A kind of increases front cylinder and high-low pressure steam ejector thermal power generating unit

Abstract

This invention discloses a thermal power unit with an added pre-cylinder and high and low pressure steam ejectors. The outlet of the main steam pipeline is connected to the inlet of the pre-cylinder via a newly added high-pressure main steam valve and a newly added high-pressure regulating valve. The outlet of the main steam pipeline is also connected to the inlet of the high-pressure cylinder via the high-pressure main steam valve and the high-pressure regulating valve. The outlet of the main steam pipeline is connected to the inlet of the reheater via a high-pressure bypass valve. The first extraction port of the pre-cylinder is connected to the inlet of the high-pressure steam ejector. The outlet of the high-pressure steam ejector is connected to the inlet of the reheater via a first desuperheater. The second extraction port of the pre-cylinder is connected to the inlet of the low-pressure steam ejector. The outlet of the low-pressure steam ejector is connected to the industrial steam supply pipeline via a second desuperheater. The outlet of the reheater is connected to the inlets of both the high-pressure and low-pressure steam ejectors. This generator unit features strong peak-shaving capacity, good low-load economy, fast load response, and flexible steam and heat supply.

Description

Technical Field

[0001] This invention belongs to the field of thermal power generation and relates to a thermal power unit with an added front cylinder and high and low pressure steam injectors. Background Technology

[0002] With the increasing proportion of new energy power generation, higher requirements are placed on the peak-shaving capacity and operational flexibility of coal-fired power units. However, traditional coal-fired power generating units are designed with a greater emphasis on efficient operation under rated load. When they are under low load conditions, they face a series of economic and safety challenges, among which steam throttling losses are a particularly prominent issue.

[0003] In existing technologies, generating units primarily control the amount and parameters of steam entering the high-pressure cylinder through main steam valves and regulating valves. During low-load operation, to reduce steam flow and pressure, these valves employ throttling regulation, resulting in reduced valve opening. This causes a significant pressure drop and heat loss in front of the valves, rather than the steam fully expanding and performing work in the flow path. This throttling process is essentially an irreversible entropy increase process, causing a significant loss of work capacity and directly lowering the unit's thermal economy under low load. Furthermore, regarding heating flexibility, traditional units typically extract a portion of steam directly from the turbine's intermediate-pressure or high-pressure cylinder exhaust pipes for external heating. When large amounts of industrial steam extraction are needed, this method severely reduces the steam flow entering the subsequent low-pressure cylinder, leading to a significant decrease in power generation and creating a "heat-driven power generation" situation, severely restricting the unit's deep peak-shaving capability during the heating season. Therefore, the main dilemma of existing technologies lies in the conflict between the unit's desire to participate in deep peak shaving and the inefficiency caused by throttling under low load, as well as the inherent contradiction between heating and power generation. The industry urgently needs an innovative technical solution that can simultaneously address the three major challenges of low-load economy, rapid load response, and flexible heating. Summary of the Invention

[0004] The purpose of this invention is to overcome the shortcomings of the prior art and provide a thermal power unit with an added front cylinder and high and low pressure steam injectors. This generator unit has the characteristics of strong peak-shaving capability, good low-load economy, fast load response, and flexible steam and heat supply.

[0005] To achieve the above objectives, the present invention discloses a thermal power unit with an added front cylinder and high and low pressure steam ejectors, including a main steam pipeline, a front cylinder, a high pressure cylinder, a reheater, a high pressure steam ejector, a low pressure steam ejector, and an industrial steam supply pipeline. The outlet of the main steam pipeline is connected to the inlet of the front cylinder via a newly added high-pressure main steam valve and a newly added high-pressure regulating valve. The outlet of the main steam pipeline is connected to the inlet of the high-pressure cylinder via a high-pressure main steam valve and a high-pressure regulating valve. The outlet of the main steam pipeline is connected to the inlet of the reheater via a high-pressure bypass regulating valve. The first extraction port of the front cylinder is connected to the inlet of the high-pressure steam ejector, and the outlet of the high-pressure steam ejector is connected to the inlet of the reheater via the first desuperheater. The second extraction port of the front cylinder is connected to the inlet of the low-pressure steam ejector, and the outlet of the low-pressure steam ejector is connected to the industrial steam supply pipeline via the second desuperheater. The outlet of the reheater is connected to the inlet of both the high-pressure steam ejector and the low-pressure steam ejector.

