High-efficiency steam turbine thermodynamic system and high-efficiency steam turbine thermodynamic system control method

Abstract

The invention relates to an efficient steam turbine thermodynamic system and an efficient steam turbine thermodynamic system control method. The efficient steam turbine thermodynamic system comprises a first medium-low pressure cylinder set and a second medium-low pressure cylinder set which are connected in parallel. The first cylinder group steam admission amount of the first medium-low pressure cylinder group and the second cylinder group steam admission amount of the second medium-low pressure cylinder group are set according to a preset proportion, and the sum of the first cylinder group steam admission amount and the second cylinder group steam admission amount meets the rated working condition use requirement of the efficient steam turbine thermodynamic system; a first cylinder set steam inlet of the first medium-low pressure cylinder set is connected with a reheat steam conveying pipeline of the efficient turbine thermodynamic system through a first reheat steam conveying branch. A second cylinder group steam inlet of the second medium-low pressure cylinder group is connected with the reheat steam conveying pipeline through a second reheat steam conveying branch; a first valve is arranged on the first reheat steam conveying branch and used for adjusting a first steam inlet parameter of the first medium-low pressure cylinder set. By the adoption of the efficient steam turbine thermodynamic system, the wide-load efficiency of the whole unit can be improved.

Description

Technical Field

[0001] The present application relates to the technical field of generator sets, and in particular to a high-efficiency steam turbine thermal system and a high-efficiency steam turbine thermal system control method. Background Art

[0002] Power generation from coal-fired power plants is a complex energy conversion process involving the interconversion of multiple energy forms. The steam turbine in a high-efficiency steam turbine thermal system is a crucial component of coal-fired power plants' energy conversion, and its operating efficiency and performance directly impact the overall efficiency and performance of the unit. The steam turbine's cylinders are divided into high-pressure, intermediate-pressure, and low-pressure cylinders based on the steam inlet parameters. In actual operation, the high-pressure cylinder uses the main steam to perform work, and the exhaust steam enters the boiler reheater for heating before entering the intermediate-pressure cylinder to perform work. The exhaust steam from the intermediate-pressure cylinder then enters the low-pressure cylinder to perform work.

[0003] Traditional turbine units are typically built with maximum power generation as the goal, so the turbine's intermediate and low-pressure cylinders are typically designed based on rated operating conditions. However, with the development of renewable energy and the construction of new power systems, coal-fired power is gradually shifting towards regulating and supporting power sources. Large-inlet ultra-supercritical units generally operate at medium and low loads, unable to fully utilize the advantages of high efficiency at rated load. Therefore, how to improve the operating efficiency of the turbine's intermediate and low-pressure cylinders under various load conditions, thereby improving the wide-load efficiency of the entire unit, is a pressing issue for current generator sets. Summary of the Invention

[0004] Based on this, it is necessary to provide a high-efficiency steam turbine thermal system and a high-efficiency steam turbine thermal system control method that can improve the wide-load efficiency of the entire unit in response to the above technical problems.

[0005] In a first aspect, the present application provides a high-efficiency steam turbine thermal system, the high-efficiency steam turbine thermal system comprising: a first intermediate and low-pressure cylinder group and a second intermediate and low-pressure cylinder group connected in parallel;

[0006] The steam intake amount of the first cylinder group of the first intermediate and low-pressure cylinder group and the steam intake amount of the second cylinder group of the second intermediate and low-pressure cylinder group are set according to a preset ratio, and the steam intake amount of the first cylinder group and the steam intake amount of the second cylinder group meet the rated operating condition requirements of the high-efficiency steam turbine thermal system;

[0007] The first cylinder group steam inlet of the first intermediate and low pressure cylinder group is connected to the reheat steam delivery pipeline of the high-efficiency steam turbine thermal system through a first reheat steam delivery branch; the second cylinder group steam inlet of the second intermediate and low pressure cylinder group is connected to the reheat steam delivery pipeline through a second reheat steam delivery branch;

[0008] The first reheat steam delivery branch is provided with a first valve for adjusting the first steam inlet parameters of the first intermediate and low pressure cylinder groups.

[0009] In a second aspect, the present application also provides a method for controlling a high-efficiency steam turbine thermal system. The method comprises:

[0010] Obtaining operating condition information of the high-efficiency steam turbine thermal system;

[0011] When it is determined based on the operating condition information that the high-efficiency steam turbine thermal system is in a rated operating condition, controlling a first valve of the high-efficiency steam turbine thermal system to be at a maximum opening;

[0012] If the high-efficiency steam turbine thermal system is not in the rated operating condition, determining an operating condition range of the high-efficiency steam turbine thermal system based on the operating condition information; the operating condition range is determined based on a first matching load condition corresponding to the steam intake of the first cylinder group and a second matching load condition corresponding to the steam intake of the second cylinder group;

[0013] Based on the operating condition range, the valve opening of the first valve in the high-efficiency steam turbine thermal system is adjusted.

[0014] The above-mentioned high-efficiency steam turbine thermal system and high-efficiency steam turbine thermal system control method, the high-efficiency steam turbine thermal system includes a first medium-low pressure cylinder group and a second medium-low pressure cylinder group connected in parallel, the first medium-low pressure cylinder group is connected to the reheat steam transmission pipeline through a first reheat steam transmission branch, and the second medium-low pressure cylinder group is connected to the reheat steam transmission pipeline through a second reheat steam transmission branch, wherein a first valve is provided on the first reheat steam transmission branch, and the first steam inlet parameter of the first medium-low pressure cylinder group can be adjusted by adjusting the valve opening of the first valve. Since the steam inlet volume of the first cylinder group and the steam inlet volume of the second cylinder group meet the rated operating conditions of the high-efficiency steam turbine thermal system, when the high-efficiency steam turbine thermal system is operating at the rated operating conditions, the valve opening of the first valve can be adjusted to a fully open opening, so that both the first medium-low pressure cylinder group and the second medium-low pressure cylinder group can achieve the best energy conversion efficiency. When the operating conditions of the high-efficiency steam turbine thermal system begin to decline, the valve opening of the first valve can be adjusted to maintain the high energy conversion efficiency of the second intermediate and low-pressure cylinder group by reducing the steam intake of the first intermediate and low-pressure cylinder group, thereby improving the energy conversion efficiency of the overall intermediate and low-pressure cylinder group, and further achieving high efficiency in wide-load operation of the high-efficiency steam turbine thermal system. BRIEF DESCRIPTION OF THE DRAWINGS

[0015] Figure 1 A schematic structural diagram of a high-efficiency steam turbine thermal system in one embodiment;

[0016] Figure 2 A schematic structural diagram of a high-efficiency steam turbine thermal system in another embodiment;

[0017] Figure 3A schematic structural diagram of a high-efficiency steam turbine thermal system in another embodiment;

[0018] Figure 4 A schematic structural diagram of a high-efficiency steam turbine thermal system in another embodiment;

[0019] Figure 5 A schematic structural diagram of a high-efficiency steam turbine thermal system in another embodiment;

[0020] Figure 6 A schematic structural diagram of a high-efficiency steam turbine thermal system in another embodiment;

[0021] Figure 7 1 is a flow chart of a method for controlling a high-efficiency steam turbine thermal system in one embodiment;

[0022] Figure 8 A schematic flow chart of a method for controlling a high-efficiency steam turbine thermal system in another embodiment;

[0023] Figure 9 is a structural block diagram of a high-efficiency steam turbine thermal system control device in one embodiment;

[0024] Figure 10 FIG. 1 is a diagram showing the internal structure of a computer device in one embodiment.

