A 660mw grade high-efficiency ultra-supercritical flexible deep-topping steam turbine applied to high-altitude areas

Abstract

A kind of 660MW level high-efficiency ultra-supercritical flexible deep governing steam turbine applied in high-altitude area, it relates to steam turbine technical field.To solve the problem that existing steam turbine unit causes lower vacuum degree when applied in high-altitude area, which directly shows the increase of steam turbine exhaust back pressure, thereby causing lower operation safety of unit.Mainly through the structure optimization of valve, high-pressure module, medium-pressure module and low-pressure module, the excellent economy and operation flexibility are ensured;Through the application of advanced 1100mm deep peak shaving last-stage blade, the operation flexibility, deep peak shaving performance and adaptability of high back pressure and high altitude of unit are improved;And the condenser vacuum degree in summer high back pressure condition is ensured.The steam turbine unit with such structure can be applied in high-altitude area, and after ensuring the vacuum degree of unit, the safety of unit operation is ensured.The utility model is suitable for steam turbine structure technical field in high-altitude area.

Description

Technical Field

[0001] This utility model relates to the field of steam turbine technology, specifically to a 660MW-class high-efficiency ultra-supercritical flexible deep-tuning steam turbine for use in high-altitude areas. Background Technology

[0002] In high-altitude areas (taking Golmud, Qinghai as an example), the average air pressure is only 72.5 kPa. For a steam turbine unit with the same designed back pressure (8.5 kPa as an example), the vacuum degree of a unit in a plain area (100 kPa as an example) can reach 91.5 kPa, while the vacuum degree of a unit in a high-altitude area can only reach 64 kPa. The decrease in vacuum degree directly manifests as an increase in the exhaust back pressure of the steam turbine, which has a significant impact on the economic efficiency of the unit. In addition, high back pressure operation also poses a potential threat to the safety of the unit. When the back pressure increases, the expansion of steam in the last stage blades becomes insufficient, which may cause flow separation or even surge and blower overheating. This "ceiling effect" determined by the geographical environment is the primary challenge in the design of high-altitude steam turbine units.

[0003] In summary, when existing steam turbine units are used in high-altitude areas, the vacuum level of the unit decreases, which directly manifests as an increase in the exhaust back pressure of the steam turbine, resulting in a lower operational safety of the unit. Utility Model Content

[0004] This invention addresses the problem that existing steam turbine units, when used in high-altitude areas, suffer from reduced vacuum, which directly manifests as increased exhaust back pressure and consequently lower operational safety. It proposes a 660MW-class high-efficiency ultra-supercritical flexible deep-adjustment steam turbine for high-altitude applications.

[0005] This utility model discloses a 660MW-class high-efficiency ultra-supercritical flexible deep-adjustment steam turbine for high-altitude areas, which comprises a high-pressure valve I, a high-pressure body module II, a medium-pressure valve III, a medium-pressure body module IV, a low-pressure body module V, and a condenser VI.

[0006] Each of the two main steam inlets of the high-pressure main body module II is equipped with a high-pressure valve I. The output end of the high-pressure main body module II is connected to the input end of the medium-pressure main body module IV. Each of the two medium-pressure steam inlets of the medium-pressure main body module IV is equipped with a medium-pressure valve III. The output end of the medium-pressure main body module IV is connected to the input end of the low-pressure main body module V. The output end of the low-pressure main body module V is connected to the power input end of the turning gear device 68. A condenser VI is provided at the bottom of the low-pressure main body module V.

[0007] Furthermore, the interior of the medium-pressure main body module IV is connected to the interior of the low-pressure main body module V via a medium-low pressure connecting pipe 52;

[0008] Furthermore, the high-pressure body module II includes a first bearing housing 1, a first support bearing 2, a bearing housing oil baffle ring 3, a high-pressure adjusting end steam seal body 4, a high-pressure outer cylinder 5, a high-pressure inner cylinder 6, a high-pressure moving blade 7, a high-pressure rotor 8, a high-pressure stationary blade 9, a high-pressure transverse guide vane 10, a high-pressure electrical end steam seal body 11, a second bearing housing adjusting end oil baffle ring 12, a second support bearing 13, a thrust bearing 14, a second bearing housing 15, a third support bearing 16, and a second bearing housing electrical end oil baffle ring 17.

[0009] One end of the high-pressure rotor 8 is inserted into the inner ring of the first support bearing 2 inside the first bearing housing 1. A bearing housing oil retainer ring 3 is provided on the high-pressure rotor 8 at the insertion port relative to the first bearing housing 1. The high-pressure rotor 8 has a high-pressure outer cylinder 5 and a high-pressure inner cylinder 6 arranged sequentially along its length. Inside the high-pressure inner cylinder 6, a high-pressure moving blade 7, a high-pressure stationary blade 9, and a high-pressure transverse guide blade 10 are arranged sequentially along the axis. The high-pressure moving blade 7 is mounted on the high-pressure rotor 8. A high-pressure adjusting steam seal 4 is provided between the outer surface of the high-pressure rotor 8 and the input port at one end of the high-pressure outer cylinder 5. A high-pressure electric terminal steam seal body 11 is provided between the outer surface of the high-pressure rotor 8 and the output port of the other end of the high-pressure outer cylinder 5. A second support bearing 13, a thrust bearing 14 and a third support bearing 16 are sequentially provided along the axial direction on the other end of the high-pressure rotor 8. The second support bearing 13, the thrust bearing 14 and the third support bearing 16 are all located inside the second bearing housing 15. The input end of the second bearing housing 15 is provided with a second bearing housing adjustment end oil baffle ring 12, and the output end of the second bearing housing 15 is provided with a second bearing housing electric terminal oil baffle ring 17.

