CN114251135A - Low-flow low-load operation method of steam seal system of steam supplementing type steam turbine unit - Google Patents
Low-flow low-load operation method of steam seal system of steam supplementing type steam turbine unit Download PDFInfo
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- 238000007789 sealing Methods 0.000 claims abstract description 20
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- 238000013021 overheating Methods 0.000 abstract description 8
- 238000007664 blowing Methods 0.000 description 7
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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
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Abstract
The invention provides a small-flow low-load operation method of a steam seal system of a steam supplementing type steam turbine unit, which comprises the following steps: when the operation load of the steam turbine unit reaches a load point and a steam seal system of the steam supplementing type steam turbine unit is in a self-sealing state, the steam supplementing pipe supplements redundant steam in the steam seal main pipe into a through-flow structure of the steam turbine; when the operating load of the steam turbine unit is lower than a load point and a steam seal system of the steam supplementing type steam turbine unit is in a non-self-sealing state, a high-pressure steam source or a starting steam source supplies steam to a steam seal main pipe to maintain the pressure of the steam seal main pipe constant, and the steam supplementing pipe supplements the steam to the upstream side of the next-to-last stage stationary blade or the next-to-last stage stationary blade of the steam turbine. The invention can not only improve the operation efficiency of the steam turbine unit under the working condition of the load point, but also avoid the phenomena of vortex blast and overheating of the steam turbine unit under the working condition of low flow and low load, thereby improving the low-load operation capability of the low-load operation safety of the steam turbine unit.
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 compensating type turbine set.
Background
The low-load operation capacity 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 and low-load operation capacity of a unit. Especially, under the background environment that the traditional thermal power generation energy is required to give way for clean power energy at present, the low-load operation capacity of the traditional power station steam turbine is more actively concerned.
As shown in fig. 1, in a rated condition, the flow rate of the steam flowing through the last stage blade 01 of the steam turbine reaches a rated value, and a stable ordered flow field 02 is formed inside the steam turbine. As shown in fig. 2, when the unit operates at a low load, the volume flow of the steam at the last stage blade 01 is less than the design working condition, the streamline begins to twist, when the volume flow is reduced to a certain value, the root of the movable blade is out of flow, negative velocity components occur in a reverse flow region, the steam flows backwards towards the movable blade, the steam outlet edge of the root of the movable blade is flushed with water, and the interaction of the steam flow in the negative velocity direction and the main flow forms an annular vortex, namely a turbulent flow field 03 is formed inside the impeller. The harm and adverse effect on the unit are as follows: (1) the eddy current region can cause strong eddy current loss, so that the stage efficiency is reduced; (2) the movable blades can generate strong vibration, so that the dynamic stress is increased, and the safety of the unit is threatened; (3) the movable blades do friction work on through-flow steam to generate blast air, so that exhaust steam is overheated, and safety of the movable blades and the condenser is not good. Studies have shown that the degree of adverse effects on the above problem is related to the volume flow of steam in the last stage blade zone, with smaller volumes of steam having higher degrees of adverse effects.
Disclosure of Invention
In view of the above drawbacks of the prior art, the technical problem to be solved by the present invention is to provide a low flow and low load operation method for a steam seal system of a steam compensating turbine unit, which can not only improve the operation efficiency of the turbine unit under the working condition of a load point, but also avoid the formation of vortex blowing and overheating of the turbine unit under the working condition of low flow and low load, and improve the low load operation capability of the low load operation safety of the turbine unit.
In order to solve the technical problem, the invention provides a low-flow low-load operation method of a steam seal system of a steam compensating type steam turbine unit, which comprises the following steps:
when the operation load of the steam turbine unit reaches a load point and a steam seal system of the steam supplementing type steam turbine unit is in a self-sealing state, the steam supplementing pipe supplements redundant steam in the steam seal main pipe into a through-flow structure of the steam turbine;
when the operating load of the steam turbine unit is lower than a load point and a steam seal system of the steam supplementing type steam turbine unit is in a non-self-sealing state, a high-pressure steam source or a starting steam source supplies steam to a steam seal main pipe to maintain the pressure of the steam seal main pipe constant, and the steam supplementing pipe supplements the steam to the upstream side of the next-to-last stage stationary blade or the next-to-last stage stationary blade of the steam turbine.
Preferably, the method further comprises the following steps:
when the steam turbine unit is turned, vacuumized and started, steam supplied by a starting steam source flows into the steam seal main pipe through the auxiliary steam source control station, and the pressure of the steam seal main pipe is adjusted to be 0.125-0.130 MPa by a starting adjusting valve of the auxiliary steam source control station.