[0025] Description of Figure Numbers:

[0026] First intermediate and low-pressure cylinder group 101; second intermediate and low-pressure cylinder group 102; reheat steam delivery pipeline 103; heat recovery assembly 104; first cylinder group steam inlet 1011; first reheat steam delivery branch 1012; first valve 1013; first intermediate-pressure cylinder 1014; first low-pressure cylinder group 1015; first intermediate-pressure exhaust port 1016; first low-pressure steam inlet 1017; first intermediate-pressure exhaust pipeline 1018; first intermediate-pressure steam inlet 1019; first low-pressure exhaust port 10110; first low-pressure exhaust pipeline 10111; second valve 10112; second cylinder Group steam inlet 1021; second reheat steam delivery branch 1022; second intermediate-pressure cylinder 1023; second low-pressure cylinder group 1024; second intermediate-pressure exhaust port 1025; second low-pressure steam inlet 1026; second intermediate-pressure exhaust pipe 1027; second intermediate-pressure steam inlet 1028; second low-pressure exhaust port 1029; second low-pressure exhaust pipe 10210; third valve 10211; fourth valve 10212; first low-pressure heater 1041; second low-pressure heater 1042; third low-pressure heater 1043; fourth low-pressure heater 1044. DETAILED DESCRIPTION

[0027] In order to make the purpose, technical solutions and advantages of this application more clear, the following further describes this application in detail with reference to the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are only used to explain this application and are not intended to limit this application.

[0028] In the steam turbine of the traditional high-efficiency steam turbine thermal system, an intermediate-pressure cylinder is usually set up to connect to a low-pressure cylinder for operation. The exhaust steam of the intermediate-pressure cylinder is input into the low-pressure cylinder to continue to do work. All the reheated steam generated by the high-efficiency steam turbine thermal system will enter the only intermediate-pressure cylinder, expand in the intermediate-pressure cylinder to do work, drive the turbine rotor to operate, and perform energy conversion.

[0029] Since traditional high-efficiency steam turbine thermal systems are usually built with the goal of increasing power generation, the rated operating conditions are usually used as the design benchmark for the intermediate and low-pressure cylinders of the steam turbine. That is, the intermediate and low-pressure cylinders in traditional steam turbines can only maintain high-efficiency energy conversion under rated operating conditions. Under medium and low load conditions, the reheated steam parameters generated by the high-efficiency steam turbine thermal system do not match the design values corresponding to the rated operating conditions, such as reduced steam inlet flow and lower steam inlet pressure. This will lead to a decrease in the energy conversion efficiency of the intermediate and low-pressure cylinders, which is one of the reasons for the increase in coal consumption of coal-fired power units under medium and low load conditions.

[0030] In order to improve the operating efficiency of the medium and low pressure cylinders of the steam turbine under various load conditions, and thus improve the wide load efficiency of the entire unit, such as Figure 1 As shown, the present application provides a high-efficiency steam turbine thermal system, which includes: a first intermediate and low-pressure cylinder group 101 and a second intermediate and low-pressure cylinder group 102 connected in parallel.

[0031] The steam intake amount of the first cylinder group of the first intermediate and low pressure cylinder group 101 and the steam intake amount of the second cylinder group of the second intermediate and low pressure cylinder group 102 are set according to a preset ratio, and the steam intake amount of the first cylinder group and the second cylinder group meet the rated operating requirements of the high-efficiency steam turbine thermal system.

[0032] A first cylinder steam inlet 1011 of the first intermediate and low-pressure cylinder group 101 is connected to the reheat steam delivery pipeline 103 of the high-efficiency steam turbine thermal system via a first reheat steam delivery branch 1012. A second cylinder steam inlet 1021 of the second intermediate and low-pressure cylinder group 102 is connected to the reheat steam delivery pipeline 103 via a second reheat steam delivery branch 1022. A first valve 1013 is provided on the first reheat steam delivery branch 1012 for adjusting the first steam inlet parameters of the first intermediate and low-pressure cylinder group 101.

[0033] The intermediate and low-pressure cylinder groups are energy conversion devices that use reheated steam generated by a high-efficiency steam turbine thermal system to perform work, achieving energy conversion. The first intermediate and low-pressure cylinder group 101 is formed by a first intermediate-pressure cylinder and a first low-pressure cylinder connected in series, while the second intermediate and low-pressure cylinder group 102 is formed by a second intermediate-pressure cylinder and a second low-pressure cylinder connected in series.

[0034] The first cylinder group steam intake rate of the first intermediate and low-pressure cylinder group 101 refers to the designed steam intake rate of the first intermediate and low-pressure cylinder group 101, that is, the corresponding reheat steam intake rate that needs to pass through the first intermediate and low-pressure cylinder group 101 when the first intermediate and low-pressure cylinder group 101 achieves the optimal energy conversion efficiency. The second cylinder group steam intake rate of the second intermediate and low-pressure cylinder group 102 refers to the designed steam intake rate of the second intermediate and low-pressure cylinder group 102, that is, the corresponding reheat steam intake rate that needs to pass through the second intermediate and low-pressure cylinder group 102 when the second intermediate and low-pressure cylinder group 102 achieves the optimal energy conversion efficiency.

[0035] Among them, the sum of the steam intake of the first cylinder group and the steam intake of the second cylinder group meets the rated operating condition use demand of the high-efficiency steam turbine thermal system, which means that when the high-efficiency steam turbine thermal system is operating at the rated operating condition, the first intermediate and low-pressure cylinder group 101 and the second intermediate and low-pressure cylinder group 102 can receive all the reheated steam generated by the high-efficiency steam turbine thermal system. When designing the thermal system, the energy conversion efficiency of the high-efficiency steam turbine thermal system under the rated operating condition can be guaranteed by ensuring that the sum of the steam intake of the first cylinder group and the steam intake of the second cylinder group meets the rated operating condition use demand of the high-efficiency steam turbine thermal system. It can be understood that the specific design scheme of the steam intake of the first cylinder group and the second cylinder group can be determined according to the actual use of the high-efficiency steam turbine thermal system.

[0036] In one embodiment, the relationship between the steam inlet volume of the first and second cylinder groups is expressed as a ratio. The steam inlet ratio of the first and second intermediate and low-pressure cylinder groups 101, 102 can be designed based on the length of time the coal-fired power unit operates at medium and low loads in the location where the unit is located. For example, if the unit actually operates at 40% load for a significant period of time, the steam inlet ratio of the first and second intermediate and low-pressure cylinder groups 101, 102 can be set to 4:6, i.e., the steam inlet volume of the first cylinder group is 40% of the total reheat steam generated by the unit under rated conditions, and the steam inlet volume of the second cylinder group is 60% of the total reheat steam generated by the unit under rated conditions. For another example, if the unit actually operates at 30% load for a significant period of time, the steam inlet ratio of the first and second intermediate and low-pressure cylinder groups 101, 102 can be set to 3:7, i.e., the steam inlet volume of the first cylinder group is 30% of the total reheat steam generated by the unit under rated conditions, and the steam inlet volume of the second cylinder group is 70% of the total reheat steam generated by the unit under rated conditions. The steam intake ratio of the first cylinder group to the second cylinder group can be 1:9, 2:8, 3:7, 4:6, 5:5, etc.

[0037] The reheated steam delivery pipeline 103 is a main gas transmission pipeline for transmitting reheated steam. The steam inlet end of the reheated steam delivery pipeline 103 can be connected to a reheated steam generation source in the high-efficiency steam turbine thermal system, such as a boiler reheater, to receive the reheated steam generated by the reheater. The first reheated steam delivery branch 1012 is a steam delivery pipeline for transmitting reheated steam to the first intermediate and low-pressure cylinder group 101. The first cylinder group steam inlet 1011 of the first intermediate and low-pressure cylinder group 101 can be connected to the reheated steam delivery pipeline 103 via the first reheated steam delivery branch 1012, so that the reheated steam can be transmitted to the first intermediate and low-pressure cylinder group 101 for energy conversion. The second reheat steam delivery branch 1022 is a steam delivery pipeline for delivering reheat steam to the second intermediate and low pressure cylinder group 102. The rear second cylinder group steam inlet 1021 of the second intermediate and low pressure cylinder group 102 can be connected to the reheat steam delivery pipeline 103 through the second reheat steam delivery branch 1022, so that the reheat steam can be delivered to the second intermediate and low pressure cylinder group 102 for energy conversion.

[0038] Among them, a first valve 1013 is provided on the first reheat steam delivery branch 1012 for adjusting the first steam inlet parameters of the first intermediate and low pressure cylinder group 101. The first steam inlet parameters are parameter information used to characterize the transmission of reheat steam into the first intermediate and low pressure cylinder group 101. The first steam inlet parameters may include the steam inlet volume and / or steam inlet pressure of the reheat steam. By providing the first valve 1013 on the first reheat steam delivery branch 1012, when the operating load of the high-efficiency steam turbine thermal system changes, the reheat steam inlet parameters of the first intermediate and low pressure cylinder group 101 can be adjusted according to the operating load change.