[0010] Furthermore, the high-pressure inner cylinder 6 is a barrel-shaped cylinder, and the high-pressure inner cylinder 6 adopts a 2×180° tangential volute steam inlet method;

[0011] Furthermore, the medium-pressure main body module IV includes a medium-pressure adjusting end steam seal body 18, a medium-pressure outer cylinder 19, a medium-pressure adjusting end baffle sleeve 20, medium-pressure reverse 1-15 moving blades 21, medium-pressure reverse 7-15 stationary blades 22, a medium-pressure inner cylinder 23, medium-pressure reverse 1-6 stage stationary blades 24, a medium-pressure first stage baffle 25, a medium-pressure rotor cooling device 26, medium-pressure forward 1-6 stage stationary blades 27, medium-pressure forward 7-15 stationary blades 28, a medium-pressure rotor 29, medium-pressure forward 1-15 moving blades 30, a medium-pressure electrical end baffle sleeve 31, a medium-pressure electrical end steam seal body 32, a No. 3 bearing box adjusting end oil baffle ring 33, a No. 4 support bearing 34, a No. 3 bearing box 35, a No. 5 support bearing 36, and a No. 3 bearing box electrical end oil baffle ring 37.

[0012] A medium-pressure adjusting steam seal 18 is provided on the input end of the medium-pressure outer cylinder 19. The end of the medium-pressure rotor 29 passes through the interior of the medium-pressure outer cylinder 19 and is inserted into the interior of the No. 3 bearing housing 35. The No. 4 support bearing 34, the No. 5 support bearing 36, and the No. 3 bearing housing electrical end oil baffle ring 37 are sequentially arranged along the axial direction inside the No. 3 bearing housing 35. A No. 3 bearing housing adjusting oil baffle ring 33 is provided at the insertion port of the No. 3 bearing housing 35 at the end of the medium-pressure rotor 29. A medium-pressure electrical end steam seal 32 is provided at the connection between the outer surface of the medium-pressure rotor 29 and the output end of the medium-pressure outer cylinder 19. A medium-pressure rotor cooling device 26 is provided in the middle of the outer surface of the medium-pressure outer cylinder 19. The middle part of the sub-29 is provided with a medium-pressure inner cylinder 23. The interior of the medium-pressure inner cylinder 23 is provided with medium-pressure reverse 1-15 moving blades 21, medium-pressure reverse 1-6 stationary blades 24, medium-pressure first-stage baffle 25, medium-pressure forward 1-6 stationary blades 27 and medium-pressure forward 1-15 moving blades 30 in sequence along the axial direction. One end of the medium-pressure inner cylinder 23 is provided with a medium-pressure adjusting end baffle sleeve 20, and the other end of the medium-pressure inner cylinder 23 is provided with a medium-pressure electric end baffle sleeve 31. The interior of the medium-pressure adjusting end baffle sleeve 20 is provided with medium-pressure reverse 7-15 stationary blades 22 along the axial direction. The interior of the medium-pressure electric end baffle sleeve (31) is provided with medium-pressure forward 7-15 stationary blades 28 along the axial direction.

[0013] Furthermore, the intermediate pressure first-stage diaphragm 25 is an impulse diaphragm;

[0014] Furthermore, the low-pressure body module V includes a low-pressure adjusting end steam seal body 38, a low-pressure rotor 39, an adjusting end bellows 40, a low-pressure outer cylinder 41, an adjusting end exhaust guide ring 42, an adjusting end final stage moving vane 43, a first atmospheric valve 44, a low-pressure inner cylinder 45, an adjusting end final stage baffle 46, an adjusting end secondary final stage baffle 47, an adjusting end secondary-secondary final stage baffle 48, an adjusting end second stage stationary vane 49, an adjusting end baffle sleeve 50, a low-pressure horizontal stationary vane 51, and a sealing baffle. 53. Electrical end baffle sleeve; 54. Electrical end second stage stationary vane; 55. Electrical end secondary and final stage baffle; 56. Electrical end secondary and final stage baffle; 57. Electrical end final stage baffle; 58. Electrical end final stage moving vane; 59. No. 2 atmospheric valve; 60. Electrical end exhaust guide ring; 61. Electrical end bellows; 62. Low-pressure electrical end steam seal; 63. No. 4 bearing housing adjusting end oil baffle ring; 64. No. 6 support bearing; 65. No. 4 bearing housing; 66. Coupling; 67. No. 4 bearing housing electrical end oil baffle ring; 69.

