Multi-machine-furnace combined transportation system

Abstract

The invention discloses a multi-machine-boiler combined transportation system, and relates to the technical field of generator sets, the multi-machine-boiler combined transportation system comprises a plurality of boilers and a plurality of steam turbines, the boilers converge main steam pipes to the same main steam main pipe, and the steam turbines are in one-to-one correspondence with the boilers; the main steam mother pipe distributes main steam to high-pressure cylinders of all the steam turbines according to needs, the high-pressure cylinders of all the steam turbines feed exhausted steam into all the boiler reheaters through reheating cold section pipes and reheater steam inlet pipes, and all the reheating cold section pipes are provided with steam supplementing pipes. The boiler reheaters feed steam into an intermediate-pressure cylinder of the steam turbine through reheating heat section pipes respectively, and each reheating heat section pipe is provided with a steam extraction pipe. According to the system, main steam, cold reheat and hot reheat parameters can be consistent with operation requirements of all equipment of the system, machine-boiler decoupling and decoupling between units can be achieved, and conditions for flexible operation of the units are promoted.

Description

Technical Field

[0001] The present application relates to the technical field of generator sets, and in particular to a multi-machine-boiler combined operation system. Background Art

[0002] Multi-unit, multi-boiler interoperation busbar control units connect multiple units to boiler and turbine systems through a busbar control. Instead of the conventional one-to-one correspondence between a single boiler and a single turbine, the boilers and turbines can each operate across a wide range of loads, even in a split configuration. This improves operational flexibility when the boilers and turbines are mismatched. With increasing demands for low-carbon, high-efficiency, and flexible units, and with the advancement of rapid load-variation and deep peak-shaving technologies, busbar control has become increasingly valuable for large units due to its ability to reduce operational dependencies between units and boilers and improve operational flexibility.

[0003] Large units typically have reheat systems, with the main steam and reheater interconnected with the turbine and boiler. This results in complex control systems for these units. Key issues include overheating or underheating of the boiler reheater, imbalanced steam flow between the high-pressure and intermediate-pressure cylinders of the turbine, and imbalanced feedwater systems. Improper system configuration can significantly restrict turbine and boiler operation, failing to meet the required flexibility of the control system. Summary of the Invention

[0004] The main purpose of this application is to provide a multi-machine-boiler intermodal system, aiming to solve the technical problem of insufficient operating flexibility of existing multi-machine-boiler intermodal main control units.

[0005] The technical solutions adopted in this application are as follows: A multi-machine-boiler interoperation system includes multiple boilers and multiple steam turbines. The multiple boilers each gather their main steam pipes into the same main steam header. The multiple steam turbines correspond to the multiple boilers one-to-one, and the main steam header distributes the main steam to the high-pressure cylinder of each steam turbine as needed. The high-pressure cylinder of each steam turbine sends exhaust steam into the reheater of each boiler through the reheat cold section pipe and the reheater steam inlet pipe. Each of the reheat cold section pipes is provided with a steam supply pipe. The boiler reheater each sends steam into the intermediate pressure cylinder of the steam turbine through the reheat hot section pipe. Each of the reheat hot section pipes is provided with a steam extraction pipe.

[0006] Optionally, a main steam inlet pipe is provided between the main steam main pipe and the high-pressure cylinder of the steam turbine, and a high-pressure regulating valve is provided on the main steam inlet pipe.

[0007] Optionally, a high-discharge check valve is provided on the reheat cold section pipe.

[0008] Optionally, a reheater inlet regulating valve and a reheater inlet flow meter are provided on the reheater steam inlet pipe.

[0009] Optionally, an auxiliary reheater is provided between the reheat cold section tube and the reheat hot section tube, the steam inlet pipe of the auxiliary reheater is located before the reheater inlet regulating valve, and the steam outlet pipe of the auxiliary reheater is located after the outlet of the boiler reheater.