[0006] Furthermore, the front-mounted cylinder is connected to the high-pressure cylinder via a 3S clutch.

[0007] Furthermore, the first extraction port of the front cylinder is connected to the inlet of the high-pressure steam ejector via the first extraction electric valve and the high-pressure regulating valve.

[0008] Furthermore, the second extraction port of the front cylinder is connected to the inlet of the low-pressure steam ejector via the second extraction electric valve and the low-pressure regulating valve.

[0009] Furthermore, it also includes a low-pressure cylinder, with the exhaust port of the front cylinder connected to the inlet of the low-pressure cylinder via a first exhaust check valve.

[0010] Furthermore, it also includes a heat exchanger for the heating network, with the exhaust port of the front cylinder connected to the heat exchanger via a second exhaust check valve and a heating temperature control valve.

[0011] Furthermore, the exhaust port of the high-pressure cylinder is connected to the inlet of the reheater via a high-pressure exhaust check valve.

[0012] Furthermore, it also includes an intermediate-pressure cylinder, a condenser, and an extraction steam shut-off valve. The reheater outlet is divided into three paths. The first path is connected to the inlet of the intermediate-pressure cylinder via the intermediate-pressure main steam valve and the intermediate-pressure regulating valve. The second path is connected to the inlet of the condenser via the low-pressure bypass valve. The third path is connected to the inlet of the extraction steam shut-off valve. The outlet of the extraction steam shut-off valve is connected to the inlet of the high-pressure steam ejector via the first extraction steam regulating valve. The outlet of the extraction steam shut-off valve is connected to the inlet of the low-pressure steam ejector via the second extraction steam regulating valve.

[0013] Furthermore, the extraction port of the intermediate-pressure cylinder is connected to the condenser via an extraction non-return valve, an extraction electric valve, and a heat exchanger, while the outlet of the low-pressure cylinder is connected to the condenser.

[0014] Furthermore, the generator is coaxially arranged with the low-pressure cylinder, intermediate-pressure cylinder, and high-pressure cylinder.

[0015] The present invention has the following beneficial effects: In practical operation, the thermal power unit with added pre-cylinder and high and low pressure steam ejectors described in this invention adds a pre-cylinder before the high-pressure cylinder. Under low load, the pre-cylinder allows more main steam to expand fully and do work. Under medium and high load, the load response speed is fast, which is beneficial for peak shaving. At the same time, it has a steam extraction process to increase the boiler inlet water temperature. In addition, this invention is equipped with high and low pressure steam ejectors. Through the pre-cylinder with steam extraction and high and low pressure steam ejectors, the peak shaving capacity and steam and heat supply flexibility of the unit are improved. It has the characteristics of strong operability, strong peak shaving capacity, flexible steam supply mode, and significant energy saving effect. Attached Figure Description

[0016] To more clearly illustrate the technical solutions of the embodiments of this application, the drawings used in the description of the embodiments of this application will be briefly introduced below. Obviously, the drawings described below are only some embodiments of this application. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0017] Figure 1 This is a structural diagram of the present invention.

[0018] Among them, 1 is the newly added high-pressure main steam valve, 2 is the newly added high-pressure regulating valve, 3 is the front-mounted cylinder, 4 is the first extraction steam electric valve, 5 is the second extraction steam electric valve, 6 is the low-pressure regulating valve, 7 is the high-pressure regulating valve, 8 is the first exhaust steam non-return valve, 9 is the 3S clutch, 10 is the second exhaust steam non-return valve, 11 is the low-pressure steam ejector, 12 is the high-pressure steam ejector, 13 is the second extraction steam regulating valve, 14 is the first extraction steam regulating valve, 15 is the extraction steam shut-off valve, and 16 is the second reduction valve. 17 is the first desuperheater, 18 is the high-pressure bypass valve, 19 is the high-pressure main steam valve, 20 is the high-pressure regulating valve, 21 is the high-pressure cylinder, 22 is the high-pressure exhaust check valve, 23 is the intermediate-pressure cylinder, 24 is the intermediate-pressure regulating valve, 25 is the intermediate-pressure main steam valve, 26 is the extraction steam check valve, 27 is the extraction steam electric valve, 28 is the reheater, 29 is the heating temperature control valve, 30 is the low-pressure cylinder, 31 is the heat exchanger, 32 is the condenser, 33 is the low-pressure bypass valve, and 34 is the generator. Detailed Implementation

[0019] The technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some, not all, of the embodiments of the present invention. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.