Preferably, the method further comprises the following steps:
when the steam turbine unit is started to rotate 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 a steam seal main pipe, and a high-pressure regulating valve of a high-pressure steam source control station maintains the pressure of the steam seal main pipe to be 0.125-0.130 MPa; or starting the steam source to continuously supply steam to the steam seal main pipe through the auxiliary steam source control station.
Preferably, the method further comprises the following steps:
when the operation load of the steam turbine unit reaches 27% -33% of the rated load, the steam quantity leaked from the high-pressure side of the steam turbine exceeds the steam supply quantity required by the low-pressure side of the steam turbine; when the pressure of the steam seal main pipe is increased to 0.130-0.135 MPa, the overflow valve is opened, the auxiliary steam source control station is closed, the steam seal system of the steam supplementing type steam turbine unit enters a self-sealing state, and the pressure of the steam seal main pipe is maintained to be 0.130-0.135 MPa by the overflow valve.
Preferably, the temperature difference between the steam in the steam compensating pipe and the steam in the steam turbine is 30-50 Kelvin, and the pressure difference is 0.05-0.2 MPa.
Preferably, before the steam turbine set is started or during the process of running and load rising, the steam supplementing regulating valve arranged on the steam supplementing pipe is in a full-closed state.
Preferably, the steam seal system of the steam supplementing type steam turbine unit comprises:
the high-pressure side of the steam turbine is provided with a high-pressure side steam runner, and the low-pressure side of the steam turbine is provided with a low-pressure side steam runner;
the steam seal main pipe is communicated with the high-pressure side steam flow channel through a high-pressure side steam seal pipe, the steam seal main pipe is communicated with the low-pressure side steam flow channel through a 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, the high-pressure steam source control station and the auxiliary steam source control station are connected in parallel and then 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 supply pipe is communicated with the steam seal main pipe, the other end of the steam supply pipe is communicated with a steam supply port of the steam turbine, and a steam supply adjusting valve is arranged on the steam supply pipe.
Preferably, the temperature of steam in the low-pressure side steam seal pipe is 121-176 ℃.
Preferably, the steam seal system of the steam supplementing type steam turbine unit further comprises a gas leakage pipeline, the gas leakage pipeline is communicated with the high-pressure steam pipe through a high-pressure side gas leakage pipe, and the gas leakage pipeline is communicated with the low-pressure steam pipe through a low-pressure side gas leakage pipe.
Preferably, the steam seal system of the steam supplementing type steam turbine unit further comprises a condenser and a steam seal cooler, wherein one of the condenser and the steam seal cooler is arranged at one end of the steam seal main pipe, and the other one of the condenser and the steam seal cooler is arranged at one end of the gas leakage pipeline.
As described above, the low-flow low-load operation method of the steam seal system of the steam compensating type steam turbine unit of the invention has the following beneficial effects: in the low-flow low-load operation method, one end of the steam supply pipe is communicated with the steam seal main pipe, and the other end of the steam supply pipe is communicated with a steam supply port of the steam turbine. When the operating load of the steam turbine unit reaches a load point and a steam seal system of the steam-supplementing type steam turbine unit is in a self-sealing state, the steam-supplementing pipe supplements redundant steam in the steam seal main pipe into a through-flow structure of the steam turbine so as to increase the steam flow after the current supplement stage, reduce the steam flow flowing out of the steam seal main pipe and improve the heat efficiency of the steam turbine unit; in other words, the energy waste caused by the fact that the redundant steam directly flows out of the steam seal main pipe can be reduced by opening the steam supplementing pipe, the 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 steam turbine unit is lower than a load point and a steam seal system of the steam supplementing type steam turbine unit is in a non-self-sealing state, steam is supplemented into the upstream side of the penultimate stationary blade or the penultimate stationary blade of the steam turbine through the steam supplementing pipe, so that the steam volume flow of the long blade area with high vortex blowing danger degree can be improved, vortex blowing and overheating phenomena in the long blade area are greatly avoided under the low-flow and low-load working condition of the steam turbine unit, and the low-load operation capacity of the low-load operation safety of the steam turbine unit is improved. Therefore, the low-flow low-load operation method of the steam seal system of the steam compensating type steam turbine unit can improve the operation efficiency of the steam turbine unit under the working condition of a load point, can avoid the phenomena of vortex blowing and overheating of the steam turbine unit under the working condition of low flow and low load, and improves the low-load operation capability 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 the last stage blade of a steam turbine at rated operating conditions;
FIG. 2 is a schematic view of a prior art flow field at the last stage blade of a steam turbine under low load conditions;
fig. 3 is a schematic view of a steam seal system of the steam turbine unit according to the present invention.
