Thermal power generating unit additionally provided with high-pressure cylinder front cylinder

Abstract

The thermal power generating unit is characterized in that an outlet of a main steam pipeline is communicated with an inlet of the front cylinder, an inlet of the high-pressure cylinder and an inlet of a reheater, and the outlet of the main steam pipeline is communicated with an inlet of a front cylinder bypass adjusting valve through a front cylinder bypass; an outlet of the front cylinder bypass regulating valve is communicated with an industrial steam supply pipeline through a steam supply pressure regulating valve and a second desuperheater, the outlet of the front cylinder bypass regulating valve is communicated with an inlet of a reheater through a steam ejector and a first desuperheater, and an outlet of the front cylinder is communicated with an inlet of a low-pressure cylinder through a first steam exhaust check valve; an outlet of the high-pressure cylinder is communicated with an inlet of the reheater through the high-exhaust check valve, an outlet of the reheater is communicated with the steam ejector and an inlet of the medium-pressure cylinder, an outlet of the low-pressure cylinder is communicated with the condenser, and the unit can improve the peak load regulation capacity of the thermal power generating unit, the heat efficiency of the cylinders in the low load state and the steam supply capacity in the low load state.

Description

Technical Field

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

[0002] In recent years, with the increasing environmental awareness of the public and the introduction of relevant national policies, small coal-fired boilers with high pollution and high energy consumption have been gradually phased out and shut down. The flexible transformation of large thermal power generating units meets national environmental protection requirements and related energy-saving policies, yielding significant economic, environmental, and social benefits. Given the rapid development of clean energy, which is characterized by random and intermittent power generation, large-scale grid connection of new energy sources can negatively impact the stable operation of the power grid to some extent. The demand for power system adjustability is surging. Therefore, thermal power units, which occupy a dominant position in the grid load, not only need to ensure a stable power supply and peak-shaving capabilities, but also must fulfill the obligation of peak shaving for the power system and meet steam supply demands. Without considering turbine modifications, common existing modification technologies for steam supply include intermediate control valves, small back-pressure turbines for heating, steam ejectors, and direct desuperheating and depressurization of high-pressure steam. Based on the current high-pressure steam supply parameters, the intermediate control valve's parameter adjustment method cannot meet the requirements for providing high-pressure steam supply over a wide load range. Conventional steam supply technology also uses the main steam extraction method, but excessive extraction will cause the reheater to overheat, which limits the unit's steam supply capacity. Summary of the Invention

[0003] The purpose of this invention is to overcome the shortcomings of the prior art and provide a thermal power unit with an increased high-pressure cylinder front cylinder, which can improve the peak-shaving capacity, cylinder thermal efficiency at low load, and steam supply capacity at low load.

[0004] To achieve the above objectives, the present invention discloses a thermal power unit with an added high-pressure cylinder front cylinder, comprising a main steam pipeline, a front cylinder, a high-pressure cylinder, a reheater, a front cylinder bypass control valve, an industrial steam supply pipeline, a reheater, a low-pressure cylinder, and a condenser. The outlet of the main steam pipeline is connected to the inlet of the pre-cylinder, the inlet of the high-pressure cylinder, and the inlet of the reheater. The outlet of the main steam pipeline is connected to the inlet of the pre-cylinder bypass regulating valve via the pre-cylinder bypass. The outlet of the pre-cylinder bypass regulating valve is connected to the industrial steam supply pipeline via the steam supply pressure regulating valve and the second desuperheater. The outlet of the pre-cylinder bypass regulating valve is connected to the inlet of the reheater via the steam ejector and the first desuperheater. The outlet of the pre-cylinder is connected to the inlet of the low-pressure cylinder via the first exhaust check valve. The outlet of the high-pressure cylinder is connected to the inlet of the reheater via a high-pressure exhaust check valve. The outlet of the reheater is connected to the steam ejector and the inlet of the intermediate-pressure cylinder. The outlet of the low-pressure cylinder is connected to the condenser.

[0005] Furthermore, the outlet of the main steam pipeline is connected to the inlet of the front-mounted cylinder via a newly added high-pressure main steam valve and a newly added high-pressure regulating valve.

[0006] Furthermore, the outlet of the main steam pipeline is connected to the inlet of the high-pressure cylinder via the outlet of the high-pressure main steam valve and the high-pressure regulating valve.