[0015] A low-pressure adjusting steam seal body 38 is provided at one end of the low-pressure rotor 39, and an adjusting bellows 40 is provided on one side of the low-pressure adjusting steam seal body 38 on the low-pressure rotor 39. A low-pressure outer cylinder 41 is provided in the middle of the outer surface of the low-pressure rotor 39. A first atmospheric valve 44 and a second atmospheric valve 60 are provided sequentially along the length direction on the outer surface of the low-pressure outer cylinder 41. A low-pressure inner cylinder 45 is provided inside the low-pressure outer cylinder 41. The low-pressure inner cylinder 45 is provided sequentially along the axial direction as follows: adjusting exhaust steam guide ring 42, adjusting final stage moving vane 43, adjusting final stage baffle 46, adjusting secondary final stage baffle 47, adjusting secondary final stage baffle 48, adjusting second stage stationary vane 49, adjusting baffle sleeve 50, low-pressure transverse stationary vane 51, sealing baffle 53, electric end baffle sleeve 54, and electric end second stage stationary vane 55. The low-pressure rotor 39 has an electric terminal secondary and final stage partition 56, an electric terminal secondary and final stage partition 57, an electric terminal final stage partition 58, an electric terminal final stage moving blade 59, and an electric terminal exhaust guide ring 61. On the outer surface of the other end of the low-pressure rotor 39, an electric terminal corrugated section 62 and a low-pressure electric terminal steam seal body 63 are arranged sequentially along the axial direction. The other end of the low-pressure rotor 39 is inserted into the inner ring of the No. 6 support bearing 65 inside the No. 4 bearing housing 66. The upper surface of the No. 4 bearing housing 66 is provided with a turning device 68. After the power input end of the turning device 68 passes through the No. 4 bearing housing 66, it is connected to the low-pressure rotor 39 through a coupling 67. The No. 4 bearing housing 66 has a No. 4 bearing housing adjusting end oil baffle ring 64 in the middle of one side and a No. 4 bearing housing 66 has a No. 4 bearing housing electric terminal oil baffle ring 69 in the middle of the other side.

[0016] Furthermore, both the terminal blade 43 and the electrical terminal blade 59 are 1100mm deep peak-shaving blades with a circular arc fir tree shape at the root. They are connected to adjacent blades by an integral shroud, and the middle part is connected by a boss-shaped tie rod in a full circle structure.

[0017] Compared with the prior art, the present invention has the following advantages:

[0018] This invention overcomes the shortcomings of existing technologies by optimizing the structure of valves and high, medium, and low-pressure modules to ensure excellent economy and operational flexibility. The application of advanced 1100mm deep peak-shaving final-stage blades improves the unit's operational flexibility, deep peak-shaving performance, and adaptability to high back pressure and high altitude conditions. It also ensures condenser vacuum under high back pressure conditions in summer. This turbine unit structure is suitable for high-altitude areas, and by guaranteeing the unit's vacuum level, it ensures the safety of unit operation. Attached Figure Description

[0019] Figure 1 This is a top view of a 660MW-class high-efficiency ultra-supercritical flexible deep-tuning steam turbine applied in high-altitude areas, as described in this utility model.

[0020] Figure 2This is a front view of a 660MW-class high-efficiency ultra-supercritical flexible deep-tuning steam turbine applied in high-altitude areas, as described in this utility model.

[0021] Figure 3 This is a main sectional view of the high-pressure main body module of a 660MW-class high-efficiency ultra-supercritical flexible deep-tuning steam turbine applied in high-altitude areas, as described in this utility model.

[0022] Figure 4 This is a main sectional view of the intermediate pressure body module of a 660MW-class high-efficiency ultra-supercritical flexible deep-adjustment steam turbine applied in high-altitude areas, as described in this utility model.

[0023] Figure 5 This is a main sectional view of the low-pressure main body module of a 660MW-class high-efficiency ultra-supercritical flexible deep-tuning steam turbine applied in high-altitude areas, as described in this utility model.

[0024] Figure 6 This is a side view of a 660MW-class high-efficiency ultra-supercritical flexible deep-tuning steam turbine applied in high-altitude areas, as described in this utility model. Detailed Implementation

[0025] Specific implementation method one: Combining Figure 1 , Figure 2 and Figure 6 This embodiment describes a 660MW-class high-efficiency ultra-supercritical flexible deep-adjustment steam turbine applied in high-altitude areas, which comprises a high-pressure valve I, a high-pressure main body module II, a medium-pressure valve III, a medium-pressure main body module IV, a low-pressure main body module V, and a condenser VI.