Description of the element reference numerals
01 last stage blade
02 ordered flow field
03 turbulent 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 gland sealing pipe
22 low pressure side gland sealing pipe
23 first desuperheater
24 overflow valve
3 steam 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 air leakage pipe
52 low pressure side leakage pipe
6 steam seal cooler
7 steam supply pipe
71 steam compensating regulating valve
8 atmosphere pipe
81 safety valve
Detailed Description
The following description of the embodiments of the present invention is provided for illustrative purposes, and other advantages and effects of the present invention will become apparent to those skilled in the art from the present disclosure.
It should be understood that the structures, ratios, sizes, and the like shown in the drawings are only used for matching the disclosure of the present disclosure, and are not used for limiting the conditions that the present disclosure can be implemented, so that the present disclosure is not limited to the technical essence, and any structural modifications, ratio changes, or size adjustments should still fall within the scope of the present disclosure without affecting the efficacy and the achievable purpose of the present disclosure. In addition, the terms "upper", "lower", "left", "right", "middle" and "one" used in the present specification are for clarity of description, and are not intended to limit the scope of the present invention, and the relative relationship between the terms and the terms is not to be construed as a scope of the present invention.
Effective measures for solving the problems in the background art: allowing a sufficient volumetric flow of steam to flow through 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 quality can be larger, and the phenomenon of flow field disorder caused by insufficient volume flow is eliminated. However, the backpressure is affected by the condensing capacity of the condenser, the type selection of the condenser is mainly determined by a rated working condition design value, and under the working condition of small volume flow, a steam exhaust point becomes a dry steam area, so that the condensing capacity of the condenser is further reduced, and therefore, the backpressure reducing method is not easy to implement.
Increasing the steam flow increases the volumetric flow. An increase in steam flow means an increase in the load on the turbine unit, which is contrary to the objective of low load operation of the turbine unit. It is worth noting that the last-stage long blade is the main area where the problems of whirlpool water washing and blast overheating occur (the blast friction work capacity is in positive correlation with the linear speed of the rotating machinery, the last-stage blade has a large diameter, the linear speed is high, and the friction work capacity is strongest), so that the purpose of the invention is how to increase the volume flow of the steam at the last-stage blade under the premise of ensuring low-load operation.
Based on this, as shown in fig. 3, the invention provides a low-flow low-load operation method of a steam seal system of a steam supplementing type steam turbine unit, which comprises the following steps:
when the operating load of the steam turbine unit reaches a load point (generally, the load point of the steam turbine unit is 20% -50% of a rated load) and a steam seal system of the steam supplementing type steam turbine unit is in a self-sealing state, the steam supplementing pipe 7 supplements redundant steam in the steam seal main pipe 2 into a through-flow structure of the steam turbine 1;
when the operating load of the steam turbine unit is lower than the load point and the steam seal system of the steam supplementing type steam turbine unit is in a non-self-sealing state, a high-pressure steam source or a starting steam source supplies steam to the steam seal main pipe 2 to maintain the pressure of the steam seal main pipe 2 constant, and the steam supplementing pipe 7 supplements the steam to the upstream side of the next-to-last stage stationary blade or the next-to-last stage stationary blade of the steam turbine 1.
In the low-flow low-load operation method, one end of the steam supply pipe 7 is communicated with the steam seal main pipe 2, and the other end of the steam supply pipe 7 is communicated with a steam supply port of the steam turbine 1. When the operation load of the steam turbine unit reaches a load point and a steam seal system of the steam-supplementing type steam turbine unit is in a self-sealing state, the steam-supplementing pipe 7 supplements redundant steam in the steam seal main pipe 2 into a through-flow structure of the steam turbine 1 so as to increase the steam flow after the current supplement stage, reduce the steam flow flowing out of the steam seal main pipe 2 and improve the heat efficiency of the steam turbine unit; in other words, the energy waste caused by the fact that the redundant steam directly flows out of the steam seal main pipe 2 can be reduced by opening the steam supplementing pipe 7, 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 steam turbine unit is lower than a load point and a steam seal system of the steam supplementing type steam turbine unit is in a non-self-sealing state, steam (for example, the temperature of the steam is 121-176 ℃ and the air pressure is 0.13MPa) is supplemented into the upstream side of the penultimate stator blade or the penultimate stator blade of the steam turbine 1 by the steam supplementing pipe 7, so that the steam volume flow of a long blade area with high vortex blowing danger degree can be improved, vortex blowing and overheating phenomena in the long blade area (for example, the last blade area) are greatly avoided under the low-flow and low-load working condition of the steam turbine unit, and the low-load operation capacity of the low-load operation safety of the steam turbine unit is improved.
