplements redundant steam in the steam sealing main pipe into the through-flow structure of the turbine so as to increase the steam flow after the current supplementing stage, reduce the steam flow flowing out of the steam sealing main pipe and improve the thermal efficiency of the turbine unit; in other words, the steam supplementing pipe is opened, so that energy waste caused by the fact that redundant steam directly flows out of the gland sealing main pipe can be reduced, redundant steam is supplemented into the through-flow structure of the steam turbine, work of the redundant steam is achieved, and the operation efficiency of the steam turbine unit is improved. When the operation load of the turbine unit is lower than the load point and the steam sealing system of the steam supplementing turbine unit is in a non-self-sealing state, the steam supplementing pipe supplements steam to the next-last stator blade or the upstream side of the next-last stator blade of the turbine, so that the steam volume flow of a long blade area with higher vortex blasting danger degree can be improved, vortex blasting and overheat phenomenon in the long blade area are greatly avoided under the working condition of low flow and low load of the turbine unit, and the low-load operation capacity of the low-load operation safety of the turbine unit is improved. Therefore, the low-flow low-load operation method of the steam seal system of the steam-supplementing steam turbine unit can not only improve the operation efficiency of the steam turbine unit under the working condition of a load point, but also avoid vortex air blowing and overheating phenomena of the steam turbine unit under the working condition of low flow and low load, and improve the low-load operation capacity of the low-load operation safety of the steam turbine unit.
Drawings
FIG. 1 is a schematic view of a prior art flow field at a last stage blade of a steam turbine under rated operating conditions;
FIG. 2 is a schematic flow field diagram of a prior art turbine at a last stage blade during low load conditions;
fig. 3 is a schematic diagram of a steam seal system of a steam turbine unit according to the present invention.
Description of element reference numerals
01. Last stage blade
02. Ordered flow field
03. Turbulence flow field
1. Steam turbine
11. High pressure side steam flow channel
12. Low pressure side steam flow channel
2. Steam seal main pipe
21. High-pressure side steam seal pipe
22. Low pressure side steam seal pipe
23. First desuperheater
24. Overflow valve
3. Condenser
4. Steam supply system
41. High-pressure steam source control station
42. Auxiliary steam source control station
43. Steam supply pipe
431. Second desuperheater
5. Air leakage pipeline
51. High pressure side leakage pipe
52. Low pressure side leakage pipe
6. Steam seal cooler
7. Steam supplementing pipe
71. Steam supplementing regulating valve
8. Atmospheric pipe
81. Safety valve
Detailed Description
Further advantages and effects of the present invention will become apparent to those skilled in the art from the disclosure of the present invention, which is described by the following specific examples.
It should be understood that the structures, proportions, sizes, etc. shown in the drawings are for the purpose of understanding and reading the disclosure, and are not intended to limit the scope of the invention, which is defined by the appended claims, but rather by the claims, unless otherwise indicated, and unless otherwise indicated, all changes in structure, proportions, or otherwise, used by those skilled in the art, are included in the spirit and scope of the invention. Also, the terms such as "upper," "lower," "left," "right," "middle," and "a" and the like recited in the present specification are merely for descriptive purposes and are not intended to limit the scope of the invention, but are intended to provide relative positional changes or modifications without materially altering the technical context in which the invention may be practiced.
Effective measures for solving the problems in the background art: a sufficient volume flow of steam is allowed to flow over the last stage blades on the low pressure side of the turbine.
The working pressure of the condenser is reduced under the low-load working condition, so that the volume flow of the steam with the same mass is larger, and the flow field disturbance phenomenon caused by insufficient volume flow is eliminated. However, the back pressure is affected by the condensing capacity of the condenser, the type of the condenser is mainly determined by the rated working condition design value, and under the working condition of small volume flow, the steam discharge point becomes a dry steam area, so that the condensing capacity of the condenser is further reduced, and therefore, the method for reducing the back pressure is not easy to execute.
Increasing the steam flow increases the volumetric flow. The increase in steam flow means an increase in load on the turbine unit, which is contrary to the purpose of low load operation of the turbine unit. It is noted that the last stage long blade is the main area where the problems of vortex water rinsing and blast overheating occur (the blast friction function is positively correlated with the linear speed of the rotating machine, the diameter of the last stage blade is large, the linear speed is high, and the friction function is strongest), so that on the premise of ensuring low-load operation, how to increase the volume flow of steam at the last stage blade is the object of the invention.