[0020] In the description of this invention, it should be understood that the terms "comprising" and "including" indicate the presence of the described features, integrals, steps, operations, elements and / or components, but do not exclude the presence or addition of one or more other features, integrals, steps, operations, elements, components and / or collections thereof.

[0021] It should also be understood that the terminology used in this specification is for the purpose of describing particular embodiments only and is not intended to limit the invention. As used in this specification and the appended claims, the singular forms “a,” “an,” and “the” are intended to include the plural forms unless the context clearly indicates otherwise.

[0022] It should also be further understood that the term "and / or" as used in this specification and the appended claims refers to any combination and all possible combinations of one or more of the associated listed items, and includes such combinations. For example, A and / or B can represent three cases: A alone, A and B simultaneously, and B alone. Additionally, the character " / " in this invention generally indicates that the preceding and following objects have an "or" relationship.

[0023] It should be understood that although terms such as first, second, third, etc., may be used in the embodiments of the present invention to describe the preset range, these preset ranges should not be limited to these terms. These terms are only used to distinguish the preset ranges from one another. For example, without departing from the scope of the embodiments of the present invention, the first preset range may also be referred to as the second preset range, and similarly, the second preset range may also be referred to as the first preset range.

[0024] Depending on the context, the word "if" as used here can be interpreted as "when," "when," "in response to determination," or "in response to detection." Similarly, depending on the context, the phrase "if determination" or "if detection (of the stated condition or event)" can be interpreted as "when determination," "in response to determination," "when detection (of the stated condition or event)," or "in response to detection (of the stated condition or event)."

[0025] To make the objectives, technical solutions, and advantages of the embodiments of the present invention clearer, the technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some, not all, of the embodiments of the present invention. The components of the embodiments of the present invention described and shown in the accompanying drawings can generally be arranged and designed in various different configurations. Therefore, the following detailed description of the embodiments of the present invention provided in the accompanying drawings is not intended to limit the scope of the claimed invention, but merely to illustrate selected embodiments of the invention. All other embodiments obtained by those skilled in the art based on the embodiments of the present invention without inventive effort are within the scope of protection of the present invention.

[0026] The accompanying drawings illustrate various structural schematic diagrams according to embodiments disclosed in this invention. These drawings are not to scale, and some details have been enlarged for clarity, and some details may have been omitted. The shapes of the various regions and layers shown in the drawings, as well as their relative sizes and positional relationships, are merely exemplary and may deviate from reality due to manufacturing tolerances or technical limitations. Furthermore, those skilled in the art can design regions / layers with different shapes, sizes, and relative positions as needed.

[0027] Example 1 The thermal power unit with added pre-cylinder and high / low pressure steam ejectors described in this invention includes a main steam pipeline, a pre-cylinder 3, a high-pressure cylinder 21, a reheater 28, a high-pressure steam ejector 12, a low-pressure steam ejector 11, and an industrial steam supply pipeline. The outlet of the main steam pipeline is connected to the inlet of the pre-cylinder 3 via a newly added high-pressure main steam valve 1 and a newly added high-pressure regulating valve 2. The outlet of the main steam pipeline is connected to the inlet of the high-pressure cylinder 21 via a high-pressure main steam valve 19 and a high-pressure regulating valve 20. The outlet of the main steam pipeline is connected to the high-pressure bypass valve 18. The inlet of reheater 28 is connected; the first extraction port of the pre-cylinder 3 is connected to the inlet of high-pressure steam ejector 12, the outlet of high-pressure steam ejector 12 is connected to the inlet of reheater 28 via the first desuperheater 17, the second extraction port of the pre-cylinder 3 is connected to the inlet of low-pressure steam ejector 11, and the outlet of low-pressure steam ejector 11 is connected to the industrial steam supply pipeline via the second desuperheater 16; the outlet of reheater 28 is connected to the inlet of high-pressure steam ejector 12 and the inlet of low-pressure steam ejector 11.

