CN114483227A - Supercritical 145MW grade single intermediate reheating reaction type steam turbine - Google Patents

Supercritical 145MW grade single intermediate reheating reaction type steam turbine Download PDF

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Publication number
CN114483227A
CN114483227A CN202111604146.3A CN202111604146A CN114483227A CN 114483227 A CN114483227 A CN 114483227A CN 202111604146 A CN202111604146 A CN 202111604146A CN 114483227 A CN114483227 A CN 114483227A
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CN
China
Prior art keywords
steam
pressure
bearing box
bearing
pressure cylinder
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Pending
Application number
CN202111604146.3A
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Chinese (zh)
Inventor
刘洋
鲍大虎
丁莹
姜喜星
邹婉秋
黄智敏
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Harbin Turbine Co Ltd
Hadian Power Equipment National Engineering Research Center Co Ltd
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Harbin Turbine Co Ltd
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Application filed by Harbin Turbine Co Ltd filed Critical Harbin Turbine Co Ltd
Priority to CN202111604146.3A priority Critical patent/CN114483227A/en
Publication of CN114483227A publication Critical patent/CN114483227A/en
Pending legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K7/00—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating
    • F01K7/16—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating the engines being only of turbine type
    • F01K7/22—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating the engines being only of turbine type the turbines having inter-stage steam heating
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D17/00—Regulating or controlling by varying flow
    • F01D17/10—Final actuators
    • F01D17/105—Final actuators by passing part of the fluid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D25/00—Component parts, details, or accessories, not provided for in, or of interest apart from, other groups
    • F01D25/16—Arrangement of bearings; Supporting or mounting bearings in casings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D25/00—Component parts, details, or accessories, not provided for in, or of interest apart from, other groups
    • F01D25/16—Arrangement of bearings; Supporting or mounting bearings in casings
    • F01D25/162—Bearing supports
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D25/00—Component parts, details, or accessories, not provided for in, or of interest apart from, other groups
    • F01D25/28—Supporting or mounting arrangements, e.g. for turbine casing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D25/00—Component parts, details, or accessories, not provided for in, or of interest apart from, other groups
    • F01D25/30—Exhaust heads, chambers, or the like
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D5/00—Blades; Blade-carrying members; Heating, heat-insulating, cooling or antivibration means on the blades or the members
    • F01D5/02—Blade-carrying members, e.g. rotors
    • F01D5/027—Arrangements for balancing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D5/00—Blades; Blade-carrying members; Heating, heat-insulating, cooling or antivibration means on the blades or the members
    • F01D5/30—Fixing blades to rotors; Blade roots ; Blade spacers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D9/00—Stators
    • F01D9/02—Nozzles; Nozzle boxes; Stator blades; Guide conduits, e.g. individual nozzles
    • F01D9/04—Nozzles; Nozzle boxes; Stator blades; Guide conduits, e.g. individual nozzles forming ring or sector
    • F01D9/042—Nozzles; Nozzle boxes; Stator blades; Guide conduits, e.g. individual nozzles forming ring or sector fixing blades to stators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K7/00—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating
    • F01K7/34—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating the engines being of extraction or non-condensing type; Use of steam for feed-water heating
    • F01K7/38—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating the engines being of extraction or non-condensing type; Use of steam for feed-water heating the engines being of turbine type

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Turbine Rotor Nozzle Sealing (AREA)

Abstract

The invention relates to a supercritical 145MW grade primary intermediate reheating reaction type steam turbine, which relates to a 145MW grade steam turbine and aims to solve the problems of low efficiency and low circulation efficiency of the existing medium and small size steam turbine cylinders; the accent end of well low pressure jar is supported on the well bearing box, and the electricity end supports on the basis, and this application belongs to the steam turbine field.