[0026] Each of the two main steam inlets of the high-pressure main body module II is equipped with a high-pressure valve I. The output end of the high-pressure main body module II is connected to the input end of the medium-pressure main body module IV. Each of the two medium-pressure steam inlets of the medium-pressure main body module IV is equipped with a medium-pressure valve III. The output end of the medium-pressure main body module IV is connected to the input end of the low-pressure main body module V. The output end of the low-pressure main body module V is connected to the power input end of the turning gear device 68. A condenser VI is provided at the bottom of the low-pressure main body module V.

[0027] Specific Implementation Method Two: Combining Figure 1 , Figure 2 and Figure 4 This embodiment further defines the steam turbine described in Specific Embodiment 1. This embodiment describes a 660MW-class high-efficiency ultra-supercritical flexible deep-adjustment steam turbine for use in high-altitude areas. The internal structure of the medium-pressure main module IV is connected to the internal structure of the low-pressure main module V through a medium-low pressure connecting pipe 52.

[0028] In this specific embodiment, the medium and low pressure connecting pipe 52 is a hot-pressed elbow, which is superior to the traditional shrimp-waist welded elbow, further reducing the pressure loss of the connecting pipe.

[0029] Specific implementation method three: Combining Figure 3 This embodiment further defines the steam turbine described in Specific Embodiment 1. This embodiment describes a 660MW-class high-efficiency ultra-supercritical flexible deep-adjustment steam turbine applied in high-altitude areas. The high-pressure main body module II includes a No. 1 bearing housing 1, a No. 1 support bearing 2, a bearing housing oil baffle ring 3, a high-pressure adjusting end steam seal body 4, a high-pressure outer cylinder 5, a high-pressure inner cylinder 6, high-pressure moving blades 7, a high-pressure rotor 8, a high-pressure stationary blade 9, a high-pressure transverse guide vane 10, a high-pressure electric end steam seal body 11, a No. 2 bearing housing adjusting end oil baffle ring 12, a No. 2 support bearing 13, a thrust bearing 14, a No. 2 bearing housing 15, a No. 3 support bearing 16, and a No. 2 bearing housing electric end oil baffle ring 17.

[0030] One end of the high-pressure rotor 8 is inserted into the inner ring of the first support bearing 2 inside the first bearing housing 1. A bearing housing oil retainer ring 3 is provided on the high-pressure rotor 8 at the insertion port relative to the first bearing housing 1. The high-pressure rotor 8 has a high-pressure outer cylinder 5 and a high-pressure inner cylinder 6 arranged sequentially along its length. Inside the high-pressure inner cylinder 6, a high-pressure moving blade 7, a high-pressure stationary blade 9, and a high-pressure transverse guide blade 10 are arranged sequentially along the axis. The high-pressure moving blade 7 is mounted on the high-pressure rotor 8. A high-pressure adjusting steam seal 4 is provided between the outer surface of the high-pressure rotor 8 and the input port at one end of the high-pressure outer cylinder 5. A high-pressure electric terminal steam seal body 11 is provided between the outer surface of the high-pressure rotor 8 and the output port of the other end of the high-pressure outer cylinder 5. A second support bearing 13, a thrust bearing 14 and a third support bearing 16 are sequentially provided along the axial direction on the other end of the high-pressure rotor 8. The second support bearing 13, the thrust bearing 14 and the third support bearing 16 are all located inside the second bearing housing 15. The input end of the second bearing housing 15 is provided with a second bearing housing adjustment end oil baffle ring 12, and the output end of the second bearing housing 15 is provided with a second bearing housing electric terminal oil baffle ring 17.

[0031] In this specific implementation, the high-pressure main body module II is designed as an inner and outer double-layer cylinder. The high-pressure inner cylinder 6 adopts a barrel-shaped cylinder with a red ring seal, which has excellent thermal stress adaptability and meets the requirements of flexible operation and deep peak shaving of the unit. The high-pressure inner cylinder 6 adopts a 2×180° tangential volute for steam inlet, and is equipped with high-pressure transverse guide vanes 10, which further reduces the steam inlet pressure loss. At the same time, the flow passage adopts a multi-stage small enthalpy drop reaction blade design technology, which effectively improves the efficiency of the high-pressure module.

[0032] Specific implementation method four: Combination Figure 3This embodiment further defines the steam turbine described in Specific Embodiment Three. This embodiment describes a 660MW-class high-efficiency ultra-supercritical flexible deep-adjustment steam turbine applied in high-altitude areas. The high-pressure inner cylinder 6 adopts a barrel-shaped cylinder and a 2×180° tangential volute steam inlet method.