[0039] Specifically, when the operating condition of the high-efficiency steam turbine thermal system is the rated operating condition, the opening of the first valve can be adjusted to fully open, and the reheated steam enters the first intermediate and low-pressure cylinder group 101 and the second intermediate and low-pressure cylinder group 102 respectively, and both cylinder groups can achieve optimal energy conversion efficiency.

[0040] When the operating conditions of the high-efficiency steam turbine thermal system start to reduce the load from the rated operating conditions, the opening of the first valve 1013 can be reduced according to the decrease in the operating load, thereby reducing the steam intake of the first intermediate and low-pressure cylinder group 101 and ensuring the steam intake of the second intermediate and low-pressure cylinder group 102. Compared with the traditional single intermediate and low-pressure cylinder group, the energy conversion efficiency of the entire intermediate and low-pressure cylinder group can be effectively improved, thereby achieving high efficiency in wide-load operation of the high-efficiency steam turbine thermal system.

[0041] Taking the steam intake ratio of the first cylinder group to the second cylinder group as 4:6 as an example, the operation of the first intermediate and low-pressure cylinder group 101 and the second intermediate and low-pressure cylinder group 102 under different load conditions is explained.

[0042] When the operating condition of the high-efficiency steam turbine thermal system is the rated operating condition, the opening of the first valve is adjusted to fully open, and the reheated steam enters the first intermediate and low-pressure cylinder group 101 and the second intermediate and low-pressure cylinder group 102 respectively. At this time, the steam intake amount of the first cylinder group of the first intermediate and low-pressure cylinder 101 is 40%, and the steam intake amount of the second cylinder group of the second intermediate and low-pressure cylinder group 102 is 60%. Both cylinder groups can achieve the best energy conversion efficiency.

[0043] When the operating conditions of the high-efficiency steam turbine thermal system start to reduce the load from the rated operating conditions, the opening of the first valve 1013 can be reduced according to the reduction of the operating load, so as to reduce the steam intake of the first intermediate and low-pressure cylinder group 101 and ensure the steam intake of the second intermediate and low-pressure cylinder group 102. When the coal-fired power unit operates in the load range of 100%-60%, the second intermediate and low-pressure cylinder group 102 can always maintain the rated operating steam intake and operate with the best energy conversion efficiency. When the coal-fired power unit operates to a load below 60%, the energy conversion efficiency of the second intermediate and low-pressure cylinder group 102 will also be higher than that of the traditional intermediate and low-pressure cylinder group.

[0044] The above-mentioned high-efficiency steam turbine thermal system includes a first intermediate- and low-pressure cylinder group and a second intermediate- and low-pressure cylinder group connected in parallel. The first intermediate- and low-pressure cylinder group is connected to the reheat steam transmission pipeline via a first reheat steam transmission branch, and the second intermediate- and low-pressure cylinder group is connected to the reheat steam transmission pipeline via a second reheat steam transmission branch. A first valve is provided on the first reheat steam transmission branch, and a first steam inlet parameter of the first intermediate- and low-pressure cylinder group can be adjusted by adjusting the valve opening of the first valve. Because the steam inlet volume of the first cylinder group and the steam inlet volume of the second cylinder group meet the rated operating requirements of the high-efficiency steam turbine thermal system, when the high-efficiency steam turbine thermal system is operating at rated operating conditions, the valve opening of the first valve can be adjusted to a fully open position, so that both the first intermediate- and low-pressure cylinder group and the second intermediate- and low-pressure cylinder group can achieve optimal energy conversion efficiency. When the operating conditions of the high-efficiency steam turbine thermal system begin to decline, the valve opening of the first valve can be adjusted to maintain the high energy conversion efficiency of the second intermediate and low-pressure cylinder group by reducing the steam intake of the first intermediate and low-pressure cylinder group, thereby improving the energy conversion efficiency of the overall intermediate and low-pressure cylinder group, and further achieving high efficiency in wide-load operation of the high-efficiency steam turbine thermal system.

[0045] In one embodiment, Figure 2 As shown, the first intermediate- and low-pressure cylinder group 101 includes a first intermediate-pressure cylinder 1014 and a first low-pressure cylinder group 1015 , and the second intermediate- and low-pressure cylinder group 102 includes a second intermediate-pressure cylinder 1023 and a second low-pressure cylinder group 1024 .

[0046] The first intermediate pressure exhaust port 1016 of the first intermediate pressure cylinder 1014 is connected to the first low pressure steam inlet 1017 of the first low pressure cylinder group 1015 via a first intermediate pressure exhaust pipe 1018. The second intermediate pressure exhaust port 1025 of the second intermediate pressure cylinder 1023 is connected to the second low pressure steam inlet 1026 of the second low pressure cylinder group 1024 via a second intermediate pressure exhaust pipe 1027.

[0047] The first intermediate pressure steam inlet 1019 of the first intermediate pressure cylinder 1014 is connected to the reheat steam delivery pipeline 103 of the high-efficiency steam turbine thermal system via the first reheat steam delivery branch 1012. The second intermediate pressure steam inlet 1028 of the second intermediate pressure cylinder 1023 is connected to the reheat steam delivery pipeline 103 via the second reheat steam delivery branch 1022.

[0048] Specifically, by connecting the first intermediate-pressure cylinder with the first low-pressure cylinder group and connecting the second intermediate-pressure cylinder with the second low-pressure cylinder group, the first intermediate-pressure cylinder and the first low-pressure cylinder group constituted by the first intermediate-pressure cylinder and the first low-pressure cylinder group can be independent of each other when exhausting steam and the second intermediate-pressure cylinder and the second low-pressure cylinder group constituted by the second intermediate-pressure cylinder and the second low-pressure cylinder group. The exhaust steam of the first intermediate-pressure cylinder will only enter the first low-pressure cylinder group, and the exhaust steam of the second intermediate-pressure cylinder will only enter the second low-pressure cylinder group. The steam between the two cylinder groups does not mix, and the steam inlet ratio can be adjusted, thereby realizing the high efficiency of wide-load operation of the high-efficiency steam turbine thermal system.

[0049] In one embodiment, the first intermediate pressure cylinder, the second intermediate pressure cylinder, the first low pressure cylinder group and the second low pressure cylinder group in the high efficiency steam turbine thermal system are arranged on the same axis.

[0050] Specifically, the first intermediate pressure cylinder, the second intermediate pressure cylinder, the first low pressure cylinder group and the second low pressure cylinder group are arranged on the same axis. The entire high-efficiency steam turbine thermal system can operate the unit with only a single generator, effectively reducing the complexity of the unit layout.

[0051] In one embodiment, Figure 3 As shown, the high-efficiency steam turbine thermal system further includes: a heat recovery component 104 for extracting low-pressure exhaust steam from the first low-pressure cylinder group 1015 and the second low-pressure cylinder group 1024 to heat boiler feed water.

[0052] The first low-pressure exhaust port 10110 of the first low-pressure cylinder group 1015 is connected to the heat recovery component 104 through a first low-pressure exhaust pipe 10111 ; the second low-pressure exhaust port 1029 of the second low-pressure cylinder group 1024 is connected to the heat recovery component 104 through a second low-pressure exhaust pipe 10210 .

[0053] Among them, the heat recovery component 104 can extract part of the steam that has done work from the first low-pressure cylinder group 1015 and the second low-pressure cylinder group 1024 to heat the condensate. This process is called feedwater heat recovery heating, and the corresponding steam cycle is called feedwater heat recovery cycle.

[0054] Specifically, during the operation of the high-efficiency steam turbine thermal system, the heat recovery component 104 can extract part of the steam that has already done work from the first low-pressure cylinder group 1015 through the first low-pressure exhaust pipe 10111, and at the same time extract part of the steam that has already done work from the second low-pressure cylinder group 1024 through the second low-pressure exhaust pipe 10210. The extracted steam is used to heat the feed water in the heat recovery component 104 to increase the temperature of the feed water entering the boiler.