[0010] Optionally, an auxiliary reheater steam inlet regulating valve is provided on the steam inlet pipe of the auxiliary reheater.

[0011] Optionally, the steam inlet end of the steam extraction pipe is located between the steam outlet end of the auxiliary reheater and the steam inlet end of the intermediate pressure cylinder of the steam turbine.

[0012] Optionally, the heat recovery water supply pipes of the plurality of boilers are combined into the same water supply main pipe, and the water supply main pipe supplies water to each boiler as needed through the heat supply water inlet pipe.

[0013] Optionally, a booster pump is provided on the heat recovery water supply pipe, and a water supply regulating valve and a water supply flow meter are provided on the heat supply water inlet pipe.

[0014] Optionally, a water supply isolation valve is provided on the water supply main pipe, and the water supply isolation valve is located between the heat recovery water supply pipes.

[0015] Compared with the prior art, the present invention has the following advantages: The present application proposes a multi-machine boiler interoperation system, including multiple boilers and multiple steam turbines. The multiple boilers each collect their main steam pipes into the same main steam main pipe. The multiple steam turbines correspond to the multiple boilers one by one, and the main steam main pipe distributes the main steam to the high-pressure cylinder of each steam turbine as needed. The high-pressure cylinder of each steam turbine sends the exhaust steam into the reheater of each boiler through the reheat cold section pipe and the reheater steam inlet pipe. Each reheat cold section pipe is provided with a steam supply pipe. The boiler reheater each sends steam into the medium-pressure cylinder of the steam turbine through the reheat hot section pipe. Each of the hot section pipes of the reheating device is provided with an extraction pipe, which connects the main steam mother pipe of the boiler. The cylinders of the steam turbine of each unit still operate according to the original system. By setting an adjustable auxiliary reheater, an imbalance between the turbine and the boiler can be allowed, which improves the operating flexibility of the mother pipe unit. At the same time, a supplementary steam pipe is installed on the cold section pipe of the reheating device. When the steam temperature is too high or too low, the supplementary steam pipe is used to maintain the boiler reheater working within the normal temperature range. An extraction pipe is also installed on the hot section pipe of the reheating device to promptly extract the steam during the supplementary steam, so as to avoid the excessive pressure of the intermediate pressure cylinder of the steam turbine. The steam turbine body of this solution has no safety issues. By adapting the boiler and setting the adjustment means, it is possible to achieve decoupling of the turbine and boiler, decoupling between the units, and promote the conditions for flexible operation of the units. BRIEF DESCRIPTION OF THE DRAWINGS

[0016] Figure 1 This is a system structure diagram of the multi-machine-furnace intermodal operation system provided in an embodiment of the present application.

[0017] Description of the reference numerals in the accompanying drawings: 1- Main steam header; 2- Main steam isolation valve; 3- Feedwater isolation valve; 4- Feedwater header; 5- #1 steam turbine high-pressure cylinder; 6- #1 steam turbine intermediate-pressure cylinder; 7- #2 steam turbine high-pressure cylinder; 8- #2 steam turbine intermediate-pressure cylinder; 9- #1 boiler; 10- #1 auxiliary reheater; 11- #2 boiler; 12- #2 auxiliary reheater; 13- #1 main steam pipe; 14- #1 main steam inlet pipe; 15-#1 booster pump; 16-#1 reheat cold section pipe; 17-#1 heat recovery feed water pipe; 18-#1 heat recovery water inlet pipe; 19-#1 reheater steam inlet pipe; 20-#1 auxiliary reheater air inlet pipe; 21-#1 reheater hot section pipe; 22-#1 high discharge check valve; 23-#1 feed water regulating valve; 24-#1 feed water flow meter; 25-#1 reheater inlet regulating valve; 26 -#1 reheater inlet flowmeter; 27-#1 auxiliary reheater inlet regulating valve; 28-#2 booster pump; 29-#1 high-pressure regulating valve; 30-#2 main steam pipe; 31-#2 main steam inlet pipe; 32-#2 high-pressure regulating valve; 33-#2 reheat cold section pipe; 34-#2 heat recovery feed water pipe; 35-#2 heat recovery inlet pipe; 36-#2 reheater steam inlet pipe; 37-auxiliary reheater steam inlet pipe; 38-#2 intermediate pressure cylinder steam inlet pipe; 39-#2 high-pressure exhaust check valve; 40-#2 feed water regulating valve; 41-#2 feed water flowmeter; 42-#2 reheater inlet regulating valve; 43-#2 reheater inlet flowmeter; 44-#2 auxiliary reheater inlet regulating valve; 45-#1 supplementary steam pipe; 46-#1 extraction pipe; 47-#2 supplementary steam pipe; 48-#2 extraction pipe. DETAILED DESCRIPTION