[0028] To address the economic issues of turbine operation under low load conditions, traditional methods require closing the regulating valve to reduce steam flow. However, this leads to a significant throttling effect, resulting in a substantial decrease in the ideal enthalpy drop of the steam. The lower the load, the more severe the throttling loss, affecting not only unit energy efficiency but also limiting its ability to participate in deep peak shaving. To address these issues, this invention adds a pre-cylinder 3 before the high-pressure cylinder 21. Under low load conditions, more main steam is fed into the pre-cylinder 3 for full expansion and work, improving energy utilization efficiency. Under medium and high load conditions, the pre-cylinder 3 helps to accelerate load response and enhance peak shaving adaptability. A portion of the steam that has performed work in the pre-cylinder 3 is directly introduced into the low-pressure cylinder 30, bypassing the reheater 28, thus preventing the reheater 28 from overheating due to excessive main steam extraction, which would affect the steam intake of the pre-cylinder 3 and the unit's steam supply capacity. This also addresses the potential overheating problem of the reheater 28. This invention introduces reheater recirculation cooling technology, employing a high-pressure steam ejector 12. A small amount of main steam is used as a power source to pressurize a portion of the reheat steam. The mixed steam, after cooling, flows back into the reheater 28 to enhance its internal cooling effect. Under deep peak-shaving conditions (e.g., below 50% THA), the pressure of hot and cold reheat steam often fails to meet industrial steam supply requirements, and the fourth and fifth stages of extraction steam from the intermediate-pressure cylinder 23 are also insufficient to meet the pressure demands of domestic heating. Therefore, this invention incorporates a low-pressure steam ejector 11, which extracts high-quality steam from the front-mounted cylinder 3 to supply industrial users, and extracts the exhaust steam from the front-mounted cylinder 3 for domestic heating. This invention, through the integrated method of "front-mounted cylinder 3 with extraction steam + high-pressure steam ejector 12 + low-pressure steam ejector 11," significantly improves the unit's operating economy, peak-shaving capacity, and flexibility in heating and steam supply.

[0029] Example 2 To improve this application, refer to Figure 1 The thermal power unit with added front-mounted cylinder and high and low pressure steam injectors described in this invention includes a newly added high-pressure main steam valve 1, a newly added high-pressure regulating valve 2, a front-mounted cylinder 3, a first extraction steam electric valve 4, a second extraction steam electric valve 5, a low-pressure regulating valve 6, a high-pressure regulating valve 7, a first exhaust steam non-return valve 8, a 3S clutch 9, a second exhaust steam non-return valve 10, a low-pressure steam injector 11, a high-pressure steam injector 12, a second extraction steam regulating valve 13, and a first extraction steam regulating valve 14. 15. Extraction steam shut-off valve, 16. Second desuperheater, 17. First desuperheater, 18. High pressure bypass valve, 19. High pressure main steam valve, 20. High pressure regulating valve, 21. High pressure cylinder, 22. High pressure exhaust check valve, 23. Medium pressure cylinder, 24. Medium pressure regulating valve, 25. Medium pressure main steam valve, 26. Extraction steam check valve, 27. Extraction steam electric valve, 28. Reheater, 29. Heating temperature control valve, 30. Low pressure cylinder, 31. Heat exchanger, 32. Condenser, 33. Low pressure bypass valve, and 34. Generator; The outlet of the main steam pipeline is connected to the inlet of the front cylinder 3 via the newly added high-pressure main steam valve 1 and the newly added high-pressure regulating valve 2. The outlet of the main steam pipeline is connected to the inlet of the high-pressure cylinder 21 via the high-pressure main steam valve 19 and the high-pressure regulating valve 20. The outlet of the main steam pipeline is connected to the inlet of the reheater 28 via the high-pressure bypass regulating valve 18.