[0055] In the above embodiment, by providing a heat recovery assembly connected to each of the first and second low-pressure cylinder groups, thermal energy can be more fully utilized, cooling losses can be reduced, and the efficiency of the entire thermal cycle can be improved. Furthermore, by extracting a portion of steam from the first and second low-pressure cylinder groups for heat recovery, the amount of steam entering the condenser of the high-efficiency steam turbine thermal system can be reduced, lowering the condenser's heat load. This reduces steam erosion and damage to the condenser equipment, thereby extending the service life of the equipment associated with the high-efficiency steam turbine thermal system.

[0056] Further, such as Figure 4 As shown, in one embodiment, a second valve 10112 is provided on the first low-pressure exhaust steam pipeline 10111 for controlling the on-off of the first low-pressure exhaust steam pipeline 10111 .

[0057] Specifically, in actual use, if the operating conditions of the high-efficiency steam turbine thermal system have been reduced to the point where it is necessary to cut off the first intermediate and low-pressure cylinder group to maintain the steam intake of the second intermediate and low-pressure cylinder group, the first intermediate and low-pressure cylinder group can be cut off. At this time, in order to reduce the probability of damage to the heat recovery component, it is necessary to set a second valve 10112 on the first low-pressure exhaust pipe 10111. When it is necessary to cut off the first intermediate and low-pressure cylinder group, it is only necessary to adjust the valve opening of the first valve 1013 to the valve opening corresponding to the zero output or micro-output state, and close the second valve 10112 to achieve cylinder cutting and continue to maintain the energy conversion efficiency of the second intermediate and low-pressure cylinder group.

[0058] Taking the steam intake ratio of the first cylinder group to the second cylinder group as 4:6 as an example, when the operating condition of the high-efficiency steam turbine thermal system is 60% load condition, in order to enable the second intermediate and low-pressure cylinder group to maintain the optimal energy conversion efficiency, it is necessary to adjust the valve opening of the first valve 1013 to the valve opening corresponding to the zero output or micro-output state, and at the same time close the second valve 10112 to realize the cylinder cutting processing of the first intermediate and low-pressure cylinder group, so that all the reheated steam enters the second intermediate and low-pressure cylinder group to perform work.

[0059] In the above embodiment, by providing a second valve on the first low-pressure exhaust pipe, the on-off of the first low-pressure exhaust pipe can be accurately controlled, and the cylinder cutting processing of the first intermediate and low-pressure cylinder group can be realized when necessary, so as to stably maintain the energy conversion efficiency of the second intermediate and low-pressure cylinder group, thereby realizing the high efficiency of wide-load operation of the high-efficiency steam turbine thermal system.

[0060] In one embodiment, Figure 5 As shown, the steam intake of the second cylinder group is greater than that of the first cylinder group. A third valve 10211 is provided on the second reheat steam delivery branch 1022 for adjusting the second steam intake parameters of the second intermediate and low-pressure cylinder groups 102. A fourth valve 10212 is provided on the second low-pressure exhaust steam pipe 10210 for controlling the on / off state of the second low-pressure exhaust steam pipe 10210.

[0061] Specifically, when the steam intake amount of the second cylinder group is greater than that of the first cylinder group, in order to further improve the overall energy conversion efficiency of the unit, a third valve 10211 can be set on the second reheat steam delivery branch 1022 to adjust the second steam intake parameters of the second medium and low pressure cylinder group 102, and at the same time, a fourth valve 10212 can be set on the second low pressure exhaust pipe 10210 to control the on and off of the second low pressure exhaust pipe 10210.

[0062] During actual operation, when the operating conditions of the high-efficiency steam turbine thermal system are reduced to the point where the total amount of reheated steam can only meet the operation of the first intermediate and low-pressure cylinder group 101 at the optimal energy conversion efficiency, or cannot meet the operation of the first intermediate and low-pressure cylinder group 101 at the optimal energy conversion efficiency, the second intermediate and low-pressure cylinder group 102 can be cut off at this time, and all the reheated steam can be transported to the first intermediate and low-pressure cylinder group 101 to perform work. By maintaining the energy conversion efficiency of the first intermediate and low-pressure cylinder group 101 to the greatest extent, the overall operating efficiency of the high-efficiency steam turbine thermal system can be improved.

[0063] Taking the steam intake ratio of the first cylinder group to the second cylinder group as 4:6 as an example, when the operating condition of the high-efficiency steam turbine thermal system is 60% load condition, the valve opening of the first valve 1013 can be adjusted to the valve opening corresponding to the zero output or micro-output state, and the second valve 10112 can be closed to realize the cylinder cutting processing of the first intermediate and low pressure cylinder group 101, so that all the reheated steam enters the second intermediate and low pressure cylinder group 102 to perform work.

[0064] During the process of decreasing the operating conditions of the high-efficiency steam turbine thermal system from a 60% load condition to a 40% load condition, it can be considered that even if all the reheated steam is input into the second intermediate and low-pressure cylinder group 102 to perform work, it is impossible to achieve the second intermediate and low-pressure cylinder group 102 operating at the optimal energy conversion efficiency, and the first intermediate and low-pressure cylinder group 102 is also unable to handle all the steam. Therefore, there are two steam intake methods in this process. The first method is to close the second valve 10112, adjust the valve opening of the first valve 1013 to the valve opening corresponding to the zero output or low output state, adjust the third valve 10211 to fully open, and open the fourth valve 10212 to implement the cylinder cutting process of the first intermediate and low-pressure cylinder group 101, so that all the reheated steam enters the second intermediate and low-pressure cylinder group 102 to perform work, thereby reducing the impact of the reduced steam volume on the energy conversion efficiency of the second intermediate and low-pressure cylinder group 102. The second method is to adjust the first valve 1013 to be fully opened, and at the same time open the second valve 10112, so that the first intermediate and low pressure cylinder group 101 is fully filled with steam, and the third valve 10211 is adjusted according to the valve opening of the third valve 10211 determined according to the remaining steam amount, and at the same time open the fourth valve 10212, so that the reheated steam enters the first intermediate pressure cylinder first, and the remaining steam enters the second intermediate pressure cylinder, so as to maintain the rated steam intake of the first intermediate pressure cylinder.

[0065] When the operating condition of the high-efficiency steam turbine thermal system is 40% load condition or below, the valve opening of the first valve 1013 and the second valve 10112 is kept unchanged, and then the valve opening of the third valve 10211 is adjusted to the valve opening corresponding to the zero output or micro output state, and the fourth valve is closed to realize the cylinder cutting processing of the second medium and low pressure cylinder.

[0066] In the above embodiment, by providing a third valve on the second reheat steam delivery branch and a fourth valve on the second low-pressure exhaust pipe, the second intermediate and low-pressure cylinder groups can be cut off when necessary, thereby stably maintaining the energy conversion efficiency of the first intermediate and low-pressure cylinder groups, thereby achieving high efficiency in wide-load operation of the high-efficiency steam turbine thermal system.

[0067] In one embodiment, the heat recovery assembly includes a first low-pressure heater, a second low-pressure heater, a third low-pressure heater, and a fourth low-pressure heater. The first low-pressure heater, the second low-pressure heater, the third low-pressure heater, and the fourth low-pressure heater are sequentially connected via a feedwater channel, and the steam extraction temperatures of the first low-pressure heater, the second low-pressure heater, the third low-pressure heater, and the fourth low-pressure heater decrease in sequence.

[0068] Specifically, the first, second, third, and fourth low-pressure heaters are connected in sequence via a feedwater channel, and the steam extraction temperatures of the first, second, third, and fourth low-pressure heaters decrease in sequence. Therefore, after the fourth low-pressure heater heats the condensate, it can deliver the heated feedwater to the third low-pressure heater via the feedwater channel. The third low-pressure heater then reheats the feedwater using the extracted steam and delivers the reheated feedwater to the second low-pressure heater via the feedwater channel. The second low-pressure heater also reheats the feedwater using the extracted steam and delivers the reheated feedwater to the first low-pressure heater via the feedwater channel. After heating the feedwater using the extracted steam, the first low-pressure heater can deliver the heated feedwater to the deaerator of the high-efficiency steam turbine thermal system for treatment.

[0069] In the above embodiment, by setting low-pressure heaters with different extraction steam temperatures, a multi-stage heat recovery system is formed, which can achieve cascade utilization of thermal energy, reduce energy loss, and improve the overall cycle thermal efficiency of the unit.