[0018] The following will be combined with the drawings in the embodiments of this application to clearly and completely describe the technical solutions in the embodiments of this application. Obviously, the embodiments described are only part of the embodiments of this application, not all of the embodiments. Based on the embodiments of this application, all other embodiments obtained by ordinary technicians in this field without making creative efforts are within the scope of protection of this application.

[0019] It should be noted that all directional indications in the embodiments of the present application (such as up, down, left, right, front, back, etc.) are only used to explain the relative position relationship, movement status, etc. between the various components under a certain specific posture (as shown in the accompanying drawings). If the specific posture changes, the directional indication will also change accordingly.

[0020] In this application, unless otherwise specified or limited, the terms "connection" and "fixation" should be understood in a broad sense. For example, "fixation" can mean fixed connection, detachable connection, or integration; mechanical connection or electrical connection; direct connection or indirect connection through an intermediate medium; internal communication between two elements or interaction between two elements, unless otherwise specified. For those skilled in the art, the specific meanings of the above terms in this application can be understood according to specific circumstances.

[0021] In addition, if there are descriptions involving "first", "second", etc. in the embodiments of the present application, the descriptions of "first", "second", etc. are only for descriptive purposes and cannot be understood as indicating or suggesting their relative importance or implicitly indicating the number of the indicated technical features. Therefore, the features defined as "first" and "second" may explicitly or implicitly include at least one of such features. In addition, the meaning of "and / or" appearing throughout the text includes three parallel schemes. Taking "A and / or B" as an example, it includes scheme A, or scheme B, or a scheme in which A and B are satisfied at the same time. In addition, the technical solutions between the various embodiments can be combined with each other, but it must be based on the ability of ordinary technicians in this field to implement it. When the combination of technical solutions is mutually contradictory or cannot be implemented, it should be deemed that such a combination of technical solutions does not exist and is not within the scope of protection required by this application.

[0022] Refer to the attached Figure 1 , an embodiment of the present application provides a multi-machine-boiler interoperation system, including multiple boilers and multiple steam turbines. The multiple boilers each gather their main steam pipes into the same main steam main pipe. The multiple steam turbines correspond one-to-one to the multiple boilers, and the main steam main pipe distributes the main steam to the high-pressure cylinder of each steam turbine as needed. The high-pressure cylinder of each steam turbine sends the exhaust steam into the reheater of each boiler through the reheat cold section pipe and the reheater steam inlet pipe. Each reheat cold section pipe is provided with a steam supply pipe. The boiler reheater each sends steam into the intermediate pressure cylinder of the steam turbine through the reheat hot section pipe, and each reheat hot section pipe is provided with a steam extraction pipe.

[0023] Traditional steam-powered multi-unit boiler interoperation is a classic steam power system operating method in thermal power plants. Its core is to interconnect multiple boilers and multiple steam turbines through a steam main (common pipeline). However, in actual application, it faces the following problems: First, due to the differences in the reheat steam parameters (temperature / pressure) output by multiple boilers, the steam from different boilers may form local high-temperature or low-temperature areas after entering the main pipe and mixing. This may easily cause the boiler reheater to overheat or underheat after the main pipe supplies hot steam.