[0007] Furthermore, the outlet of the main steam pipeline is connected to the inlet of the reheater via a high-pressure bypass valve and a high-pressure bypass.

[0008] Furthermore, the outlet of the front cylinder is connected to the inlet of the second desuperheater via the second exhaust check valve.

[0009] Furthermore, the reheater outlet is connected to the steam ejector, intermediate pressure cylinder, and condenser.

[0010] Furthermore, the reheater outlet is divided into three paths. The first path is connected to the steam ejector via the extraction steam shut-off valve and the extraction steam regulating valve. The second 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 third path is connected to the condenser via the bypass regulating valve. The outlet of the low-pressure cylinder is connected to the condenser.

[0011] Furthermore, the front-mounted cylinder is connected to the high-pressure cylinder via a 3S clutch. Additionally, it includes a generator, which is coaxially arranged with the low-pressure, intermediate-pressure, and high-pressure cylinders.

[0012] Furthermore, the outlet of the pre-cylinder bypass control valve is connected to the inlet of the reheater via the steam shut-off valve, steam injector, and first desuperheater.

[0013] The present invention has the following beneficial effects: In specific operation, the thermal power unit with the addition of a high-pressure cylinder and a front-mounted cylinder as described in this invention adds a steam injector and a front-mounted cylinder bypass. Through the front-mounted cylinder + reheater recirculation + front-mounted cylinder bypass, the unit's peak-shaving capacity and steam supply flexibility 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

[0014] 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.

[0015] Figure 1 This is a structural diagram of the present invention.

[0016] Among them, 1 is the front cylinder bypass valve, 2 is the first exhaust non-return valve, 3 is the front cylinder, 4 is the second exhaust non-return valve, 5 is the steam supply pressure regulating valve, 6 is the steam inlet shut-off valve, 7 is the steam ejector, 8 is the newly added high-pressure main steam valve, 9 is the newly added high-pressure regulating valve, 10 is the second desuperheater, 11 is the high-pressure bypass valve, 12 is the high-pressure main steam valve, 13 is the high-pressure regulating valve, 14 is the 3S clutch, 15 is the high-pressure cylinder, 16 is the first desuperheater, 17 is the extraction steam regulating valve, 18 is the extraction steam shut-off valve, 19 is the high-pressure exhaust non-return valve, 20 is the reheater, 21 is the intermediate-pressure cylinder, 22 is the intermediate-pressure regulating valve, 23 is the intermediate-pressure main steam valve, 24 is the low-pressure bypass valve, 25 is the low-pressure cylinder, 26 is the condenser, and 27 is the generator. Detailed Implementation

[0017] 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.

[0018] 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.

[0019] 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.

[0020] 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.

[0021] 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.

[0022] 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)."

[0023] 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.

[0024] 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.

[0025] Example 1 refer to Figure 1The thermal power unit with an added high-pressure cylinder front cylinder according to the present invention includes a main steam pipeline, a front cylinder 3, a high-pressure cylinder 15, a reheater 20, a front cylinder bypass control valve 1, an industrial steam supply pipeline, a reheater 20, a low-pressure cylinder 25, and a condenser 26; the outlet of the main steam pipeline is connected to the inlet of the front cylinder 3, the inlet of the high-pressure cylinder 15, and the inlet of the reheater 20; the outlet of the main steam pipeline is connected to the inlet of the front cylinder bypass control valve 1 via a front cylinder bypass; the outlet of the front cylinder bypass control valve 1 is connected to the industrial steam supply pipeline. The pressure regulating valve 5 and the second desuperheater 10 are connected to the industrial steam supply pipeline. The outlet of the pre-cylinder bypass regulating valve 1 is connected to the inlet of the reheater 20 via the steam ejector 7 and the first desuperheater 16. The outlet of the pre-cylinder 3 is connected to the inlet of the low-pressure cylinder 25 via the first exhaust check valve 2. The outlet of the high-pressure cylinder 15 is connected to the inlet of the reheater 20 via the high exhaust check valve 19. The outlet of the reheater 20 is connected to the steam ejector 7 and the inlet of the intermediate-pressure cylinder 21. The outlet of the low-pressure cylinder 25 is connected to the condenser 26.