Description

Supercritical 145MW grade single intermediate reheating reaction type steam turbine
Technical Field
The invention relates to a 145MW grade steam turbine, in particular to a supercritical 145MW grade primary intermediate reheating reaction type steam turbine, and relates to the technical field of steam turbines.
Background
The existing middle and small-sized steam turbines in China are early in forming design, mostly have high-temperature and high-pressure parameters, generally have the problems of low main steam parameters, unreasonable system design and structural design and the like, and have low unit circulation efficiency, high power supply coal consumption, low energy utilization rate and large pollution emission.
Disclosure of Invention
The invention aims to solve the problems of low efficiency and low cycle efficiency of the existing medium and small-sized steam turbine cylinder, and further provides a supercritical 145MW grade primary intermediate reheating reaction steam turbine.
The technical scheme adopted by the invention for solving the problems is as follows:
the high-pressure oil pump comprises a high-pressure cylinder, a middle-low pressure cylinder, a front bearing box, a middle bearing box, a rear bearing box, a high-pressure rotor, a middle-low pressure rotor, a first bearing, a second bearing, a third bearing, a main oil pump, a thrust bearing and two sliding mechanisms, wherein the middle-low pressure rotor and the high-pressure rotor are sequentially connected from left to right; the adjusting end of the medium-low pressure cylinder is supported on a middle bearing box, the electric end is supported on the basis, a thrust bearing is arranged in the middle bearing box, the thrust bearing is arranged on a rotor thrust disc outside the high-pressure rotor, a main oil pump is arranged in a front bearing box, and the main oil pump is connected with the front bearing box, the middle bearing box, a rear bearing box and the thrust bearing through pipelines and supplies oil to the front bearing box, the middle bearing box, the rear bearing box and the thrust bearing.
Further, install two high pressure steam supplementing mouths and two balanced hub steam leakage mouths on the high pressure jar, two high pressure steam supplementing mouths symmetry are installed on high pressure jar top and bottom, and two balanced hub steam leakage mouths symmetry are installed on 1 top of high pressure jar and bottom, the bottom of high pressure jar is equipped with high pressure steam extraction mouth and steam extraction mouth, and balanced hub steam leakage mouth, high pressure steam supplementing mouth, steam extraction mouth and high pressure steam extraction mouth are close to first bearing setting from left to right in proper order.
Furthermore, the bottom of the medium and low pressure cylinder is provided with an eight steam extraction port, a seven steam extraction port, a six steam extraction port, a five steam extraction port, a three steam extraction port and a four steam extraction port from left to right in sequence.
Furthermore, the high-pressure main steam adjusting combination valve is arranged on the right side of the high-pressure cylinder and located on the main steam pipeline, and a valve shell of the high-pressure main steam adjusting combination valve is directly connected with the high-pressure cylinder through a flange bolt.
Furthermore, the device also comprises two reheating main steam adjusting combined valves, wherein the two reheating main steam adjusting combined valves are respectively positioned at the left side and the right side of the middle-low pressure cylinder, and the two reheating main steam adjusting combined valves are respectively connected with a reheating steam pipeline of the middle-low pressure cylinder.
Furthermore, all the movable and static blades of the high-pressure part adopt an assembly type structure, and all the movable and static blades of the middle-low pressure part except the last two stages of static blades also adopt the assembly type structure.
Furthermore, the adjusting end of the medium and low pressure cylinder is fixedly connected with the middle bearing box through an I-beam, the middle bearing box is fixedly connected with the high pressure cylinder through an I-beam, and the high pressure cylinder is fixedly connected with the front bearing box through an I-beam.
The invention has the beneficial effects that:
1. the main steam parameters of the unit are improved to 24.2MPa and 600 ℃, and the circulation efficiency is fundamentally improved;
2. the high-pressure module and the medium-pressure module of the unit are designed in a cylinder-separated manner, the high-pressure through-flow length is not limited by the bearing span, the optimized setting of the number of stages can be achieved, and higher cylinder efficiency is obtained;
3. the unit adopts full-cycle steam admission, the high-pressure main steam adjusting combined valve is directly connected with the cylinder, and the design of no adjusting stage is adopted, so that the steam admission loss is reduced to the maximum extent, and the enthalpy drop of the unit is distributed on the reaction pressure level with small enthalpy drop, so that higher stage efficiency can be obtained;
4. all the movable and fixed blades of high pressure adopt an assembly type structure, and compared with the traditional welding clapboard, the assembly type structure has no welding line, thereby avoiding welding deformation and better ensuring through-flow precision;