[0024] Second, when multiple turbines adjust their inlet valves simultaneously, the main pipe pressure fluctuates, leading to a mismatch between the HP cylinder exhaust flow and the demand from the IP cylinder. For example, if a turbine is rapidly deloaded, its HP cylinder exhaust steam decreases, but the IP cylinder still relies on the existing reheat steam flow, causing a transient shortfall.

[0025] In response to the above-mentioned technical problems that need to be solved urgently, the present application provides a multi-machine-boiler interoperation system, including multiple boilers and multiple steam turbines. The multiple boilers each gather their main steam pipes into the same main steam mother pipe, and the multiple steam turbines correspond one-to-one to the multiple boilers. The main steam mother pipe distributes the main steam to the high-pressure cylinder of each steam turbine as needed. The high-pressure cylinder of each steam turbine sends the exhaust steam into the reheater of each boiler through the reheat cold section pipe and the reheater steam inlet pipe. Each reheat cold section pipe is provided with a steam supply pipe. The boiler reheater each sends steam into the medium-pressure cylinder of the steam turbine through the reheat hot section pipe, and each reheat hot section pipe is provided with a steam extraction pipe.

[0026] It is not difficult to find that under this implementation mode, by connecting the boiler main steam main pipe, the cylinders of each unit's steam turbine still operate according to the original system without main pipe connection. At the same time, steam supply pipes and steam extraction pipes are added at the steam inlet and outlet ends of the boiler reheater. The main pipe can realize the on-demand distribution of steam. Steam extraction and supply steam can ensure that the boiler reheater operates at normal temperature, does not overheat, and prevents low temperature. The differences between the boiler and steam turbine of this unit and between the boilers and steam turbines of different units are configured according to the main steam and reheat requirements of the boiler, and are also adapted to the needs of the steam turbine. Through various adjustment means set up in this system, the main steam, cold reheat and hot reheat parameters can be made consistent with the operating requirements of each equipment in the system, and the decoupling of the machine and boiler and the decoupling between units can be achieved, thus promoting the conditions for flexible operation of the units.

[0027] In this embodiment, by providing the supplementary steam pipe and the extraction steam pipe, when the main steam flow of the boiler of a unit is greater than the steam flow to the high-pressure cylinder of the steam turbine of the unit, the supplementary steam pipe on the cold-end reheat pipe of the unit is used to supplement the low-temperature steam flow into the boiler reheater, thereby preventing the boiler reheater from overheating. At the same time, the extraction steam pipe on the hot-end reheat pipe is used to prevent the supplementary steam from entering the intermediate-pressure cylinder of the unit, thereby ensuring normal steam demand, preventing the intermediate-pressure cylinder pressure from exceeding the limit, and realizing flexible operation of the unit.

[0028] In one embodiment, main steam for the steam turbine to perform work is generated during the combustion process of the boiler. The main steam flows into the main steam header through the main steam pipe. The main steam header is provided with a main steam isolation valve. The steam from all boilers converges in the main steam header for mixing. Of course, a main steam inlet pipe is provided between the main steam header and the high-pressure cylinder of the steam turbine. The main steam inlet pipe is used to send the steam in the main steam header into the high-pressure cylinder of the steam turbine. A high-pressure regulating valve is provided on the main steam inlet pipe connecting the main steam header and the high-pressure cylinder of the steam turbine.

[0029] It is not difficult to imagine that under this embodiment, a high-pressure regulating valve is provided on the main steam inlet pipe connecting the main steam main pipe and the high-pressure cylinder of the steam turbine, and the high-pressure regulating valve is used to realize on-demand adjustment of the steam intake amount of the high-pressure cylinder of the steam turbine. When the high-pressure cylinder of the steam turbine requires a larger amount of steam, the opening of the high-pressure regulating valve is increased to increase the steam intake amount of the high-pressure cylinder of the steam turbine. On the contrary, when the high-pressure cylinder of the steam turbine requires a smaller amount of steam, the opening of the high-pressure regulating valve is reduced to reduce the steam intake amount of the high-pressure cylinder of the steam turbine, thereby realizing on-demand adjustment of the steam intake amount of the high-pressure cylinder of the steam turbine.