Therefore, the low-flow low-load operation method of the steam seal system of the steam compensating type steam turbine unit can improve the operation efficiency of the steam turbine unit under the working condition of a load point, can avoid the phenomena of vortex blowing and overheating of the steam turbine unit under the working condition of low flow and low load, and improves the low-load operation capability of the low-load operation safety of the steam turbine unit.
The small flow low load operation method further comprises the following steps: when the steam turbine unit is turned, 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 pressure of the steam seal main pipe 2 is adjusted to be 0.125-0.130 MPa by a starting adjusting valve of the auxiliary steam source control station 42; when the steam turbine unit is started to rotate by adopting medium parameters and the pressure of main steam is increased to 3.5-5 MPa, the high-pressure steam source replaces a starting steam source to supply steam to the steam seal main pipe 2, and the high-pressure regulating valve of the high-pressure steam source control station 41 maintains the pressure of the steam seal main pipe 2 to be 0.125-0.130 MPa; or, starting the steam source to continuously supply steam to the steam seal main pipe 2 through the auxiliary steam source control station 42; when the operation load of the steam turbine unit reaches 27% -33% of the rated load, the steam quantity leaked from the high-pressure side of the steam turbine 1 exceeds the steam supply quantity required by the low-pressure side of the steam turbine 1; when the pressure of the steam seal 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 seal system of the steam supplementing type steam turbine unit enters a self-sealing state, and the overflow valve 24 maintains the pressure of the steam seal main pipe 2 to be 0.130-0.135 MPa.
The temperature difference between the steam in the steam supply pipe 7 and the steam in the steam turbine 1 is 30 to 50 Kelvin, and the pressure difference is 0.05 to 0.2 MPa.
Before the steam turbine set is started or in the process of impulse and load rise, the steam supply regulating valve 71 arranged on the steam supply pipe 7 is in a full-closed state.
The steam seal system of the steam supplementing type steam turbine unit comprises:
the high-pressure side of the steam turbine 1 is provided with a high-pressure side steam runner 11, and the low-pressure side of the steam turbine 1 is provided with a low-pressure side steam runner 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 a first desuperheater 23 and an overflow valve 24 are arranged on the steam seal main pipe 2;
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, wherein the high-pressure steam source control station 41 and the auxiliary steam source control station 42 are connected in parallel and then 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 steam seal 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.
The temperature of the steam in the low-pressure side steam seal pipe 22 is 121-176 ℃.
The steam seal system of the steam supplementing type steam turbine unit further comprises a gas leakage pipeline 5, wherein the gas leakage pipeline 5 is communicated with the high-pressure steam pipe 11 through a high-pressure side gas leakage pipe 51, and the gas leakage pipeline 5 is communicated with the low-pressure steam pipe 12 through a low-pressure side gas leakage pipe 52.
The steam seal system of the steam supplementing type steam turbine unit further comprises a condenser 3 and a steam seal cooler 6, wherein one of the condenser 3 and the steam seal cooler 6 is arranged at one end of the steam seal main pipe 2, and the other one of the condenser 3 and the steam seal cooler 6 is arranged at one end of the air leakage pipeline 5.
In order to facilitate control of the steam supply regulating valve 71, the steam seal system of the steam supply type steam turbine unit further comprises a control system, and the steam supply regulating valve 71 is in communication connection with the control system. The make-up damper 71 may receive manual commands or commands from the control system and may be continuously adjustable.
In order to avoid the overlarge pressure in the gland sealing main pipe 2, the gland sealing system of the steam supplementing type steam turbine unit further comprises an atmosphere pipe 8 communicated with the gland sealing main pipe 2, and a safety valve 81 is arranged on the atmosphere pipe 8. When one end of the gland header 2 is connected to the condenser 3, the relief valve 24 is disposed on the gland header 2 near the condenser 3.
In conclusion, the invention can not only improve the operation efficiency of the steam turbine unit under the working condition of the load point, but also avoid the phenomena of vortex blast and overheating of the steam turbine unit under the working condition of low flow and low load, thereby improving the low-load operation capability of the low-load operation safety of the steam turbine unit. Therefore, the invention effectively overcomes various defects in the prior art and has high industrial utilization value.
The foregoing embodiments are merely illustrative of the principles and utilities of the present invention and are not intended to limit the invention. Any person skilled in the art can modify or change the above-mentioned embodiments without departing from the spirit and scope of the present invention. Accordingly, it is intended that all equivalent modifications or changes which can be made by those skilled in the art without departing from the spirit and technical spirit of the present invention be covered by the claims of the present invention.