Based on the above, as shown in fig. 3, the invention provides a low-flow low-load operation method of a steam seal system of a steam turbine unit, which comprises the following steps:
when the operation load of the turbine unit reaches a load point (in general, the load point of the turbine unit is 20% -50% of rated load) and the steam sealing system of the steam supplementing turbine unit is in a self-sealing state, the steam supplementing pipe 7 supplements redundant steam in the steam sealing main pipe 2 to the through-flow structure of the turbine 1;
when the operation load of the turbine unit is lower than the load point and the steam sealing system of the steam supplementing turbine unit is in a non-self-sealing state, the high-pressure steam source or the starting steam source supplies steam to the steam sealing main pipe 2 to maintain the pressure of the steam sealing main pipe 2 constant, and the steam supplementing pipe 7 supplements the steam to the next-last stator blade or the upstream side of the next-last stator blade of the turbine 1.
In the low-flow low-load operation method, one end of the steam supplementing pipe 7 is communicated with the gland sealing main pipe 2, and the other end of the steam supplementing pipe 7 is communicated with a steam supplementing port of the steam turbine 1. When the running load of the turbine unit reaches a load point and the steam sealing system of the steam-supplementing turbine unit is in a self-sealing state, the steam supplementing pipe 7 supplements redundant steam in the steam sealing main pipe 2 to the through-flow structure of the turbine 1 so as to increase the steam flow after the current supplementing stage, reduce the steam quantity flowing out of the steam sealing main pipe 2 and improve the thermal efficiency of the turbine unit; in other words, by opening the steam supplementing pipe 7, the energy waste caused by the fact that the redundant steam directly flows out of the gland sealing main pipe 2 can be reduced, the redundant steam is supplemented into the through-flow structure of the steam turbine 1, the work of the redundant steam is realized, and the operation efficiency of the steam turbine unit is improved. When the operation load of the turbine unit is lower than the load point and the steam sealing system of the steam supplementing turbine unit is in a non-self-sealing state, the steam supplementing pipe 7 supplements steam (for example, the temperature of the steam is 121-176 degrees and the air pressure is 0.13 MPa) to the last-stage stator blade or the upstream side of the last-stage stator blade of the turbine 1, so that the steam volume flow of a long blade area with higher vortex air blast risk degree can be improved, vortex air blast and overheat phenomenon in the long blade area (for example, the last-stage blade area) are greatly avoided under the working condition of low flow and low load of the turbine unit, and the low load operation capacity of the turbine unit is improved.
Therefore, the low-flow low-load operation method of the steam seal system of the steam-supplementing steam turbine unit can not only improve the operation efficiency of the steam turbine unit under the working condition of a load point, but also avoid vortex air blowing and overheating phenomena of the steam turbine unit under the working condition of low flow and low load, and improve the low-load operation capacity of the low-load operation safety of the steam turbine unit.
The low-flow low-load operation method further comprises the following steps: when the steam turbine unit is turned on, vacuumized and started, steam supplied by a starting steam source flows into the gland box main pipe 2 through the auxiliary steam source control station 42, and the starting regulating valve of the auxiliary steam source control station 42 regulates the pressure of the gland box main pipe 2 to be 0.125-0.130 MPa; when the turbine unit starts the flushing rotation by adopting medium parameters and the pressure of main steam is increased to 3.5-5 MPa, the high-pressure steam source replaces the starting steam source to supply steam to the gland box main pipe 2, and the high-pressure regulating valve of the high-pressure steam source control station 41 maintains the pressure of the gland box main pipe 2 to be 0.125-0.130 MPa; or the starting steam source continues to supply steam to the gland box main pipe 2 through the auxiliary steam source control station 42; when the operation load of the turbine unit reaches 27% -33% of the rated load, the steam leakage amount of the high-pressure side of the turbine 1 exceeds the steam supply amount required by the low-pressure side of the turbine 1; when the pressure of the gland sealing main pipe 2 is increased to 0.130-0.135 MPa, the overflow valve 24 is opened, the auxiliary steam source control station 42 is closed, the steam sealing system of the steam supplementing steam turbine unit enters a self-sealing state, and the overflow valve 24 maintains the pressure of the gland sealing main pipe 2 to 0.130-0.135 MPa.
The temperature difference between the steam in the steam supplementing pipe 7 and the steam in the steam turbine 1 is 30 to 50 Kelvin and the pressure difference is 0.05 to 0.2MPa.
Before the turbine unit starts, or during the process of the impact rotation and the load lifting, the steam supplementing regulating valve 71 arranged on the steam supplementing pipe 7 is in a fully closed state.