[0030] In one embodiment, the high-pressure cylinder of the steam turbine is connected to the boiler reheater at the exhaust port through the reheat cold section pipe and the reheater steam inlet pipe, and a high-pressure exhaust check valve is provided on the exhaust pipe.

[0031] As will be appreciated, in this embodiment, the high-pressure discharge check valve is installed to prevent backflow of the medium. In a steam turbine system, when the high-pressure cylinder discharges steam to the reheater or other components, the check valve can prevent steam from flowing back into the high-pressure cylinder during unit shutdown or failure, potentially causing equipment damage or safety hazards. The installation of a check valve is particularly important in multi-unit systems. Since multiple units are interconnected, the check valve can isolate the faulty unit and ensure normal operation of the rest of the system.

[0032] In one embodiment, a reheater inlet regulating valve and a reheater inlet flow meter are provided on the reheater steam inlet pipe.

[0033] In the above-described embodiment, the reheater inlet regulating valve is typically used to control the flow and pressure entering the boiler reheater, ensuring that steam parameters meet design requirements. Furthermore, the regulating valve adjusts flow during variable load conditions to maintain system stability, prevent excessive temperature fluctuations, and protect the reheater piping. A reheater inlet flowmeter monitors steam flow in real time and provides feedback to the control system, enabling the reheater inlet regulating valve to make appropriate adjustments. Furthermore, flow data may be used to calculate efficiency, optimize combustion and steam parameters, and monitor for anomalies, such as sudden changes in flow rate that may indicate leaks or blockages.

[0034] In one embodiment, an auxiliary reheater is provided between the cold reheating section pipe and the hot reheating section pipe, the steam inlet pipe of the auxiliary reheater is located before the reheater inlet regulating valve, and the steam outlet pipe of the auxiliary reheater is located after the outlet of the boiler reheater (i.e., before the intermediate pressure cylinder of the steam turbine).

[0035] In the above embodiment, it is conceivable that the boiler reheater outlet steam temperature may be insufficient (e.g., below the design value of 540°C) due to load fluctuations, fuel changes, or equipment aging. The auxiliary reheater can then reheat the steam to ensure that the steam temperature entering the intermediate pressure cylinder remains stable within the range of 540–570°C, thus preventing the reduction of turbine efficiency due to excessively low temperatures. Furthermore, under low load or high backpressure conditions, the boiler reheater outlet steam may carry moisture (wet steam) due to insufficient temperature. Further heating by the auxiliary reheater can increase the steam dryness (approaching dry saturation or superheated state), preventing wet steam from entering the intermediate pressure cylinder and corroding the blades. Therefore, by providing an auxiliary reheater, precise adjustment of the intermediate pressure cylinder inlet steam parameters can be achieved, thereby improving unit thermal efficiency, enhancing operational flexibility, and protecting the turbine.

[0036] In one embodiment, an auxiliary reheater steam inlet regulating valve is provided on the steam inlet pipe of the auxiliary reheater.

[0037] In the above embodiment, the auxiliary reheater steam inlet regulating valve is installed to precisely control the steam flow rate, optimize the auxiliary reheater's heating efficiency, and thus improve the overall thermal cycle efficiency. This also prevents excessive fluctuations in steam parameters, reduces thermal stress on the equipment, and extends its service life.

[0038] In one embodiment, the heat recovery water pipes of multiple boilers are combined into the same water supply main pipe, which is provided with a water supply isolation valve. The water supply main pipe supplies water to each boiler as needed through the heat supply water inlet pipe.