[0033] Specific Implementation Method Five: Combining Figure 4 This embodiment further defines the steam turbine described in Specific Embodiment 1. This embodiment describes a 660MW-class high-efficiency ultra-supercritical flexible deep-adjustment steam turbine for high-altitude areas. The intermediate-pressure main body module IV includes an intermediate-pressure regulating end steam seal 18, an intermediate-pressure outer cylinder 19, an intermediate-pressure regulating end diaphragm sleeve 20, intermediate-pressure reverse 1-15 moving blades 21, intermediate-pressure reverse 7-15 stationary blades 22, an intermediate-pressure inner cylinder 23, and an intermediate-pressure reverse... 24. Stationary blades of stages 1-6; 25. First stage diaphragm of medium pressure; 26. Medium pressure rotor cooling device; 27. Stationary blades of stages 1-6 of medium pressure forward direction; 28. Stationary blades of stages 7-15 of medium pressure forward direction; 29. ​​Medium pressure rotor; 30. Moving blades of stages 1-15 of medium pressure forward direction; 31. Diaphragm sleeve of medium pressure electric terminal; 32. Steam seal of medium pressure electric terminal; 33. Oil baffle ring of the adjusting end of bearing box No. 3; 34. Support bearing No. 4; 35. Bearing box No. 3; 36. Support bearing No. 5; and oil baffle ring of the electric terminal of bearing box No. 3.

[0034] A medium-pressure adjusting steam seal 18 is provided on the input end of the medium-pressure outer cylinder 19. The end of the medium-pressure rotor 29 passes through the interior of the medium-pressure outer cylinder 19 and is inserted into the interior of the No. 3 bearing housing 35. The No. 4 support bearing 34, the No. 5 support bearing 36, and the No. 3 bearing housing electrical end oil baffle ring 37 are sequentially arranged along the axial direction inside the No. 3 bearing housing 35. A No. 3 bearing housing adjusting oil baffle ring 33 is provided at the insertion port of the No. 3 bearing housing 35 at the end of the medium-pressure rotor 29. A medium-pressure electrical end steam seal 32 is provided at the connection between the outer surface of the medium-pressure rotor 29 and the output end of the medium-pressure outer cylinder 19. A medium-pressure rotor cooling device 26 is provided in the middle of the outer surface of the medium-pressure outer cylinder 19. The rotor 29 has a medium-pressure inner cylinder 23 in the middle. Inside the medium-pressure inner cylinder 23, along the axial direction, there are medium-pressure reverse 1-15 moving blades 21, medium-pressure reverse 1-6 stationary blades 24, medium-pressure first-stage baffle 25, medium-pressure forward 1-6 stationary blades 27, and medium-pressure forward 1-15 moving blades 30. One end of the medium-pressure inner cylinder 23 is provided with a medium-pressure adjusting end baffle sleeve 20, and the other end of the medium-pressure inner cylinder 23 is provided with a medium-pressure electrical end baffle sleeve 31. Inside the medium-pressure adjusting end baffle sleeve 20, along the axial direction, there are medium-pressure reverse 7-15 stationary blades 22, and inside the medium-pressure electrical end baffle sleeve 31, along the axial direction, there are medium-pressure forward 7-15 stationary blades 28.

[0035] In this specific embodiment, the medium-pressure main body module IV is designed as an inner and outer double-layer cylinder, and a medium-pressure rotor cooling device 26 is also provided. The first-stage medium-pressure baffle 25 adopts an impulse baffle, which gives the medium-pressure flow excellent variable load adaptability and meets the needs of flexible operation and deep peak shaving of the unit. At the same time, the medium-pressure flow also adopts multi-stage small enthalpy drop reaction blade design technology, with a total of 2×16 pressure stages, which effectively improves the economy of the medium-pressure module across the entire load range.

[0036] Specific Implementation Method Six: Combination Figure 4 This embodiment further defines the steam turbine described in Specific Embodiment Five. The 660MW-class high-efficiency ultra-supercritical flexible deep-tuning steam turbine applied in high-altitude areas described in this embodiment uses an impulse-type diaphragm 25 for the intermediate-pressure first-stage diaphragm.

[0037] Specific implementation method seven: Combination Figure 5 This embodiment further defines the steam turbine described in Specific Embodiment 1. This embodiment describes a 660MW-class high-efficiency ultra-supercritical flexible deep-tuning steam turbine for high-altitude areas. The low-pressure main body module V includes a low-pressure regulating end steam seal 38, a low-pressure rotor 39, a regulating end bellows 40, a low-pressure outer cylinder 41, a regulating end exhaust guide ring 42, a regulating end last-stage moving blade 43, a first atmospheric valve 44, a low-pressure inner cylinder 45, a regulating end last-stage diaphragm 46, a regulating end secondary last-stage diaphragm 47, and a regulating end secondary last-stage diaphragm... Plate 48, Second stage stationary vane at adjusting end 49, Adjusting end baffle sleeve 50, Low-pressure horizontal stationary vane 51, Sealing baffle 53, Electrical end baffle sleeve 54, Electrical end second stage stationary vane 55, Electrical end secondary and final stage baffle 56, Electrical end secondary and final stage baffle 57, Electrical end final stage baffle 58, Electrical end final stage moving vane 59, No. 2 atmospheric valve 60, Electrical end exhaust guide ring 61, Electrical end bellows 62, Low-pressure electrical end steam seal 63, No. 4 bearing housing adjusting end oil baffle ring 64, No. 6 support bearing 65, No. 4 bearing housing 66, Coupling 67, No. 4 bearing housing electrical end oil baffle ring 69;