[0070] There are many ways to connect each low-pressure heater to the first and second intermediate- and low-pressure cylinder groups. The following examples illustrate possible connection methods:

[0071] In one embodiment, the first low-pressure heater, the second low-pressure heater, the third low-pressure heater and the fourth low-pressure heater can be connected to the first intermediate and low-pressure cylinder group and the second intermediate and low-pressure cylinder group at the same time. In actual use, steam of corresponding temperature can be extracted from the first intermediate and low-pressure cylinder group and the second intermediate and low-pressure cylinder group for energy utilization.

[0072] In one embodiment, the first low-pressure exhaust port is connected to the first low-pressure heater and the second low-pressure heater via a first low-pressure exhaust pipe, and the second low-pressure exhaust port is connected to the third low-pressure heater and the fourth low-pressure heater via a second low-pressure exhaust pipe.

[0073] Alternatively, the first low-pressure steam exhaust port is connected to the third low-pressure heater and the fourth low-pressure heater via a first low-pressure steam exhaust pipe, and the second low-pressure steam exhaust port is connected to the first low-pressure heater and the second low-pressure heater via a second low-pressure steam exhaust pipe.

[0074] Specifically, the first intermediate and low pressure cylinder group can be connected to the first and second low pressure heaters via the first low pressure exhaust pipe, and the second intermediate and low pressure cylinder group can be connected to the third and fourth low pressure heaters via the second low pressure exhaust pipe.

[0075] Alternatively, the second low-pressure cylinder group can be connected to the first and second low-pressure heaters via the first low-pressure exhaust pipe, and the first intermediate and low-pressure cylinder group can be connected to the third and fourth low-pressure heaters via the second low-pressure exhaust pipe.

[0076] The above two connection methods both connect one cylinder group to two consecutive low-pressure heaters, which can ensure the continuity of the steam temperature extracted from the low-pressure cylinder group.

[0077] In one embodiment, the first low-pressure exhaust port is connected to the first low-pressure heater and the third low-pressure heater through a first low-pressure exhaust pipe; the second low-pressure exhaust port is connected to the second low-pressure heater and the fourth low-pressure heater through a second low-pressure exhaust pipe.

[0078] Alternatively, the first low-pressure exhaust port is connected to the second low-pressure heater and the fourth low-pressure heater through a first low-pressure exhaust pipe; the second low-pressure exhaust port is connected to the first low-pressure heater and the third low-pressure heater through a second low-pressure exhaust pipe.

[0079] Specifically, the first intermediate and low-pressure cylinder group can be connected to the first and third low-pressure heaters via the first low-pressure exhaust pipe, and the second intermediate and low-pressure cylinder group can be connected to the second and fourth low-pressure heaters via the second low-pressure exhaust pipe. Alternatively, the second intermediate and low-pressure cylinder group can be connected to the first and third low-pressure heaters via the first low-pressure exhaust pipe, and the first intermediate and low-pressure cylinder group can be connected to the second and fourth low-pressure heaters via the second low-pressure exhaust pipe.

[0080] Both of the above connection methods are to connect a group of cylinder groups to two spaced low-pressure heaters by jumper connection, which can ensure the balance of steam temperature extracted from the low-pressure cylinder group.

[0081] In one embodiment, the second low-pressure exhaust port is connected to the first low-pressure heater and any one low-pressure heater except the first low-pressure heater through a second low-pressure exhaust pipe.

[0082] Specifically, during actual operation, the probability of cylinder cutting of the first intermediate and low-pressure cylinder group will be greater than the probability of cylinder cutting of the second intermediate and low-pressure cylinder group. When the first intermediate and low-pressure cylinder group is cut off, the first low-pressure exhaust pipe will also be cut off. Therefore, in order to improve the utilization rate of steam exhaust, the second intermediate and low-pressure cylinder group with a lower probability of cylinder cutting is connected to the first low-pressure heater through the second low-pressure exhaust pipe. This can improve the utilization rate of the first low-pressure heater during actual operation, extract higher temperature steam to heat the feed water, effectively improve energy utilization, and thereby improve the overall operating efficiency of the high-efficiency steam turbine thermal system.

[0083] In one embodiment, Figure 6 As shown, a high-efficiency steam turbine thermal system 600 is provided, including a first intermediate pressure cylinder 1014, a first low pressure cylinder group 1015, a second intermediate pressure cylinder 1023, a second low pressure cylinder group 1024, a reheat steam delivery pipeline 103, a first low pressure heater 1041, a second low pressure heater 1042, a third low pressure heater 1043 and a fourth low pressure heater 1044.

[0084] Among them, the ratio of the steam intake volume of the first cylinder group to the steam intake volume of the second cylinder group is 4:6, and the steam intake volume of the first cylinder group and the steam intake volume of the second cylinder group meet the rated operating requirements of the high-efficiency steam turbine thermal system.

[0085] The first intermediate-pressure exhaust port of the first intermediate-pressure cylinder is connected to the first low-pressure inlet of the first low-pressure cylinder group via a first intermediate-pressure exhaust pipe. The second intermediate-pressure exhaust port of the second intermediate-pressure cylinder is connected to the second low-pressure inlet of the second low-pressure cylinder group via a second intermediate-pressure exhaust pipe. The first intermediate-pressure inlet of the first intermediate-pressure cylinder is connected to the reheat steam pipeline of the high-efficiency steam turbine thermal system via a first reheat steam supply branch; the second intermediate-pressure inlet of the second intermediate-pressure cylinder is connected to the reheat steam pipeline via a second reheat steam supply branch.

[0086] A first valve is provided on the first reheat steam delivery branch for adjusting the first steam inlet parameter of the first medium and low pressure cylinder group. A third valve is provided on the second reheat steam delivery branch for adjusting the second steam inlet parameter of the second medium and low pressure cylinder group.

[0087] The first low-pressure steam exhaust port of the first low-pressure cylinder group is connected to the second and fourth low-pressure heaters via a first low-pressure steam exhaust pipe. The second low-pressure steam exhaust port of the second low-pressure cylinder group is connected to the first and third low-pressure heaters via a second low-pressure steam exhaust pipe. A second valve is provided on the first low-pressure steam exhaust pipe to control the flow of the first low-pressure steam exhaust pipe. A fourth valve is provided on the second low-pressure steam exhaust pipe to control the flow of the second low-pressure steam exhaust pipe.

[0088] Specifically, when the high-efficiency steam turbine thermal system operates at rated conditions, the first valve and the third valve are adjusted to a fully open state. At this time, steam is fully introduced into the first intermediate pressure cylinder and the second intermediate pressure cylinder, both meeting the optimal energy conversion efficiency.

[0089] When the operating conditions of the high-efficiency steam turbine thermal system start to reduce the load from the rated operating conditions, the valve opening of the first valve is reduced to reduce the reheat steam flow and pressure entering the first intermediate pressure cylinder. At the same time, the steam flow and pressure entering the second intermediate pressure cylinder are maintained at a state consistent with the rated operating conditions until the operating conditions are reduced from 100% load to 60% load.

[0090] When the load is reduced to 60%, the valve opening of the first valve is adjusted to the valve opening corresponding to the zero output or micro output state, that is, the safety valve opening, and the second valve is closed at the same time to maintain the first intermediate pressure cylinder at zero output or micro output state, and all the reheated steam enters the second intermediate pressure cylinder until the unit load is reduced from 60% load to 40% load.

[0091] When the operating conditions of the high-efficiency steam turbine thermal system drop to 40% load, the first valve is adjusted to full opening, and the second valve is opened simultaneously. The third valve is adjusted to the opening corresponding to zero or low output, i.e., the safety valve opening, and the fourth valve is closed simultaneously, maintaining the second intermediate pressure cylinder at zero or low output, allowing all reheated steam to enter the first intermediate pressure cylinder.

[0092] When the operating conditions of the high-efficiency steam turbine thermal system begin to decrease from 40% load, the second intermediate pressure cylinder can be maintained at zero output or micro output state, and the valve opening of the first valve can be reduced to reduce the amount and pressure of steam entering the first intermediate pressure cylinder.

[0093] In the above embodiment, the high-efficiency steam turbine thermal system can improve the energy conversion efficiency of the medium and low pressure cylinder groups under medium and low load conditions by setting up a grouped medium and low pressure steam turbine system, reduce the coal consumption of the unit, and achieve high efficiency of the coal-fired power unit under wide load conditions.