[0039] In the above-described embodiment, by connecting all main pipes related to the water supply system, the differences between the boiler and steam turbine of the local unit, and between the boilers and steam turbines of different units, are configured according to the boiler feed water requirements, and the requirements of the steam turbine are also adapted. Through the water supply regulation means provided by this system, the water supply parameters can be consistent with the operating requirements of each device in the system, and decoupling of the boiler and the units can be achieved, thus promoting the conditions for flexible operation of the units. At the same time, installing a water supply isolation valve on the water supply main pipe can physically isolate the water supply pipeline of the corresponding unit when repairing a unit, thereby facilitating maintenance.

[0040] In one embodiment, a booster pump is provided on the heat recovery water supply pipe, and a water supply regulating valve and a water supply flow meter are provided on the heat supply water inlet pipe.

[0041] In the above implementation, the return water pressure drops after passing through the condenser, deaerator, heater, and other equipment. The booster pump then raises the return water pressure to the boiler feedwater requirement (e.g., 1.5–3 MPa), ensuring that the water can overcome pipe friction and height differences. Furthermore, when the boiler is operating at high load, the booster pump ensures that the return water flow matches the evaporation rate, preventing boiler water shortages (which could lead to pipe bursts) or overfilling (which could affect steam quality). The feedwater regulating valve dynamically adjusts its opening based on the boiler evaporation rate (e.g., opening the valve wider as load increases) to maintain a stable drum water level (water level fluctuations must be controlled within ±10 mm). Throttling also balances the booster pump outlet pressure with the boiler inlet pressure, preventing overpressure (which could damage pipes) or underpressure (which could lead to insufficient water supply). A feedwater flowmeter provides flow data feedback to the DCS system, interacting with the regulating valve to form a "monitoring-regulation-stabilization" closed loop, ensuring that the flow rate precisely matches the setpoint.