The steam sealing system of the steam supplementing turbine unit comprises:
the high-pressure side of the steam turbine 1 is provided with a high-pressure side steam flow channel 11, and the low-pressure side of the steam turbine 1 is provided with a low-pressure side steam flow channel 12;
the steam seal main pipe 2 is communicated with the high-pressure side steam flow channel 11 through a high-pressure side steam seal pipe 21, the steam seal main pipe 2 is communicated with the low-pressure side steam flow channel 12 through a low-pressure side steam seal pipe 22, and the steam seal main pipe 2 is provided with a first desuperheater 23 and an overflow valve 24;
the steam supply system 4, the steam supply system 4 comprises a high-pressure steam source control station 41, an auxiliary steam source control station 42, a steam supply pipe 43, a high-pressure steam source and a starting steam source, the high-pressure steam source control station 41 and the auxiliary steam source control station 42 are mutually connected in parallel and then are communicated with the steam seal main pipe 2 through the steam supply pipe 43, a second attemperator 431 is arranged on the steam supply pipe 43, the high-pressure steam source is connected with the high-pressure steam source control station 41, and the starting steam source is connected with the auxiliary steam source control station 42;
and one end of the steam supplementing pipe 7 is communicated with the gland sealing main pipe 2, the other end of the steam supplementing pipe 7 is communicated with a steam supplementing port of the steam turbine 1, and the steam supplementing pipe 7 is provided with a steam supplementing regulating valve 71.
The temperature of the steam in the low-pressure side gland sealing pipe 22 is 121-176 ℃.
The steam seal system of the steam supplementing steam turbine unit further comprises a gas leakage pipeline 5, the gas leakage pipeline 5 is communicated with the high-pressure side steam flow channel 11 through a high-pressure side gas leakage pipe 51, and the gas leakage pipeline 5 is communicated with the low-pressure side steam flow channel 12 through a low-pressure side gas leakage pipe 52.
The steam sealing system of the steam supplementing steam turbine unit further comprises a condenser 3 and a steam sealing cooler 6, wherein one of the condenser 3 and the steam sealing cooler 6 is arranged at one end of the steam sealing main pipe 2, and the other is arranged at one end of the air leakage pipeline 5.
In order to facilitate the control of the steam compensating adjusting valve 71, the steam sealing system of the steam compensating turbine unit further comprises a control system, and the steam compensating adjusting valve 71 is in communication connection with the control system. The make-up valve 71 may be manually commanded or commanded by a control system and may be continuously adjusted.
In order to avoid the excessive pressure in the gland box main pipe 2, the gland box system of the steam-supplementing turbine unit further comprises an air pipe 8 communicated with the gland box main pipe 2, and a safety valve 81 is arranged on the air pipe 8. In addition, when one end of the gland box pipe 2 is connected to the condenser 3, the above-mentioned overflow valve 24 is disposed on the gland box pipe 2 near the condenser 3.
In summary, the invention not only can improve the operation efficiency of the turbine unit under the working condition of the load point, but also can avoid vortex blast and overheat phenomena of the turbine unit under the working condition of low flow and low load, and improve the low load operation capability of the turbine unit for low load operation safety. Therefore, the invention effectively overcomes various defects in the prior art and has high industrial utilization value.
The above embodiments are merely illustrative of the principles of the present invention and its effectiveness, and are not intended to limit the invention. Modifications and variations may be made to the above-described embodiments by those skilled in the art without departing from the spirit and scope of the invention. Accordingly, it is intended that all equivalent modifications and variations of the invention be covered by the claims, which are within the ordinary skill of the art, be within the spirit and scope of the present disclosure.
Claims (9)
1. The low-flow low-load operation method of the steam seal system of the steam-supplementing turbine unit is characterized by comprising the following steps of:
when the running load of the turbine unit reaches a load point and the steam sealing system of the steam supplementing turbine unit is in a self-sealing state, the steam supplementing pipe (7) supplements redundant steam in the steam sealing main pipe (2) into a through-flow structure of the turbine (1);
when the operation load of the turbine unit is lower than the load point and the steam sealing system of the steam supplementing turbine unit is in a non-self-sealing state, a high-pressure steam source or a starting steam source supplies steam to the steam sealing main pipe (2) to maintain the constant pressure of the steam sealing main pipe (2), and the steam supplementing pipe (7) supplements the steam to the next-last stator blade or the upstream side of the next-last stator blade of the turbine (1);
the steam sealing system of the steam supplementing turbine unit comprises:
the steam turbine comprises a steam turbine (1), wherein a high-pressure side steam flow channel (11) is arranged on the high-pressure side of the steam turbine (1), and a low-pressure side steam flow channel (12) is arranged on the low-pressure side of the steam turbine (1);
the steam seal main pipe (2), the steam seal main pipe (2) is communicated with the high-pressure side steam flow channel (11) through the high-pressure side steam seal pipe (21), the steam seal main pipe (2) is communicated with the low-pressure side steam flow channel (12) through the low-pressure side steam seal pipe (22), and the steam seal main pipe (2) is provided with a first desuperheater (23) and an overflow valve (24);
the steam supply system (4), the steam supply system (4) comprises a high-pressure steam source control station (41), an auxiliary steam source control station (42), a steam supply pipe (43), a high-pressure steam source and a starting steam source, the high-pressure steam source control station (41) and the auxiliary steam source control station (42) are mutually connected in parallel and then are communicated with the steam seal main pipe (2) through the steam supply pipe (43), a second desuperheater (431) is arranged on the steam supply pipe (43), the high-pressure steam source is connected with the high-pressure steam source control station (41), and the starting steam source is connected with the auxiliary steam source control station (42);
and one end of the steam supplementing pipe (7) is communicated with the gland sealing main pipe (2), the other end of the steam supplementing pipe (7) is communicated with a steam supplementing port of the steam turbine (1), and a steam supplementing regulating valve (71) is arranged on the steam supplementing pipe (7).