[0094] Based on the same inventive concept, Figure 7 As shown in the figure, a high-efficiency steam turbine thermal system control method is provided, which is applied to Figures 1 to 6 The controller of the high-efficiency steam turbine thermal system shown in FIG. 1 is used as an example for explanation. The controller is electrically connected to each valve in the high-efficiency steam turbine thermal system to adjust the valve opening of each valve. The method comprises the following steps:

[0095] S702, obtaining operating condition information of the high-efficiency steam turbine thermal system.

[0096] Among them, the operating condition information is information data used to characterize the operating conditions of the high-efficiency steam turbine thermal system. The operating condition information may include the operating conditions, load changes, electrical parameters of the coal-fired power unit, etc. of the high-efficiency steam turbine thermal system.

[0097] Specifically, the controller may obtain the operating condition information of the high-efficiency steam turbine thermal system from the management server of the high-efficiency steam turbine thermal system.

[0098] S704 , when it is determined based on the operating condition information that the high-efficiency steam turbine thermal system is in a rated operating condition, controlling a first valve of the high-efficiency steam turbine thermal system to be at a maximum opening.

[0099] Among them, the rated operating condition is the full-load operating condition of the high-efficiency steam turbine thermal system. The high-efficiency steam turbine thermal system can continuously output maximum power when operating under the rated operating condition.

[0100] Specifically, the controller analyzes the operating condition information to obtain the operating condition of the coal-fired power unit's thermal system. The controller compares the operating condition with the rated operating condition to determine whether the high-efficiency steam turbine thermal system is operating at the rated condition. If the high-efficiency steam turbine thermal system is operating at the rated condition, the controller controls the first valve of the high-efficiency steam turbine thermal system to its maximum opening.

[0101] S706: If the high-efficiency steam turbine thermal system is not in the rated operating condition, determine the operating condition range of the high-efficiency steam turbine thermal system based on the operating condition information.

[0102] The operating condition range is determined according to a first matching load operating condition corresponding to the steam intake amount of the first cylinder group and a second matching load operating condition corresponding to the steam intake amount of the second cylinder group.

[0103] Specifically, when determining that the high-efficiency steam turbine thermal system is not in the rated operating condition, the controller may analyze the operating condition information to determine the operating condition range of the high-efficiency steam turbine thermal system.

[0104] In one embodiment, when the high-efficiency steam turbine thermal system is not operating at rated conditions, a first matched load condition corresponding to the steam inlet volume of the first cylinder group and a second matched load condition corresponding to the steam inlet volume of the second cylinder group in the high-efficiency steam turbine thermal system are obtained. The high-efficiency steam turbine thermal system is divided into operating conditions according to the first matched load condition and the second matched load condition to obtain candidate load condition ranges. The operating condition range of the high-efficiency steam turbine thermal system is then determined from the candidate load condition ranges.

[0105] S708, adjusting the valve opening of the first valve in the high-efficiency steam turbine thermal system based on the operating condition range.

[0106] Specifically, the controller may adjust the valve opening of the first valve in the high-efficiency steam turbine thermal system based on the operating condition range of the operating condition.

[0107] In the above embodiment, by determining the operating range described in the operating conditions and then adjusting the valve opening of the first valve in the high-efficiency steam turbine thermal system based on the operating range, the adjustment efficiency and accuracy of the subsequent valve opening adjustment can be effectively improved, so that the adjustment process can better match the actual operating conditions of the unit.

[0108] In one embodiment, the steam intake amount of the second cylinder group is greater than the steam intake amount of the first cylinder group. S708, based on the operating condition range, adjusts the valve opening of the first valve in the high-efficiency steam turbine thermal system. This includes: when the operating condition range is a first low-load operating condition range, determining a target valve opening of the first valve based on the load difference between the operating condition of the high-efficiency steam turbine thermal system and a second matched load condition. Adjusting the opening of the first valve according to the target valve opening.

[0109] The upper limit of the first low-load operating range is the rated operating condition, and the lower limit is the second matched load condition. For example, if the ratio of the steam intake of the first cylinder group to the steam intake of the second cylinder group is 4:6, the second matched load condition can be 60%, and the first low-load operating range is 100%-60%.

[0110] Specifically, when the operating range is the first low-load operating range, the controller can calculate the load difference between the operating condition of the high-efficiency steam turbine thermal system and the second matching load condition, determine the target valve opening of the first valve based on the load difference, and adjust the opening of the first valve according to the target valve opening.

[0111] For example, if the operating condition of the high-efficiency steam turbine thermal system is an 85% load condition and the second matching load condition is a 60% load condition, the controller can determine that the load difference is 15%. This 15% load difference will be borne by the first intermediate and low-pressure cylinder groups. Therefore, the controller can determine the theoretical opening of the first valve when the first intermediate and low-pressure cylinder groups bear the 15% load difference condition as the target valve opening of the first valve, and adjust the opening of the first valve according to the target valve opening. For example, if the operating condition increases from 70% to 85%, the controller will increase the valve opening of the first valve according to the target valve opening. Conversely, if the operating condition decreases from 100% to 85%, the controller will decrease the valve opening of the first valve according to the target valve opening.

[0112] In the above embodiment, when the target operating range is the first low-load operating range, the valve opening of the first valve is adjusted based on the load difference between the operating condition of the high-efficiency steam turbine thermal system and the second matching load condition, thereby reducing the steam inflow into the first intermediate and low-pressure cylinder groups. This can enable the second intermediate and low-pressure cylinder groups to be continuously in the optimal operating state, thereby improving the operating efficiency of the entire high-efficiency steam turbine thermal system.

[0113] In one embodiment, the high-efficiency steam turbine thermal system control method further includes: reducing the opening of the first valve to a safe opening when the operating range is within the second low-load operating range, and closing a second valve disposed on the first low-pressure exhaust pipe in the high-efficiency steam turbine thermal system.

[0114] The upper limit of the second low-load operating range is the second matched load condition, and the lower limit is the first matched load condition. For example, if the ratio of the steam intake of the first cylinder group to the steam intake of the second cylinder group is 4:6, the first matched load condition can be 40% and the second matched load condition can be 60%. In this case, the second low-load operating range is 60%-40%.

[0115] Specifically, when the operating range is the second low-load operating range, the controller can reduce the opening of the first valve to a safe opening and simultaneously close the second valve provided on the first low-pressure exhaust pipe in the high-efficiency steam turbine thermal system.

[0116] In the above embodiment, when the operating range is the second low-load operating range, the controller may perform cylinder cutting processing on the first intermediate and low-pressure cylinder groups to achieve high efficiency in wide-load operation of the entire unit.

[0117] In one embodiment, the high-efficiency steam turbine thermal system control method further includes: when the operating range is a third low-load operating condition, adjusting the valve opening of the first valve to a maximum opening; opening a second valve provided on a first low-pressure exhaust steam pipe of the high-efficiency steam turbine thermal system; and closing a fourth valve provided on a second low-pressure exhaust steam pipe of the high-efficiency steam turbine thermal system and a third valve provided on a second reheat steam transmission branch line of the high-efficiency steam turbine thermal system.

[0118] The upper limit of the third low load condition is the first matched load condition. For example, if the ratio of the steam intake of the first cylinder group to the steam intake of the second cylinder group is 4:6, the first matched load can be 40%, and the third low load condition range is less than 40%.

[0119] Specifically, when the operating range is the third low-load operating condition, the controller may adjust the valve opening of the first valve to the maximum opening, open the second valve provided on the first low-pressure exhaust steam pipe of the high-efficiency steam turbine thermal system, and simultaneously close the fourth valve provided on the second low-pressure exhaust steam pipe of the high-efficiency steam turbine thermal system and the third valve provided on the second reheat steam transmission branch line of the high-efficiency steam turbine thermal system.

[0120] In the above embodiment, when the operating range is the third low-load operating condition, the controller may perform cylinder cutting processing on the second intermediate and low-pressure cylinders to achieve high efficiency in wide-load operation of the entire unit.