[0042] To further illustrate a multi-machine furnace intermodal system provided in the embodiment of the present application, a two-furnace two-machine mother pipe system is combined with the attached Figure 1 For explanation, #1 represents the equipment of Unit 1, and #2 represents the equipment of Unit 2. Specifically: like Figure 1 As shown, the #1 main steam pipe 13 and the #2 main steam pipe 30 of the #1 boiler 9 and the #2 boiler 11 are merged into the main steam header 1. The main steam header 1 is provided with a main steam isolation valve 2. The main steam isolation valve 2 connects the #1 main steam pipe 13 and the #2 main steam pipe 30. The setting of the main steam isolation valve 2 can physically isolate the corresponding section of the pipeline when a boiler or steam turbine needs to be repaired, thereby facilitating repair. The main steam header 1 is connected to the #1 steam turbine high-pressure cylinder 5 and the #2 steam turbine high-pressure cylinder 7 through the #1 main steam inlet pipe 14 and the #2 main steam inlet pipe 31 respectively. The main steam inlet amount entering the #1 steam turbine high-pressure cylinder 5 and the #2 steam turbine high-pressure cylinder 7 is redistributed through the #1 high-pressure regulating valve 29 of the #1 steam turbine and the #2 high-pressure regulating valve 32 of the #2 steam turbine; The exhaust steam from the high-pressure cylinder 5 of the #1 steam turbine is connected to the #1 boiler reheater via the #1 reheat cold section pipe 16 and the #1 reheater steam inlet pipe 19. The exhaust steam from the high-pressure cylinder 7 of the #2 steam turbine is connected to the #2 boiler reheater via the #2 reheat cold section pipe 33 and the #2 reheater steam inlet pipe 36. The #1 reheat cold section pipe 16 is provided with the #1 high-pressure exhaust regulating valve 22, and the #2 reheat cold section pipe 33 is provided with the #2 high-pressure exhaust regulating valve 39. The #1 reheat cold section pipe 16 is connected to the #1 supplementary steam pipe 45 after the #1 high-pressure exhaust regulating valve 22, and the #2 reheat cold section pipe 33 is connected to the #2 supplementary steam pipe 47 after the #2 high-pressure exhaust regulating valve 39. The regulation target is the high-pressure low value of the two steam turbines. The #1 reheater steam inlet pipe 19 is provided with a #1 reheater inlet regulating valve 25 and a #1 reheater inlet flowmeter 26, and the #2 reheater steam inlet pipe 36 is provided with a #2 reheater inlet regulating valve 42 and a #2 reheater inlet flowmeter 43; A #1 auxiliary reheater 10 is provided between the #1 reheat cold section pipe 16 and the #1 reheat hot section pipe 21 of the #1 boiler 9. A #2 auxiliary reheater 12 is provided between the #2 reheat cold section pipe 33 and the #2 reheat hot section pipe 48 of the #2 boiler. The #1 auxiliary reheater 10 is located before the #1 reheater inlet regulating valve 25 of the #1 boiler and after the #1 boiler reheater outlet (before the steam inlet of the #1 intermediate pressure cylinder 6). The #2 auxiliary reheater 12 is located before the #2 reheater inlet regulating valve 42 of the #2 boiler 11 and after the #2 boiler reheater outlet (before the steam inlet of the #1 intermediate pressure cylinder 8). A #1 auxiliary reheater steam inlet regulating valve 27 is provided on the #1 auxiliary reheater steam inlet pipe 20, and a #2 auxiliary reheater steam inlet regulating valve 44 is provided on the #2 auxiliary reheater steam inlet pipe 37. The steam heated by the #1 boiler reheater and the #2 boiler reheater enters the intermediate pressure cylinder 6 of the #1 steam turbine and the intermediate pressure cylinder 8 of the #2 steam turbine through the #1 reheating hot section pipe 21 and the #2 reheating hot section pipe 38 respectively. The #1 reheating hot section pipe 21 is provided with a #1 extraction pipe 46. The steam inlet end of the #1 extraction pipe is located after the steam outlet end of the #1 auxiliary reheater 10 and before the steam inlet end of the intermediate pressure cylinder 6 of the #1 steam turbine. The #2 reheating hot section pipe 38 is provided with a #2 extraction pipe 48. The inlet end of the #2 extraction pipe 48 is located after the steam outlet end of the #1 auxiliary reheater 10 and before the steam inlet end of the intermediate pressure cylinder 6 of the #1 steam turbine. The steam end is located after the steam outlet of the #2 auxiliary reheater 12 and before the steam inlet of the intermediate pressure cylinder 8 of the #2 steam turbine. When the main steam flow of the boiler of the unit is greater than the steam inlet flow of the high-pressure cylinder of the unit's steam turbine, the supplementary steam pipe on the cold reheating section of the unit is put into use to supplement the low-temperature steam flow into the boiler reheater to prevent the boiler reheater from overheating. At the same time, the steam extraction pipe on the hot reheating section is put into use to prevent the supplementary steam from entering the intermediate pressure cylinder of the unit, ensuring normal steam demand, avoiding excessive pressure in the intermediate pressure cylinder, and realizing flexible operation of the unit. The #1 heat recovery water supply pipe 17 of the #1 boiler 9 and the #2 heat recovery water supply pipe 34 of the #2 boiler 11 converge into the water supply main pipe 4, the water supply main pipe 4 is provided with a water supply isolation valve 3, the #1 heat recovery water supply pipe 17 is provided with a #1 booster pump 15, the #2 heat recovery water supply pipe 34 is provided with a #2 booster pump 28, the water supply main pipe 4 is connected to the #1 boiler 9 through the #1 heat recovery water inlet pipe 18, and the water supply main pipe 4 is connected to the #2 boiler 11 through the #2 heat recovery water inlet pipe 35. At the same time, the #1 heat recovery water inlet pipe 18 is provided with a #1 water supply regulating valve 23 and a #1 water supply flow meter 24, and the #2 heat recovery water inlet pipe 35 is provided with a #2 water supply regulating valve 40 and a #2 water supply flow meter 41, completing the system water supply cycle.