[0038] A low-pressure adjusting steam seal body 38 is provided at one end of the low-pressure rotor 39, and an adjusting bellows 40 is provided on one side of the low-pressure adjusting steam seal body 38 on the low-pressure rotor 39. A low-pressure outer cylinder 41 is provided in the middle of the outer surface of the low-pressure rotor 39. A first atmospheric valve 44 and a second atmospheric valve 60 are provided sequentially along the length direction on the outer surface of the low-pressure outer cylinder 41. A low-pressure inner cylinder 45 is provided inside the low-pressure outer cylinder 41. The low-pressure inner cylinder 45 is provided sequentially along the axial direction as follows: adjusting exhaust steam guide ring 42, adjusting final stage moving vane 43, adjusting final stage baffle 46, adjusting secondary final stage baffle 47, adjusting secondary final stage baffle 48, adjusting second stage stationary vane 49, adjusting baffle sleeve 50, low-pressure transverse stationary vane 51, sealing baffle 53, electric end baffle sleeve 54, and electric end second stage stationary vane 55. The low-pressure rotor 39 has an electric terminal secondary and final stage partition 56, an electric terminal secondary and final stage partition 57, an electric terminal final stage partition 58, an electric terminal final stage moving blade 59, and an electric terminal exhaust guide ring 61. On the outer surface of the other end of the low-pressure rotor 39, an electric terminal corrugated section 62 and a low-pressure electric terminal steam seal body 63 are arranged sequentially along the axial direction. The other end of the low-pressure rotor 39 is inserted into the inner ring of the No. 6 support bearing 65 inside the No. 4 bearing housing 66. The upper surface of the No. 4 bearing housing 66 is provided with a turning device 68. After the power input end of the turning device 68 passes through the No. 4 bearing housing 66, it is connected to the low-pressure rotor 39 through a coupling 67. The No. 4 bearing housing 66 has a No. 4 bearing housing adjusting end oil baffle ring 64 in the middle of one side and a No. 4 bearing housing 66 has a No. 4 bearing housing electric terminal oil baffle ring 69 in the middle of the other side.

[0039] In this specific implementation, the low-pressure body module IV is designed with an inner and outer double-layer cylinder, giving the low-pressure flow excellent adaptability to variable loads and meeting the unit's flexible operation and deep peak shaving requirements. Both the regulating-end final-stage blade 43 and the electric-end final-stage blade 59 are designed as 1100mm-class deep peak shaving blades, with a rounded fir tree shape at the blade root, connected to adjacent blades by an integral shroud, and a raised tie rod connecting the entire ring structure. Three-dimensional flow analysis of the final and second-final-stage blades shows good flow characteristics along the entire radial direction, without any flow splitting, counterflow, or uneven flow. Furthermore, to ensure vibration safety before delivery, dynamic frequency tuning tests are performed on the 1100mm blades to ensure that each dynamic frequency effectively avoids the "three key points" resonance, guaranteeing the unit's deep peak shaving and rapid load change requirements. The blade structure has been strengthened for high back pressure conditions, achieving a maximum back pressure adaptability of 60kPa, fully meeting the needs of units in high-altitude areas. Because the exhaust steam temperature is high under high back pressure operation, it usually triggers water spraying in the low-pressure exhaust area for cooling, causing water erosion on the last-stage blades. This invention optimizes the water erosion resistance of the last-stage blades by using laser solution strengthening on the inlet side and supersonic flame spraying on the outlet side to improve their water erosion resistance. To further reduce low-pressure loss, the low-pressure inner cylinder of this unit adopts a 360° volute inlet cast iron inner cylinder and is equipped with an adjusting end exhaust guide ring 42 and an electric end exhaust guide ring 61, effectively reducing inlet and exhaust pressure loss and improving the efficiency of the low-pressure module.

[0040] Specific implementation method eight: Combination Figure 5 This embodiment further defines the steam turbine described in Specific Embodiment Seven. The 660MW-class high-efficiency ultra-supercritical flexible deep-tuning steam turbine applied in high-altitude areas described in this embodiment uses 1100mm-class deep peak-shaving blades for both the adjusting end final stage moving blade 43 and the electric end final stage moving blade 59. The blade root is arc-shaped like a fir tree and is connected to adjacent blades by an integral shroud. The middle adopts a boss tie rod full-circle connection structure.

Claims

1. A 660MW-class high-efficiency ultra-supercritical flexible deep-tuning steam turbine for use in high-altitude areas, characterized in that: It includes high-pressure valves (Ⅰ), high-pressure body module (Ⅱ), medium-pressure valves (Ⅲ), medium-pressure body module (Ⅳ), low-pressure body module (Ⅴ) and condenser (Ⅵ); A high-pressure valve (I) is provided at each of the main steam inlets on both sides of the high-pressure main body module (II). The output end of the high-pressure main body module (II) is connected to the input end of the medium-pressure main body module (IV). A medium-pressure valve (III) is provided at each of the medium-pressure steam inlets on both sides of the medium-pressure main body module (IV). The output end of the medium-pressure main body module (IV) is connected to the input end of the low-pressure main body module (V). The output end of the low-pressure main body module (V) is connected to the power input end of the turning gear device (68). A condenser (VI) is provided at the bottom of the low-pressure main body module (V).