[0121] In one embodiment, Figure 8 As shown, a high-efficiency steam turbine thermal system control method is provided. In the high-efficiency steam turbine thermal system, the ratio of the steam intake of the first cylinder group to the steam intake of the second cylinder group is 4:6, the first matching load is 40%, and the second matching load is 60%. The method specifically includes the following steps:

[0122] First, the controller can obtain the operating condition information of the high-efficiency steam turbine thermal system, and based on the operating condition information, determine whether the high-efficiency steam turbine thermal system is in the rated operating condition. When the high-efficiency steam turbine thermal system is in the rated operating condition, the first valve and the second valve of the high-efficiency steam turbine thermal system are controlled to be at the maximum opening. At this time, the first intermediate pressure cylinder and the second intermediate pressure cylinder are fully filled with steam, which meets the steam intake of the intermediate and low pressure cylinders under the rated operating condition.

[0123] If the high-efficiency steam turbine thermal system is not operating at rated conditions, the operating condition range of the high-efficiency steam turbine thermal system is determined based on the operating condition information. When the operating condition range is 100% load to 60% load, the target valve opening of the first valve is determined based on the load difference between the operating condition of the high-efficiency steam turbine thermal system and the second matched load condition. The opening of the first valve is adjusted according to the target valve opening.

[0124] When the high-efficiency steam turbine thermal system is operating at 60%-40%, the opening of the first valve is reduced to a safe opening. The second valve, located on the first low-pressure exhaust pipe of the high-efficiency steam turbine thermal system, is closed. At this point, the first intermediate and low-pressure cylinder groups are maintained at zero or minimal output. All reheated steam enters the second intermediate and low-pressure cylinder groups.

[0125] When the high-efficiency steam turbine thermal system is operating at 40% or less, adjust the first valve's opening to its maximum. Open the second valve on the first low-pressure exhaust pipe of the high-efficiency steam turbine thermal system. Close the fourth valve on the second low-pressure exhaust pipe and the third valve on the second reheat steam branch line of the high-efficiency steam turbine thermal system. Maintain the second intermediate and low-pressure cylinder groups at zero or minimal output. All reheat steam enters the first intermediate and low-pressure cylinder groups.

[0126] In the above embodiment, the first intermediate and low-pressure cylinder group maintains rated steam intake at a load of 60%-100%, and is more efficient than the intermediate and low-pressure cylinders of conventional technology at a load below 40%-60%. Below 40% load, all reheated steam enters the first intermediate and low-pressure cylinder group, and the efficiency of the first intermediate and low-pressure cylinder group is also higher than that of the intermediate and low-pressure cylinders of conventional technology, with high efficiency over a wide load range.

[0127] It should be understood that, although the various steps in the flowcharts involved in the various embodiments described above are displayed in sequence according to the instructions of the arrows, these steps are not necessarily executed in sequence in the order indicated by the arrows. Unless otherwise specified herein, there is no strict order restriction on the execution of these steps, and these steps can be executed in other orders. Moreover, at least a portion of the steps in the flowcharts involved in the various embodiments described above can include multiple steps or multiple stages, and these steps or stages are not necessarily executed and completed at the same time, but can be executed at different times, and the execution order of these steps or stages is not necessarily to be carried out in sequence, but can be executed in turn or alternately with other steps or at least a portion of steps or stages in other steps.

[0128] Based on the same inventive concept, embodiments of the present application also provide a high-efficiency steam turbine thermal system control device for implementing the high-efficiency steam turbine thermal system control method described above. The solution provided by this device is similar to the solution described in the method described above. Therefore, the specific limitations of one or more embodiments of the high-efficiency steam turbine thermal system control device provided below can be found in the above-described limitations of the high-efficiency steam turbine thermal system control method and will not be further elaborated here.

[0129] In one embodiment, Figure 9 As shown, a high-efficiency steam turbine thermal system control device 900 is provided, comprising: an operating condition information acquisition module 901, a rated operating condition control module 902, an operating condition range determination module 903 and a valve adjustment module 904, wherein:

[0130] The operating condition information acquisition module 901 is used to obtain the operating condition information of the high-efficiency steam turbine thermal system.

[0131] The rated operating condition control module 902 is configured to control the first valve of the high-efficiency steam turbine thermal system to be at a maximum opening when it is determined based on the operating condition information that the high-efficiency steam turbine thermal system is at a rated operating condition.

[0132] The operating condition range determination module 903 is used to determine the operating condition range of the high-efficiency steam turbine thermal system based on the operating condition information if the high-efficiency steam turbine thermal system is not in the rated operating condition; the operating condition range is determined based on the first matching load condition corresponding to the steam inlet amount of the first cylinder group and the second matching load condition corresponding to the steam inlet amount of the second cylinder group.

[0133] The valve adjustment module 904 is used to adjust the valve opening of the first valve in the high-efficiency steam turbine thermal system based on the operating condition range.

[0134] In one embodiment, the steam intake of the second cylinder group is greater than that of the first cylinder group; the valve adjustment module 904 is used to: when the operating range is a first low-load operating range, determine the target valve opening of the first valve based on the load difference between the operating condition of the high-efficiency steam turbine thermal system and the second matching load condition; the upper limit value of the first low-load operating range is the rated operating condition, and the lower limit value is the second matching load condition; and adjust the opening of the first valve according to the target valve opening.

[0135] In one embodiment, the valve adjustment module 904 is also used to: reduce the opening of the first valve to a safe opening when the operating range is the second low load operating range; the upper limit value of the second low load operating range is the second matching load condition, and the lower limit value is the first matching load condition; close the second valve provided on the first low-pressure exhaust pipe in the high-efficiency steam turbine thermal system.

[0136] In one embodiment, the valve adjustment module 904 is also used to: when the operating range is the third low load condition, adjust the valve opening of the first valve to the maximum opening; the upper limit value of the third low load condition is the first matching load condition; open the second valve provided on the first low-pressure exhaust pipe in the high-efficiency steam turbine thermal system; close the fourth valve provided on the second low-pressure exhaust pipe in the high-efficiency steam turbine thermal system, and close the third valve provided on the second reheat steam transmission branch in the high-efficiency steam turbine thermal system.

[0137] Each module in the aforementioned high-efficiency steam turbine thermal system control device may be implemented in whole or in part through software, hardware, or a combination thereof. Each module may be embedded in or independent of a processor within a computer device in the form of hardware, or may be stored in a computer device memory in the form of software, allowing the processor to call and execute the corresponding operations of each module.

[0138] In one embodiment, a computer device is provided. The computer device may be a controller, and its internal structure diagram may be as follows: Figure 10 As shown. The computer device includes a processor, a memory and a network interface connected via a system bus. The processor of the computer device is used to provide computing and control capabilities. The memory of the computer device includes a non-volatile storage medium and an internal memory. The non-volatile storage medium stores an operating system, a computer program and a database. The internal memory provides an environment for the operation of the operating system and the computer program in the non-volatile storage medium. The database of the computer device is used to store data such as operating condition information and operating condition range. The network interface of the computer device is used to communicate with an external terminal via a network connection. When the computer program is executed by the processor, a high-efficiency steam turbine thermal system control method is implemented.

[0139] Those skilled in the art will understand that Figure 10 The structure shown in the figure is only a block diagram of a part of the structure related to the solution of the present application, and does not constitute a limitation on the computer device to which the solution of the present application is applied. The specific computer device may include more or fewer components than shown in the figure, or combine certain components, or have a different component arrangement.

[0140] In one embodiment, a computer device is provided, including a memory and a processor. The memory stores a computer program, and the processor implements the specific steps of the embodiment of the high-efficiency steam turbine thermal system control method when executing the computer program.

[0141] In one embodiment, a computer-readable storage medium is provided, on which a computer program is stored. When the computer program is executed by a processor, the specific steps of the embodiment of the high-efficiency steam turbine thermal system control method are implemented.

[0142] In one embodiment, a computer program product is provided, including a computer program, which implements the specific steps of the embodiment of the high-efficiency steam turbine thermal system control method when executed by a processor.

[0143] It should be noted that the user information (including but not limited to user device information, user personal information, etc.) and data (including but not limited to data used for analysis, storage, and display, etc.) involved in this application are all authorized by the user or have been fully authorized by all parties. Furthermore, the acquisition, storage, processing, and transmission of this data comply with relevant laws and regulations.