[0043] In summary, the embodiment of the present application provides a multi-machine-boiler interoperation system, which connects the main pipes of the boiler main steam and feed water-related systems. The cylinders of the steam turbines of each unit still operate according to the original system. By setting an adjustable auxiliary reheater, an imbalance between the turbine and the boiler can be allowed, which improves the operational flexibility of the main pipe unit. At the same time, a supplementary steam pipe is installed in the cold section of the reheat pipe. When the steam temperature is too high or too low, the boiler reheater is maintained to operate within the normal temperature range through the supplementary steam pipe. An extraction pipe is installed in the hot section of the reheat pipe to promptly extract the steam during the supplementary steam, thereby avoiding excessive pressure in the intermediate pressure cylinder of the steam turbine. The steam turbine body of this solution has no safety issues. By adapting the boiler and setting the adjustment means, it is possible to achieve decoupling of the machine and boiler, decoupling between the units, and promote the conditions for flexible operation of the units.

[0044] The above description is only a preferred embodiment of the present application and is not intended to limit the present application. Any modifications, equivalent replacements, improvements, etc. made within the spirit and principles of the present application should be included in the scope of protection of the present application.

Claims

1. A multi-machine and furnace intermodal system, characterized in that: It includes multiple boilers and multiple steam turbines. The multiple boilers each collect their main steam pipes into the same main steam header. The multiple steam turbines correspond to the multiple boilers one-to-one, and the main steam header distributes the main steam to the high-pressure cylinder of each steam turbine as needed. The high-pressure cylinder of each steam turbine sends the exhaust steam into the reheater of each boiler through the reheat cold section pipe and the reheater steam inlet pipe. Each of the reheat cold section pipes is provided with a steam supply pipe. The boiler reheater each sends steam into the intermediate pressure cylinder of the steam turbine through the reheat hot section pipe. Each of the reheat hot section pipes is provided with a steam extraction pipe.

2. The multi-machine and furnace intermodal system according to claim 1, characterized in that: A main steam inlet pipe is provided between the main steam main pipe and the high-pressure cylinder of the steam turbine, and a high-pressure regulating valve is provided on the main steam inlet pipe.

3. The multi-machine and furnace intermodal operation system according to claim 1, characterized in that: The reheat cold section pipe is provided with a high discharge check valve.

4. The multi-machine and furnace intermodal system according to claim 1, characterized in that: The reheater steam inlet pipe is provided with a reheater inlet regulating valve and a reheater inlet flow meter.

5. The multi-machine and furnace intermodal operation system according to claim 4, characterized in that: An auxiliary reheater is provided between the reheat cold section pipe and the reheat hot section pipe. The steam inlet pipe of the auxiliary reheater is located before the reheater inlet regulating valve, and the steam outlet pipe of the auxiliary reheater is located after the outlet of the boiler reheater.

6. The multi-machine and furnace intermodal operation system according to claim 5, characterized in that: An auxiliary reheater steam inlet regulating valve is provided on the auxiliary reheater steam inlet pipe.

7. The multi-machine and furnace intermodal operation system according to claim 5, characterized in that: The steam inlet end of the steam extraction pipe is located between the steam outlet end of the auxiliary reheater and the steam inlet end of the intermediate pressure cylinder of the steam turbine.

8. The multi-machine and furnace intermodal operation system according to claim 1, characterized in that: The heat recovery water supply pipes of the plurality of boilers are combined into the same water supply main pipe, and the water supply main pipe supplies water to each boiler as needed through the heat supply water inlet pipe.

9. The multi-machine and furnace intermodal operation system according to claim 8, characterized in that: The heat recovery water supply pipe is provided with a booster pump, and the heat supply water inlet pipe is provided with a water supply regulating valve and a water supply flow meter.

10. The multi-machine and furnace intermodal operation system according to claim 8, characterized in that: The water supply main pipe is provided with a water supply isolation valve, and the water supply isolation valve is located between the heat recovery water supply pipes.

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