2. The 660MW-class high-efficiency ultra-supercritical flexible deep-tuning steam turbine for high-altitude areas according to claim 1, characterized in that: The interior of the medium-pressure main body module (Ⅳ) is connected to the interior of the low-pressure main body module (Ⅴ) through a medium-low pressure connecting pipe (52).

3. A 660MW-class high-efficiency ultra-supercritical flexible deep-tuning steam turbine for high-altitude areas as described in claim 1, characterized in that: The high-pressure main body module (II) includes a No. 1 bearing housing (1), a No. 1 support bearing (2), a bearing housing oil baffle ring (3), a high-pressure adjusting end steam seal body (4), a high-pressure outer cylinder (5), a high-pressure inner cylinder (6), a high-pressure moving blade (7), a high-pressure rotor (8), a high-pressure stationary blade (9), a high-pressure transverse guide vane (10), a high-pressure electric end steam seal body (11), a No. 2 bearing housing adjusting end oil baffle ring (12), a No. 2 support bearing (13), a thrust bearing (14), a No. 2 bearing housing (15), a No. 3 support bearing (16), and a No. 2 bearing housing electric end oil baffle ring (17). One end of the high-pressure rotor (8) is inserted into the inner ring of the No. 1 support bearing (2) inside the No. 1 bearing housing (1), and a bearing housing oil retaining ring (3) is provided on the high-pressure rotor (8) at the insertion port of the No. 1 bearing housing (1). The high-pressure rotor (8) is provided with a high-pressure outer cylinder (5) and a high-pressure inner cylinder (6) in sequence along the length direction, and a high-pressure moving blade (7), a high-pressure stationary blade (9), and a high-pressure transverse guide blade (10) are provided in sequence along the axis inside the high-pressure inner cylinder (6). The high-pressure moving blade (7) is set on the high-pressure rotor (8), and a high-pressure adjusting end steam seal is provided between the outer surface of the high-pressure rotor (8) and the input port of one end of the high-pressure outer cylinder (5). 4) A high-pressure electric end steam seal (11) is provided between the outer surface of the high-pressure rotor (8) and the output port of the other end of the high-pressure outer cylinder (5). A second support bearing (13), a thrust bearing (14) and a third support bearing (16) are provided sequentially along the axial direction on the other end of the high-pressure rotor (8). The second support bearing (13), the thrust bearing (14) and the third support bearing (16) are all located inside the second bearing housing (15). The input end of the second bearing housing (15) is provided with a second bearing housing adjustment end oil baffle ring (12), and the output end of the second bearing housing (15) is provided with a second bearing housing electric end oil baffle ring (17).

4. A 660MW-class high-efficiency ultra-supercritical flexible deep-tuning steam turbine for high-altitude areas as described in claim 3, characterized in that: The high-pressure inner cylinder (6) is a barrel-shaped cylinder, and the high-pressure inner cylinder (6) adopts a 2×180° tangential volute steam inlet method.

5. A 660MW-class high-efficiency ultra-supercritical flexible deep-tuning steam turbine for high-altitude areas according to claim 1, characterized in that: The medium-pressure main body module (Ⅳ) includes a medium-pressure adjusting end steam seal body (18), a medium-pressure outer cylinder (19), a medium-pressure adjusting end baffle sleeve (20), medium-pressure reverse 1-15 moving blades (21), medium-pressure reverse 7-15 stationary blades (22), a medium-pressure inner cylinder (23), medium-pressure reverse 1-6 stage stationary blades (24), a medium-pressure first stage baffle (25), a medium-pressure rotor cooling device (26), medium-pressure forward 1-6 stage stationary blades (27), medium-pressure forward 7-15 stationary blades (28), a medium-pressure rotor (29), medium-pressure forward 1-15 moving blades (30), a medium-pressure electric end baffle sleeve (31), a medium-pressure electric end steam seal body (32), a No. 3 bearing box adjusting end oil baffle ring (33), a No. 4 support bearing (34), a No. 3 bearing box (35), a No. 5 support bearing (36), and a No. 3 bearing box electric end oil baffle ring (37). A medium-pressure adjusting steam seal (18) is provided on the input end of the medium-pressure outer cylinder (19). After the end of the medium-pressure rotor (29) passes through the interior of the medium-pressure outer cylinder (19), it is inserted into the interior of the No. 3 bearing housing (35). The No. 4 support bearing (34), the No. 5 support bearing (36), and the No. 3 bearing housing electrical end oil baffle ring (37) are arranged sequentially along the axial direction inside the No. 3 bearing housing (35). The end of the medium-pressure rotor (29) and the insertion port of the No. 3 bearing housing (35) are provided with the No. 3 bearing housing adjusting steam baffle ring (33). A medium-pressure electrical end steam seal (32) is provided at the connection between the outer surface of the medium-pressure rotor (29) and the output end of the medium-pressure outer cylinder (19). A medium-pressure rotor cooling device (26) is provided in the middle of the outer surface of the medium-pressure outer cylinder (19). The middle part of the pressure rotor (29) is provided with a medium pressure inner cylinder (23). The interior of the medium pressure inner cylinder (23) is provided with medium pressure reverse 1-15 moving blades (21), medium pressure reverse 1-6 stationary blades (24), medium pressure first stage baffle (25), medium pressure forward 1-6 stationary blades (27) and medium pressure forward 1-15 moving blades (30) in sequence along the axial direction. One end of the medium pressure inner cylinder (23) is provided with a medium pressure adjusting end baffle sleeve (20), and the other end of the medium pressure inner cylinder (23) is provided with a medium pressure electric end baffle sleeve (31). The interior of the medium pressure adjusting end baffle sleeve (20) is provided with medium pressure reverse 7-15 stationary blades (22) along the axial direction. The interior of the medium pressure electric end baffle sleeve (31) is provided with medium pressure forward 7-15 stationary blades (28) along the axial direction.