[0030] The first extraction port of the front cylinder 3 is connected to the inlet of the high-pressure steam ejector 12 via the first extraction electric valve 4 and the high-pressure regulating valve 7. The outlet of the high-pressure steam ejector 12 is connected to the inlet of the reheater 28 via the first desuperheater 17. The second extraction port of the front cylinder 3 is connected to the inlet of the low-pressure steam ejector 11 via the second extraction electric valve 5 and the low-pressure regulating valve 6. The outlet of the low-pressure steam ejector 11 is connected to the industrial steam supply pipeline via the second desuperheater 16. The exhaust port of the front cylinder 3 is connected to the inlet of the low-pressure cylinder 30 via the first exhaust check valve 8. The exhaust port of the front cylinder 3 is connected to the heat exchanger 31 via the second exhaust check valve 10 and the heating temperature control valve 29.

[0031] The exhaust port of the high-pressure cylinder 21 is connected to the inlet of the reheater 28 via the high-pressure exhaust check valve 22. The outlet of the reheater 28 is divided into three paths. The first path is connected to the inlet of the intermediate-pressure cylinder 23 via the intermediate-pressure main steam valve 25 and the intermediate-pressure regulating valve 24. The second path is connected to the inlet of the condenser 32 via the low-pressure bypass regulating valve 33. The third path is connected to the inlet of the extraction steam shut-off valve 15. The outlet of the extraction steam shut-off valve 15 is connected to the inlet of the high-pressure steam ejector 12 via the first extraction steam regulating valve 14. The outlet of the extraction steam shut-off valve 15 is connected to the inlet of the low-pressure steam ejector 11 via the second extraction steam regulating valve 13. The extraction port of the intermediate-pressure cylinder 23 is connected to the condenser 32 via the extraction steam check valve 26, the extraction steam electric valve 27 and the heat exchanger 31. The outlet of the low-pressure cylinder 30 is connected to the condenser 32.

[0032] The generator 34 is coaxially arranged with the low-pressure cylinder 30, the intermediate-pressure cylinder 23 and the high-pressure cylinder 21. The front-mounted cylinder 3 is connected to the high-pressure cylinder 21 through the 3S clutch 9.

[0033] During normal unit operation, the flow and pressure control of the main steam are coordinated by the high-pressure main steam valve 19 and the high-pressure regulating valve 20. The main steam enters the high-pressure cylinder 21 to expand and perform work. When the unit load rate is below 20%-30% THA, some of the main steam and hot reheat steam will enter the corresponding bypass systems; the remaining steam will pass through the partially opened high-pressure regulating valve 20 and intermediate-pressure regulating valve 24 to maintain the unit's constant pressure operation. As the load rate increases to above 20%-30% THA, the high-pressure bypass valve 18 and the low-pressure bypass valve 33 will be completely closed. At this time, all the main steam is introduced into the high-pressure cylinder 21 to expand and perform work, while all the hot reheat steam enters the intermediate-pressure cylinder 23, and the unit then switches to sliding pressure operation mode. The exhaust steam from the intermediate-pressure cylinder 23 then enters the low-pressure cylinder 30 to continue expanding and performing work. During this stage, the intermediate-pressure regulating valve 24 gradually closes completely. However, the opening of the high-pressure regulating valve 20 is kept at a small degree, especially when operating under deep peak shaving conditions below 50% THA, the energy loss caused by the throttling effect of the high-pressure regulating valve 7 is particularly significant.

[0034] This invention adds a front cylinder 3 before the high-pressure cylinder 21. The front cylinder 3 is flexibly connected to the main turbine unit via a 3S clutch 9. Under low-load conditions (unit load rate below 30% THA), the throttling loss of the high-pressure control valve 20 is significant. At this time, the system guides 40% to 50% of the main steam to the front cylinder 3, and the opening of the high-pressure control valve 20 is larger (over 70%), effectively reducing the throttling loss. The exhaust parameters of the front cylinder 3 are designed within the range of 1.5-4MPa and 300-400℃, thereby significantly improving the unit's economy under low-load operation. The front cylinder 3 has two stages of steam extraction: the first stage of extraction steam is sent to the high-pressure steam ejector 12 after passing through the extraction electric valve 27 and the high-pressure control valve 7; the second stage of extraction steam enters the low-pressure steam ejector 11 after passing through the extraction electric valve 27 and the low-pressure control valve 6. Part of the exhaust steam flows into the inlet pipe of the low-pressure cylinder 30 through the first exhaust non-return valve 8, while the other part can be connected to the heating network system for heating. When the load rises to the medium load range (30% THA to 50% THA), the unit switches to sliding pressure operation, and the opening of the high-pressure regulating valve 20 gradually increases, thereby weakening the throttling effect. At this time, the opening of the inlet regulating valve of the front cylinder 3 is correspondingly reduced, and more main steam is directed to the high-pressure cylinder 21. After entering the medium-high load range (load rate greater than 50% THA), the throttling loss of the high-pressure regulating valve 20 has been significantly reduced, and the turbine rotor is basically warmed up. The unit can then independently respond to peak demand without the front cylinder 3. At this time, the opening of the regulating valve of the front cylinder 3 is further reduced, retaining only the necessary opening to meet industrial steam supply demand and avoid overheating and damage to the blades due to cylinder idling; it can also be disconnected and shut down via the 3S clutch 9. In addition, the front cylinder 3 has the characteristics of short cylinder warm-up time and rapid start-up. When the main turbine rotor is not fully warmed up, the front cylinder 3 can take the lead in quickly lifting the load. After the main rotor is fully warmed up, the load can be smoothly transferred back to the main turbine unit.