[0026] It should be noted that under low-load conditions, to reduce the steam flow into the turbine, the regulating valve is partially closed. As steam passes through this partially closed valve, significant throttling losses occur, resulting in a substantial reduction in the ideal enthalpy drop. The lower the load, the smaller the ideal enthalpy drop and the greater the throttling losses. This is not only detrimental to the unit's economical operation but also to deep peak shaving. To address this, this invention adds a pre-cylinder 3 before the high-pressure cylinder 15. Under low load conditions, the pre-cylinder 3 allows more main steam to fully expand and perform work. Under medium- and high load conditions, the load response is faster, which is beneficial for peak shaving. After some of the main steam expands and performs work in the pre-cylinder 3, the steam directly enters the low-pressure cylinder 25 instead of the reheater 20. Excessive main steam extraction can cause the reheater 20 to overheat, limiting the steam intake of the pre-cylinder 3 and the unit's steam supply capacity. To address this issue, this invention discloses a reheater recirculation cooling technology. A steam ejector 7 is used to pressurize a portion of the reheat steam using a small amount of main steam as motive steam. The pressurized mixed steam is then de-cooled by a desuperheater and returned to the reheater 20, increasing the cooling flow rate of the reheater 20 and solving the overheating problem of the reheater 20 when the main steam extraction is excessive.

[0027] Furthermore, considering that when operating below deep heating (50% THA) conditions, the hot reheat and cold reheat pressures cannot meet the industrial steam demand, this invention adds a pre-cylinder bypass to extract high-quality steam from the main steam system to meet industrial steam requirements. This invention significantly improves the unit's operating economy, peak-shaving capacity, and steam supply flexibility through the combination of "pre-cylinder 3 + reheater recirculation + new bypass".

[0028] Example 2 To further improve this application, refer to Figure 1The thermal power unit with an added high-pressure cylinder front cylinder according to the present invention includes a front cylinder bypass regulating valve 1, a first exhaust non-return valve 2, a front cylinder 3, a second exhaust non-return valve 4, a steam supply pressure regulating valve 5, an inlet steam shut-off valve 6, a steam ejector 7, a newly added high-pressure main steam valve 8, a newly added high-pressure regulating valve 9, a second desuperheater 10, a high-pressure bypass regulating valve 11, a high-pressure main steam valve 12, a high-pressure regulating valve 13, a 3S clutch 14, a high-pressure cylinder 15, a first desuperheater 16, an extraction steam regulating valve 17, an extraction steam shut-off valve 18, a high-pressure exhaust non-return valve 19, a reheater 20, an intermediate-pressure cylinder 21, an intermediate-pressure regulating valve 22, an intermediate-pressure main steam valve 23, a low-pressure bypass regulating valve 24, a low-pressure cylinder 25, a condenser 26, and a generator 27; The outlet of the main steam pipeline is connected to the inlet of the pre-cylinder 3 via the newly added high-pressure main steam valve 8 and the newly added high-pressure regulating valve 9. The outlet of the main steam pipeline is connected to the inlet of the high-pressure cylinder 15 via the outlet of the high-pressure main steam valve 12 and the high-pressure regulating valve 13. The outlet of the main steam pipeline is connected to the inlet of the reheater 20 via the high-pressure bypass regulating valve 11 and the high-pressure bypass. The outlet of the main steam pipeline is connected to the inlet of the pre-cylinder bypass regulating valve 1. The outlet of the pre-cylinder bypass regulating valve 1 is connected to the industrial steam supply pipeline via the steam supply pressure regulating valve 5 and the second desuperheater 10. The outlet of the pre-cylinder bypass regulating valve 1 is connected to the inlet of the reheater 20 via the steam inlet shut-off valve 6, the steam ejector 7 and the first desuperheater 16. The outlet of the pre-cylinder 3 is connected to the inlet of the low-pressure cylinder 25 via the first exhaust check valve 2.

[0029] The outlet of the front cylinder 3 is connected to the inlet of the second desuperheater 10 via the second exhaust check valve 4. The outlet of the high-pressure cylinder 15 is connected to the inlet of the reheater 20 via the high exhaust check valve 19. The outlet of the reheater 20 is divided into three paths. The first path is connected to the steam ejector 7 via the extraction steam shut-off valve 18 and the extraction steam regulating valve 17. The second path is connected to the inlet of the intermediate-pressure cylinder 21 via the intermediate-pressure main steam valve 23 and the intermediate-pressure regulating valve 22. The third path is connected to the condenser 26 via the bypass regulating valve. The outlet of the low-pressure cylinder 25 is connected to the condenser 26.