Claims (10)
1. A small-flow low-load operation method of a steam seal system of a steam compensating type steam turbine unit is characterized by comprising the following steps:
when the operation load of the steam turbine unit reaches a load point and a steam seal system of the steam supplementing type steam turbine unit is in a self-sealing state, the steam supplementing pipe (7) supplements redundant steam in the steam seal main pipe (2) into a through-flow structure of the steam turbine (1);
when the operating load of the steam turbine unit is lower than a load point and a steam seal system of the steam supplementing type steam turbine unit is in a non-self-sealing state, a high-pressure steam source or a starting steam source supplies steam to a steam seal main pipe (2) to maintain the pressure of the steam seal main pipe (2) constant, and a steam supplementing pipe (7) supplements the steam to the upstream side of a next-last stage static blade or a next-last stage static blade of the steam turbine (1).
2. The method of claim 1, further comprising the steps of:
when the steam turbine unit is turned, 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 pressure of the steam seal main pipe (2) is adjusted to be 0.125-0.130 MPa by the starting adjusting valve of the auxiliary steam source control station (42).
3. The method of claim 1, further comprising the steps of:
when the steam turbine unit is started to rotate 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 steam seal main pipe (2), and a high-pressure regulating valve of a high-pressure steam source control station (41) maintains the pressure of the steam seal main pipe (2) at 0.125-0.130 MPa; or the steam source is started to continuously supply steam to the steam seal main pipe (2) through the auxiliary steam source control station (42).
4. The method of claim 1, further comprising the steps of:
when the operation load of the steam turbine unit reaches 27% -33% of the rated load, the steam quantity leaked from the high-pressure side of the steam turbine (1) exceeds the steam supply quantity required by the low-pressure side of the steam turbine (1); when the pressure of the steam seal 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 seal system of the steam supplementing type steam turbine unit enters a self-sealing state, and the overflow valve (24) maintains the pressure of the steam seal main pipe (2) to be 0.130-0.135 MPa.
5. The method for operating a steam seal system of a steam turbine plant with low flow and low load according to claim 1, wherein the method comprises the following steps: 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 method for operating a steam seal system of a steam turbine plant with low flow and low load according to claim 1, wherein the method comprises the following steps: before the steam turbine unit is started or in the processes of impact rotation and load rise, a steam supplementing regulating valve (71) arranged on a steam supplementing pipe (7) is in a fully closed state.
7. The method of claim 1, wherein the steam turbine unit gland seal system comprises:
the steam turbine (1), the high pressure side of the steam turbine (1) is provided with a high pressure side steam runner (11), and the low pressure side of the steam turbine (1) is provided with a low pressure side steam runner (12);
the steam seal device comprises a steam seal main pipe (2), wherein the steam seal main pipe (2) is communicated with a 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 a low-pressure side steam flow channel (12) through a low-pressure side steam seal pipe (22), and a first desuperheater (23) and an overflow valve (24) are arranged on the steam seal main pipe (2);
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 connected in parallel and then 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);
one end of the steam supply pipe (7) is communicated with the steam seal main pipe (2), the other end of the steam supply pipe (7) is communicated with a steam supply port of the steam turbine (1), and a steam supply adjusting valve (71) is arranged on the steam supply pipe (7).
8. The method of claim 7, wherein the method comprises the steps of: the temperature of steam in the low-pressure side steam seal pipe (22) is 121-176 ℃.
9. The method of claim 7, wherein the method comprises the steps of: the steam seal system of the steam supplementing type steam turbine unit further comprises a gas leakage pipeline (5), the gas leakage pipeline (5) is communicated with the high-pressure steam pipe (11) through a high-pressure side gas leakage pipe (51), and the gas leakage pipeline (5) is communicated with the low-pressure steam pipe (12) through a low-pressure side gas leakage pipe (52).
10. The method of claim 9 for low flow and low load operation of a steam seal system of a steam make-up steam turbine plant, wherein: the steam seal system of the steam supplementing type steam turbine unit further comprises a condenser (3) and a steam seal cooler (6), wherein one of the condenser (3) and the steam seal cooler (6) is arranged at one end of the steam seal main pipe (2) and the other end of the steam seal main pipe is arranged at one end of the gas 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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| 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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| CN120042662A (en) * | 2025-04-25 | 2025-05-27 | 西安交通大学 | Steam compensation structure for reducing the airflow excitation force of low-pressure stage of steam turbine during deep peak regulation |
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