[0035] To address the potential overheating issue caused by the main steam not entering the reheater 28 after the addition of the pre-cylinder 3, this invention adds a high-pressure steam ejector 12 and a first desuperheater 17. This device uses the steam extracted from the first section of the pre-cylinder 3 as high-pressure motive steam to pressurize a portion of the hot reheat steam. The mixed steam is cooled by the desuperheater, then merged with the cold reheat steam and returned to the reheater 28. This effectively increases the cooling steam flow rate inside the reheater 28, avoiding the risk of overheating in the reheater 28 due to excessive main steam extraction, and ensuring that the steam intake of the pre-cylinder 3 and the unit's steam supply capacity are not restricted.

[0036] When the unit operates at medium to high load, the hot reheat and cold reheat pressures can meet the industrial steam demand, and the extraction steam pressure of the intermediate-pressure cylinder 23 (four or five extractions) can meet the civil heating demand. However, when operating below deep-load conditions (unit load rate <50% THA), these demands cannot be met. Therefore, this invention adds a low-pressure steam ejector 11, which uses the second stage extraction steam of the front cylinder 3 as the driving steam to pressurize part of the hot reheat steam. The mixed steam is cooled to the required temperature by a desuperheater and then sent to the industrial steam supply pipeline. In this way, even when the unit is at a low load and the hot reheat and cold reheat pressures cannot meet the industrial steam demand, the industrial steam supply demand of the unit in a wide load range can still be met through this invention. After entering the winter heating season, the steam extracted by the fourth or fifth extraction of the medium-pressure cylinder 23 is generally used to meet the heating needs of the people. When the operation is below the deep adjustment (unit load rate <50%THA) condition, the steam extracted by the fourth or fifth extraction cannot meet the needs. At this time, the heating temperature control valve 29 is opened to use a part of the exhaust steam of the front cylinder 3 as a supplementary steam source to raise the temperature and pressure of the steam in the heating network pipeline. The heating temperature control valve 29 is used to control the outlet water temperature of the heating network to meet the heating needs and improve the reliability of the people heating.

[0037] Other embodiments of the invention will readily occur to those skilled in the art upon consideration of the specification and disclosure of the invention. This application is intended to cover any variations, uses, or adaptations of the invention that follow the general principles of the invention and include common knowledge or customary techniques in the art not disclosed herein. The specification and examples are to be considered exemplary only, and the true scope and spirit of the invention are indicated by the following claims.

[0038] It should be understood that the present invention is not limited to the precise structure described above and shown in the accompanying drawings, and various modifications and changes can be made without departing from its scope. The scope of the invention is limited only by the appended claims.

[0039] The above description is merely a preferred embodiment of the present invention and does not constitute any limitation on the present invention. Any simple modifications, alterations, or equivalent structural changes made to the above embodiments based on the technical essence of the present invention shall still fall within the protection scope of the present invention.