[0030] The front-mounted cylinder 3 is connected to the high-pressure cylinder 15 via the 3S clutch 14, and the generator 27 is arranged coaxially with the low-pressure cylinder 25, the intermediate-pressure cylinder 21 and the high-pressure cylinder 15.

[0031] During normal operation, under the control of the high-pressure main steam valve 12 and the high-pressure regulating valve 13, the main steam enters the high-pressure cylinder 15 to expand and do work. When the load rate is less than 20%-30% THA, part of the main steam and hot reheat steam will enter the high-pressure bypass and low-pressure bypass respectively through the high-pressure bypass valve 11 and the low-pressure bypass valve 24. The remaining main steam enters the high-pressure regulating valve 13 and the intermediate-pressure regulating valve 22 to maintain the unit's constant pressure operation. When the load rate is greater than 20%-30% THA, the high-pressure bypass valve 11 and the low-pressure bypass valve 24 are fully closed, and all the main steam enters the high-pressure cylinder 15 to expand and do work. All the hot reheat steam enters the intermediate-pressure cylinder 21 to expand and do work, and the unit enters the sliding pressure operation mode. The exhaust steam from the intermediate-pressure cylinder 21 enters the low-pressure cylinder 25 to expand and do work. When the load rate is greater than 20%-30% THA, the medium-pressure regulating valve 22 gradually closes completely, but the opening of the high-pressure regulating valve 13 is very small. When operating below the deep regulation (50% THA) condition, the throttling loss of the high-pressure regulating valve 13 is relatively large.

[0032] This invention introduces a new pre-cylinder 3 before the high-pressure cylinder 15, coupled to the turbine unit via a 3S clutch 14. At low loads (unit load rate <30% THA), the high-pressure regulating valve 13 experiences significant throttling losses, introducing 40%-50% of the main steam into the pre-cylinder 3. The newly added high-pressure regulating valve 9 before the pre-cylinder 3 has a large opening (>70%), resulting in minimal throttling losses. The exhaust pressure of the pre-cylinder 3 ranges from 1.5-4 MPa, and the exhaust temperature ranges from 300-400℃, thus improving the turbine unit's economic efficiency during low-load operation. A portion of the exhaust steam from the pre-cylinder 3 enters the inlet pipe of the low-pressure cylinder 25 through the first exhaust non-return valve 2, while the remaining portion participates in industrial steam supply. At medium load (30% THA < unit load rate < 50% THA), the turbine unit enters sliding pressure operation, the opening of the high-pressure control valve 13 gradually increases, and the throttling loss gradually decreases. At this time, the opening of the newly added high-pressure control valve 9 of the front cylinder 3 gradually decreases, gradually introducing more and more main steam into the high-pressure cylinder 15. After the unit load enters medium-high load (unit load rate > 50% THA), the throttling loss of the high-pressure control valve 13 is greatly reduced, and the turbine rotor is basically warmed up. It no longer needs to rely on the front cylinder 3 for rapid response peak shaving. Moreover, at this time, the opening of the newly added high-pressure control valve 9 of the front cylinder 3 is also greatly reduced. Only a part of the opening can be retained to meet the industrial steam supply demand while preventing the front cylinder 3 from idling and causing the cylinder blades to overheat and be damaged. The front cylinder 3 can also be decoupled and shut down through the 3S clutch 14. In addition, the front cylinder 3 has a short warm-up time and a fast start-up speed. When the turbine rotor is not fully warmed up, it can replace the turbine unit to quickly increase the load. After the turbine rotor is fully warmed up, the load can be switched back to the turbine unit load.

[0033] After the addition of the front cylinder 3, some of the main steam expands and does work but no longer enters the reheater 20. When the main steam extraction is too large, it will cause the reheater 20 to overheat, which will limit the steam intake of the front cylinder 3 and the steam supply capacity of the unit. Therefore, a steam ejector 7 and a first desuperheater are added. A small amount of main steam is introduced through the front cylinder bypass as power steam to pressurize some of the hot reheat steam. The pressurized mixed steam is cooled by the first desuperheater and then mixed with the cold reheat steam before returning to the reheater 20, increasing the cooling flow of the reheater 20 to solve the problem of overheating of the reheater 20 when the main steam extraction is too large.