2. The method for low flow, low load operation of a steam seal system of a steam turbine of a steam make-up turbine of claim 1, further comprising the steps of:
when the steam turbine unit is turned on, vacuumized and started, steam supplied by a starting steam source flows into the steam seal main pipe (2) through the auxiliary steam source control station (42), and the starting regulating valve of the auxiliary steam source control station (42) regulates the pressure of the steam seal main pipe (2) to be 0.125-0.130 MPa.
3. The method for low flow, low load operation of a steam seal system of a steam turbine of a steam make-up turbine of claim 1, further comprising the steps of:
when the turbine unit starts the flushing rotation by adopting medium parameters and the pressure of main steam is increased to 3.5-5 MPa, a high-pressure steam source replaces a starting steam source to supply steam to the gland box main pipe (2), and a high-pressure regulating valve of a high-pressure steam source control station (41) maintains the pressure of the gland box main pipe (2) to be 0.125-0.130 MPa; or the starting steam source continues to supply steam to the gland main pipe (2) through the auxiliary steam source control station (42).
4. The method for low flow, low load operation of a steam seal system of a steam turbine of a steam make-up turbine of claim 1, further comprising the steps of:
when the operation load of the turbine unit reaches 27% -33% of rated load, the steam leakage amount of the high-pressure side of the turbine (1) exceeds the steam supply amount required by the low-pressure side of the turbine (1); when the pressure of the gland sealing main pipe (2) is increased to 0.130-0.135 MPa, the overflow valve (24) is opened, the auxiliary steam source control station (42) is closed, the gland sealing system of the steam supplementing turbine unit enters a self-sealing state, and the overflow valve (24) maintains the pressure of the gland sealing main pipe (2) to 0.130-0.135 MPa.
5. The low flow rate and low load operation method of a steam seal system of a steam turbine unit of a steam make-up type according to claim 1, wherein: the temperature difference between the steam in the steam supplementing pipe (7) and the steam in the steam turbine (1) is 30-50 Kelvin and the pressure difference is 0.05-0.2 MPa.
6. The low flow rate and low load operation method of a steam seal system of a steam turbine unit of a steam make-up type according to claim 1, wherein: before the turbine unit is started, or in the processes of flushing and lifting load, a steam supplementing regulating valve (71) arranged on a steam supplementing pipe (7) is in a fully closed state.
7. The low flow rate and low load operation method of a steam seal system of a steam turbine unit of a steam make-up type according to claim 1, wherein: the temperature of the steam in the low-pressure side steam seal pipe (22) is 121-176 ℃.
8. The low flow rate and low load operation method of a steam seal system of a steam turbine unit of a steam make-up type according to claim 1, wherein: the steam seal system of the steam supplementing steam turbine unit further comprises a gas leakage pipeline (5), the gas leakage pipeline (5) is communicated with the high-pressure side steam flow channel (11) through a high-pressure side gas leakage pipe (51), and the gas leakage pipeline (5) is communicated with the low-pressure side steam flow channel (12) through a low-pressure side gas leakage pipe (52).
9. The low flow rate and low load operation method of a steam seal system of a steam turbine unit of claim 8, wherein: the steam sealing system of the steam supplementing turbine unit further comprises a condenser (3) and a steam sealing cooler (6), wherein one of the condenser (3) and the steam sealing cooler (6) is arranged at one end of the steam sealing main pipe (2) and the other is arranged at one end of the air leakage pipeline (5).
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| Application Number | Priority Date | Filing Date | Title |
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| CN202011009639.8A CN114251135B (en) | 2020-09-23 | 2020-09-23 | Low-flow low-load operation method of steam seal system of steam supplementing turbine unit |
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| CN202011009639.8A CN114251135B (en) | 2020-09-23 | 2020-09-23 | Low-flow low-load operation method of steam seal system of steam supplementing turbine unit |
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| CN114251135A CN114251135A (en) | 2022-03-29 |
| CN114251135B true CN114251135B (en) | 2024-03-19 |
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| CN202011009639.8A Active CN114251135B (en) | 2020-09-23 | 2020-09-23 | Low-flow low-load operation method of steam seal system of steam supplementing turbine unit |
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