6. A 660MW-class high-efficiency ultra-supercritical flexible deep-tuning steam turbine for high-altitude areas according to claim 5, characterized in that: The medium-pressure first-stage diaphragm (25) is an impulse diaphragm.

7. A 660MW-class high-efficiency ultra-supercritical flexible deep-tuning steam turbine for high-altitude areas according to claim 1, characterized in that: The low-pressure main body module (V) includes a low-pressure adjusting end steam seal (38), a low-pressure rotor (39), an adjusting end bellows (40), a low-pressure outer cylinder (41), an adjusting end exhaust guide ring (42), an adjusting end final stage moving vane (43), a first atmospheric valve (44), a low-pressure inner cylinder (45), an adjusting end final stage baffle (46), an adjusting end secondary final stage baffle (47), an adjusting end secondary secondary final stage baffle (48), an adjusting end second stage stationary vane (49), an adjusting end baffle sleeve (50), a low-pressure transverse stationary vane (51), and a sealing baffle (53). 、Electric end baffle sleeve (54), electric end second stage stationary vane (55), electric end secondary final stage baffle (56), electric end secondary final stage baffle (57), electric end final stage baffle (58), electric end final stage moving vane (59), No. 2 atmospheric valve (60), electric end exhaust guide ring (61), electric end bellows (62), low pressure electric end steam seal (63), No. 4 bearing box adjusting end oil baffle ring (64), No. 6 support bearing (65), No. 4 bearing box (66), coupling (67), No. 4 bearing box electric end oil baffle ring (69); A low-pressure adjusting steam seal body (38) is provided at one end of the low-pressure rotor (39), and an adjusting bellows (40) is provided on one side of the low-pressure adjusting steam seal body (38) on the low-pressure rotor (39). A low-pressure outer cylinder (41) is provided in the middle of the outer surface of the low-pressure rotor (39). A first atmospheric valve (44) and a second atmospheric valve (60) are provided sequentially along the length direction on the outer surface of the low-pressure outer cylinder (41). A low-pressure inner cylinder (45) is provided inside the low-pressure outer cylinder (41). A adjusting exhaust steam guide ring (42), adjusting end stage moving vane (43), adjusting end stage partition (46), adjusting end secondary stage partition (47), adjusting end secondary stage partition (48), adjusting end second stage stationary vane (49), adjusting end partition sleeve (50), low-pressure horizontal stationary vane (51), sealing partition (53), electric end partition sleeve (54), and electric end second stage stationary vane (55) are provided sequentially along the axial direction. 55), Electric terminal secondary and final stage partition (56), electric terminal secondary and final stage partition (57), electric terminal final stage partition (58), electric terminal final stage moving blade (59) and electric terminal exhaust guide ring (61), the other end of the low-pressure rotor (39) is provided with electric terminal corrugated section (62) and low-pressure electric terminal steam seal (63) in sequence along the axial direction on the outer surface of the other end, the other end of the low-pressure rotor (39) is inserted into the inner ring of the No. 6 support bearing (65) inside the No. 4 bearing housing (66), and the upper surface of the No. 4 bearing housing (66) is provided with a turning device (68), the power input end of the turning device (68) passes through the No. 4 bearing housing (66) and is connected to the low-pressure rotor (39) through a coupling (67), the middle of one side of the No. 4 bearing housing (66) is provided with a No. 4 bearing housing adjusting end oil baffle ring (64), and the middle of the other side of the No. 4 bearing housing (66) is provided with a No. 4 bearing housing electric terminal oil baffle ring (69).

8. A 660MW-class high-efficiency ultra-supercritical flexible deep-tuning steam turbine for high-altitude areas according to claim 7, characterized in that: The terminal blade (43) and the electrical terminal blade (59) both adopt 1100mm-level depth peak-shaving blades. The root part is a rounded fir tree shape and is connected to the adjacent blades by an integral shroud. The middle part adopts a boss tie rod full-circle connection structure.

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