[0144] Those skilled in the art will appreciate that all or part of the processes in the above-mentioned embodiments can be implemented by instructing the relevant hardware through a computer program. The computer program can be stored in a non-volatile computer-readable storage medium. When the computer program is executed, it can include the processes of the above-mentioned embodiments. In particular, any reference to memory, database, or other media used in the embodiments provided in this application can include at least one of non-volatile and volatile memory. Non-volatile memory can include read-only memory (ROM), magnetic tape, floppy disk, flash memory, optical memory, high-density embedded non-volatile memory, resistive random access memory (ReRAM), magnetic random access memory (MRAM), ferroelectric random access memory (FRAM), phase change memory (PCM), graphene memory, etc. Volatile memory can include random access memory (RAM) or external cache memory, etc. By way of illustration and not limitation, RAM can take various forms, such as static random access memory (SRAM) or dynamic random access memory (DRAM). The databases involved in the various embodiments provided herein may include at least one of a relational database and a non-relational database. Non-relational databases may include, but are not limited to, distributed databases based on blockchains. The processors involved in the various embodiments provided herein may be, but are not limited to, general-purpose processors, central processing units (CPUs), graphics processing units (GPUs), digital signal processors (DSPs), programmable logic devices (PLDs), data processing logic devices based on quantum computing, and the like.

[0145] The technical features of the above embodiments can be combined arbitrarily. To make the description concise, not all possible combinations of the technical features in the above embodiments are described. However, as long as there is no contradiction in the combination of these technical features, they should be considered to be within the scope of this specification.

[0146] The above-described embodiments merely represent several implementation methods of the present application. While the descriptions are relatively specific and detailed, they should not be construed as limiting the scope of the present application. It should be noted that a person of ordinary skill in the art may make various modifications and improvements without departing from the spirit of the present application, and these modifications and improvements fall within the scope of protection of the present application. Therefore, the scope of protection of the present application shall be determined by the appended claims.

Claims

1. A high-efficiency steam turbine thermal system, characterized in that: The high-efficiency steam turbine thermal system comprises: a first intermediate and low-pressure cylinder group and a second intermediate and low-pressure cylinder group connected in parallel; The steam intake amount of the first cylinder group of the first intermediate and low-pressure cylinder group and the steam intake amount of the second cylinder group of the second intermediate and low-pressure cylinder group are set according to a preset ratio, and the steam intake amount of the first cylinder group and the steam intake amount of the second cylinder group meet the rated operating condition requirements of the high-efficiency steam turbine thermal system; The first cylinder group steam inlet of the first intermediate and low pressure cylinder group is connected to the reheat steam delivery pipeline of the high-efficiency steam turbine thermal system through a first reheat steam delivery branch; the second cylinder group steam inlet of the second intermediate and low pressure cylinder group is connected to the reheat steam delivery pipeline through a second reheat steam delivery branch; The first reheat steam delivery branch is provided with a first valve for adjusting the first steam inlet parameters of the first intermediate and low pressure cylinder groups.

2. The high-efficiency steam turbine thermal system according to claim 1, characterized in that: The first intermediate- and low-pressure cylinder group includes a first intermediate-pressure cylinder and a first low-pressure cylinder group, and the second intermediate- and low-pressure cylinder group includes a second intermediate-pressure cylinder and a second low-pressure cylinder group; The first intermediate-pressure steam exhaust port of the first intermediate-pressure cylinder is connected to the first low-pressure steam inlet of the first low-pressure cylinder group through a first intermediate-pressure steam exhaust pipe; The second intermediate-pressure steam exhaust port of the second intermediate-pressure cylinder is connected to the second low-pressure steam inlet of the second low-pressure cylinder group through a second intermediate-pressure steam exhaust pipe; The first intermediate-pressure steam inlet of the first intermediate-pressure cylinder is connected to the reheat steam delivery pipeline of the high-efficiency steam turbine thermal system through a first reheat steam delivery branch; the second intermediate-pressure steam inlet of the second intermediate-pressure cylinder is connected to the reheat steam delivery pipeline through a second reheat steam delivery branch.

3. The high-efficiency steam turbine thermal system according to claim 2, characterized in that: The high-efficiency steam turbine thermal system further includes: a heat recovery component for extracting low-pressure exhaust steam from the first low-pressure cylinder group and the second low-pressure cylinder group to heat boiler feed water; The first low-pressure exhaust port of the first low-pressure cylinder group is connected to the heat recovery component through a first low-pressure exhaust pipe; the second low-pressure exhaust port of the second low-pressure cylinder group is connected to the heat recovery component through a second low-pressure exhaust pipe.

4. The high-efficiency steam turbine thermal system according to claim 3, characterized in that: The first low-pressure exhaust steam pipeline is provided with a second valve for controlling the opening and closing of the first low-pressure exhaust steam pipeline.

5. The high-efficiency steam turbine thermal system according to claim 4, characterized in that: The steam intake amount of the second cylinder group is greater than the steam intake amount of the first cylinder group; A third valve is provided on the second reheat steam delivery branch for adjusting the second steam inlet parameters of the second intermediate and low pressure cylinder groups; The second low-pressure steam exhaust pipe is provided with a fourth valve for controlling the opening and closing of the second low-pressure steam exhaust pipe.

6. The high-efficiency steam turbine thermal system according to claim 4 or 5, characterized in that: The heat recovery component includes a first low-pressure heater, a second low-pressure heater, a third low-pressure heater, and a fourth low-pressure heater; The first low-pressure heater, the second low-pressure heater, the third low-pressure heater and the fourth low-pressure heater are sequentially connected through a water supply channel, and steam extraction temperatures of the first low-pressure heater, the second low-pressure heater, the third low-pressure heater and the fourth low-pressure heater are sequentially decreased; The second low-pressure steam exhaust port is connected to the first low-pressure heater and any one low-pressure heater except the first low-pressure heater through a second low-pressure steam exhaust pipe; The first low-pressure exhaust port is connected to the second low-pressure heater and the fourth low-pressure heater through the first low-pressure exhaust pipe; the second low-pressure exhaust port is connected to the first low-pressure heater and the third low-pressure heater through the second low-pressure exhaust pipe.

7. A high-efficiency steam turbine thermal system control method, applied to the high-efficiency steam turbine thermal system according to any one of claims 1 to 6, characterized in that: The method comprises: Obtaining operating condition information of the high-efficiency steam turbine thermal system; When it is determined based on the operating condition information that the high-efficiency steam turbine thermal system is in a rated operating condition, controlling a first valve of the high-efficiency steam turbine thermal system to be at a maximum opening; If the high-efficiency steam turbine thermal system is not in the rated operating condition, determining an operating condition range of the high-efficiency steam turbine thermal system based on the operating condition information; the operating condition range is determined based on a first matching load condition corresponding to the steam intake of the first cylinder group and a second matching load condition corresponding to the steam intake of the second cylinder group; Based on the operating condition range, the valve opening of the first valve in the high-efficiency steam turbine thermal system is adjusted.

8. The method according to claim 7, characterized in that The steam intake amount of the second cylinder group is greater than the steam intake amount of the first cylinder group; Determining the valve opening of the first valve in the high-efficiency steam turbine thermal system based on the operating condition range includes: When the operating condition range is a first low-load operating condition range, determining a target valve opening of the first valve based on a load difference between an operating condition of the high-efficiency steam turbine thermal system and a second matched load condition; an upper limit of the first low-load operating condition range is the rated operating condition, and a lower limit is the second matched load condition; The opening of the first valve is adjusted according to the target valve opening.

9. The method according to claim 8, characterized in that The method further comprises: When the operating range is a second low-load operating range, reducing the opening of the first valve to a safe opening; the upper limit of the second low-load operating range is the second matching load condition, and the lower limit is the first matching load condition; Close the second valve provided on the first low-pressure exhaust pipe in the high-efficiency steam turbine thermal system.

10. The method according to claim 8, characterized in that The method further comprises: When the operating condition range is the third low load condition, adjusting the valve opening of the first valve to the maximum opening; the upper limit value of the third low load condition is the first matching load condition; Opening a second valve provided on a first low-pressure exhaust pipe of the high-efficiency steam turbine thermal system; Close the fourth valve on the second low-pressure exhaust pipe in the high-efficiency steam turbine thermal system and the third valve on the second reheat steam transmission branch in the high-efficiency steam turbine thermal system.

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