[0034] When the unit operates at medium to high loads, the hot reheat and cold reheat pressures can meet the industrial steam demand. However, when operating below deep-load conditions (unit load rate <50% THA), these demands cannot be met. Therefore, this invention adds a front-mounted cylinder bypass to extract high-quality steam from the main steam. The exhaust steam from the front-mounted cylinder 3 is mixed with the steam from the front-mounted cylinder bypass after passing through the second exhaust check valve. The steam supply pressure is controlled by the steam supply pressure regulating valve 5, and the steam supply temperature is controlled by the second desuperheater. This allows the unit to meet the industrial steam demand during operation in a wide load range, effectively improving the reliability of industrial steam supply.

[0035] 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.

[0036] 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.

[0037] 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 high-pressure cylinder front-mounted cylinder, characterized in that, It includes the main steam pipeline, the front cylinder (3), the high-pressure cylinder (15), the reheater (20), the front cylinder bypass valve (1), the industrial steam supply pipeline, the reheater (20), the low-pressure cylinder (25), and the condenser (26). The outlet of the main steam pipeline is connected to the inlet of the pre-cylinder (3), the inlet of the high-pressure cylinder (15) and the inlet of the reheater (20). The outlet of the main steam pipeline is connected to the inlet of the pre-cylinder bypass regulating valve (1) via the pre-cylinder bypass. The outlet of the pre-cylinder bypass regulating valve (1) is connected to the industrial steam supply pipeline via the steam supply pressure regulating valve (5) and the second desuperheater (10). The outlet of the pre-cylinder bypass regulating valve (1) is connected to the inlet of the reheater (20) via the steam ejector (7) and the first desuperheater (16). The outlet of the pre-cylinder (3) is connected to the inlet of the low-pressure cylinder (25) via the first exhaust check valve (2). The outlet of the high-pressure cylinder (15) is connected to the inlet of the reheater (20) via the high-pressure exhaust check valve (19). The outlet of the reheater (20) is connected to the steam ejector (7) and the inlet of the intermediate-pressure cylinder (21). The outlet of the low-pressure cylinder (25) is connected to the condenser (26).

2. The thermal power unit with an added high-pressure cylinder front-mounted cylinder according to claim 1, characterized in that, 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 (8) and the newly added high-pressure regulating valve (9).

3. The thermal power unit with an added high-pressure cylinder front-mounted cylinder according to claim 1, characterized in that, The outlet of the main steam pipeline is connected to the inlet of the high-pressure cylinder (15) via the outlet of the high-pressure main steam valve (12) and the high-pressure regulating valve (13).

4. The thermal power unit with an added high-pressure cylinder front-mounted cylinder according to claim 1, characterized in that, The outlet of the main steam pipeline is connected to the inlet of the reheater (20) via a high-pressure bypass valve (11) and a high-pressure bypass.

5. The thermal power unit with an added high-pressure cylinder front-mounted cylinder according to claim 1, characterized in that, The outlet of the front cylinder (3) is connected to the inlet of the second desuperheater (10) via the second exhaust check valve (4).

6. The thermal power unit with an added high-pressure cylinder front-mounted cylinder according to claim 1, characterized in that, The outlet of the reheater (20) is connected to the steam ejector (7), the intermediate pressure cylinder (21) and the condenser (26).

7. The thermal power unit with an added high-pressure cylinder front-mounted cylinder according to claim 1, characterized in that, The outlet of the reheater (20) is divided into three paths. The first path is connected to the steam ejector (7) via the extraction steam shut-off valve (18) and the extraction steam regulating valve (17). The second path is connected to the inlet of the intermediate pressure cylinder (21) via the intermediate pressure main steam valve (23) and the intermediate pressure regulating valve (22). The third path is connected to the condenser (26) via the bypass regulating valve. The outlet of the low pressure cylinder (25) is connected to the condenser (26).

8. The thermal power unit with an added high-pressure cylinder front-mounted cylinder according to claim 1, characterized in that, The front cylinder (3) is connected to the high-pressure cylinder (15) via the 3S clutch (14).

9. The thermal power unit with an added high-pressure cylinder front-mounted cylinder according to claim 8, characterized in that, It also includes a generator (27), which is coaxially arranged with the low-pressure cylinder (25), the medium-pressure cylinder (21) and the high-pressure cylinder (15).

10. The thermal power unit with an added high-pressure cylinder front-mounted cylinder according to claim 1, characterized in that, The outlet of the pre-cylinder bypass control valve (1) is connected to the inlet of the reheater (20) via the steam shut-off valve (6), the steam injector (7) and the first desuperheater (16).

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