Claims

1. A thermal power unit with an added front-mounted cylinder and high / low-pressure steam injectors, characterized in that, It includes the main steam pipeline, the front cylinder (3), the high-pressure cylinder (21), the reheater (28), the high-pressure steam ejector (12), the low-pressure steam ejector (11), and the industrial steam supply pipeline; The outlet of the main steam pipeline is connected to the inlet of the front cylinder (3) via the newly added high-pressure main steam valve (1) and the newly added high-pressure regulating valve (2), the outlet of the main steam pipeline is connected to the inlet of the high-pressure cylinder (21) via the high-pressure main steam valve (19) and the high-pressure regulating valve (20), and the outlet of the main steam pipeline is connected to the inlet of the reheater (28) via the high-pressure bypass regulating valve (18). The first extraction port of the front cylinder (3) is connected to the inlet of the high-pressure steam ejector (12), the outlet of the high-pressure steam ejector (12) is connected to the inlet of the reheater (28) via the first desuperheater (17), the second extraction port of the front cylinder (3) is connected to the inlet of the low-pressure steam ejector (11), and the outlet of the low-pressure steam ejector (11) is connected to the industrial steam supply pipeline via the second desuperheater (16); the outlet of the reheater (28) is connected to the inlet of the high-pressure steam ejector (12) and the inlet of the low-pressure steam ejector (11).

2. The thermal power unit with an added front-mounted cylinder and high / low-pressure steam injectors as described in claim 1, characterized in that, The front cylinder (3) is connected to the high-pressure cylinder (21) via the 3S clutch (9).

3. The thermal power unit with an added front-mounted cylinder and high / low-pressure steam injectors as described in claim 1, characterized in that, The first extraction port of the front cylinder (3) is connected to the inlet of the high-pressure steam ejector (12) via the first extraction electric valve (4) and the high-pressure regulating valve (7).

4. The thermal power unit with added front-mounted cylinder and high and low pressure steam injectors according to claim 1, characterized in that, The second extraction port of the front cylinder (3) is connected to the inlet of the low-pressure steam ejector (11) via the second extraction electric valve (5) and the low-pressure regulating valve (6).

5. The thermal power unit with an added front-mounted cylinder and high / low-pressure steam injectors as described in claim 1, characterized in that, It also includes a low-pressure cylinder (30), and the exhaust port of the front cylinder (3) is connected to the inlet of the low-pressure cylinder (30) through the first exhaust check valve (8).

6. The thermal power unit with an added front-mounted cylinder and high / low-pressure steam injectors according to claim 1, characterized in that, It also includes a heat exchanger (31), and the exhaust port of the front cylinder (3) is connected to the heat exchanger (31) via the second exhaust check valve (10) and the heating temperature control valve (29).

7. The thermal power unit with an added front-mounted cylinder and high / low-pressure steam injectors according to claim 1, characterized in that, The exhaust port of the high-pressure cylinder (21) is connected to the inlet of the reheater (28) via the high-pressure exhaust check valve (22).

8. The thermal power unit with an added front-mounted cylinder and high and low pressure steam injectors according to claim 5, characterized in that, It also includes a medium-pressure cylinder (23), a condenser (32) and an extraction steam shut-off valve (15). The outlet of the reheater (28) is divided into three paths. The first path is connected to the inlet of the medium-pressure cylinder (23) via the medium-pressure main steam valve (25) and the medium-pressure regulating valve (24). The second path is connected to the inlet of the condenser (32) via the low-pressure bypass valve (33). The third path is connected to the inlet of the extraction steam shut-off valve (15). The outlet of the extraction steam shut-off valve (15) is connected to the inlet of the high-pressure steam ejector (12) via the first extraction steam regulating valve (14). The outlet of the extraction steam shut-off valve (15) is connected to the inlet of the low-pressure steam ejector (11) via the second extraction steam regulating valve (13).

9. The thermal power unit with an added front-mounted cylinder and high and low pressure steam injectors according to claim 8, characterized in that, The extraction port of the intermediate pressure cylinder (23) is connected to the condenser (32) via the extraction steam non-return valve (26), the extraction steam electric valve (27) and the heat exchanger (31), and the outlet of the low pressure cylinder (30) is connected to the condenser (32).

10. The thermal power unit with an added front-mounted cylinder and high and low pressure steam injectors according to claim 9, characterized in that, The generator (34) is coaxially arranged with the low-pressure cylinder (30), the medium-pressure cylinder (23) and the high-pressure cylinder (21).

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