5. the middle-low pressure part is designed to be of a cylinder closing structure, steam is exhausted from the single side downwards, meanwhile, the high-pressure rotor and the middle-low pressure rotor adopt a 3-bearing supporting mode, the length of the unit is shortened to the maximum extent on the premise that the unit is high in circulation efficiency and safety, the occupied area of the unit is reduced, the space is saved, and the construction cost of a power plant is reduced.
6. The high-pressure module balances the steam leakage of the hub, can lead out high-temperature steam, prevents the high-pressure end steam seal from being overhigh in temperature, can reduce the material selection of a steam seal system pipeline, and saves the cost.
7. The high-pressure through-flow reverse arrangement and the medium-pressure double-layer cylinder part through-flow reverse arrangement can effectively reduce the axial thrust of the unit, reduce the diameter of the balance hub, reduce the steam leakage amount of the steam seal of the balance hub, increase the thermal cycle efficiency of the unit, reduce the weight of the rotor and increase the adjustment range of the critical rotating speed of the unit.
8. The exhaust cylinder is used as an absolute dead point of stator thermal expansion, the thrust bearing is used as a relative dead point of rotor thermal expansion, through-flow reverse arrangement is combined, expansion difference between moving and static can be reduced at the steam inlet temperature of 600 ℃, more through-flow stages can be arranged in the same bearing span, and the heat efficiency of the unit is improved.
Drawings
FIG. 1 is a schematic view of the overall structure of the present invention;
FIG. 2 is a top view of FIG. 1;
FIG. 3 is a schematic structural diagram of a high-pressure main steam combination valve;
FIG. 4 is a schematic diagram of a reheat main steam governor combination valve.
FIG. 5 is a schematic view of a supercritical 145MW grade single intermediate reheat reaction steam turbine of the present application.
Detailed Description
The first embodiment is as follows: the embodiment is described with reference to fig. 1-5, and the supercritical 145MW grade primary intermediate reheating reaction type steam turbine includes a high pressure cylinder 1, a medium and low pressure cylinder 2, a front bearing box 3, a middle bearing box 4, a rear bearing box 5, a high pressure rotor 8, a medium and low pressure rotor 9, a first bearing 10, a second bearing 11, a third bearing 12, a main oil pump 13, a thrust bearing 14 and two sliding mechanisms 15, wherein the medium and low pressure rotor 9 and the high pressure rotor 8 are connected in sequence from left to right, the medium and low pressure cylinder 2 is sleeved on the medium and low pressure rotor 9, the high pressure cylinder 1 is sleeved on the high pressure rotor 8, the electric end of the medium and low pressure rotor 9 is sleeved with the third bearing 12, the electric end and the adjustment end of the high pressure rotor 8 are respectively sleeved with the second bearing 11 and the first bearing 10, the first bearing 10 is located in the front bearing box 3, the second bearing 11 is located in the middle bearing box 4, the bottom of the front bearing box 3 and the middle bearing box 4 are respectively provided with one sliding mechanism 15, the third bearing 12 is positioned in the rear bearing box 5, and the adjusting end and the electric end of the high-pressure cylinder 1 are respectively supported on the front bearing box 3 and the middle bearing box 4; the adjusting end of the medium and low pressure cylinder 2 is supported on a middle bearing box 4, the electric end is supported on the basis, a thrust bearing 14 is arranged in the middle bearing box 4, the thrust bearing 14 is arranged on a rotor thrust disc outside a high pressure rotor 8, a main oil pump 13 is arranged in a front bearing box 3, and the main oil pump 13 is connected with the front bearing box 3, the middle bearing box 4, a rear bearing box 5 and the thrust bearing 14 through pipelines and supplies oil to the front bearing box 3, the middle bearing box 4, the rear bearing box 5 and the thrust bearing 14.
The front bearing box 3 and the middle bearing box 4 are respectively installed on the basis through the sliding mechanism 15, the rear bearing box 5 is installed on the basis through a floor structure, the adjusting end and the electric end of the high-pressure cylinder 1 are respectively supported on the front bearing box 3 and the middle bearing box 4 through lower claws, the adjusting end of the medium and low-pressure cylinder 2 is supported on the middle bearing box 4 through lower claws, the lower half parts of the high-pressure cylinder 1 and the medium and low-pressure cylinder 2 are provided with I-shaped beams, a push-pull rod mechanism is formed by the I-shaped beams and the front bearing box 3 and the middle bearing box 4, the electric end of the medium and low-pressure cylinder 2 is installed on the basis, and when the unit is heated and expanded, the front bearing box 3, the high-pressure cylinder 1 and the middle bearing box 4 are expanded and moved along the length direction of a rotor of the unit through the sliding mechanism 15 to serve as a push-pull mechanism for thermal expansion of a stator of a steam turbine.
In the embodiment, the low-pressure rotor 9 and the high-pressure rotor 8 are connected together through a coupling bolt; the high-pressure rotor 8 and the middle-low pressure rotor 9 are integrally forged rotors, the high-temperature section and the low-temperature section of the middle-low pressure rotor 9 are tightened by bolts, and the front section and the rear section have different mechanical properties, so that the high-temperature strength requirement of the high-temperature section is met, and the high-strength and low-brittleness transition temperature value performance of the low-temperature section is also met.
The high-pressure cylinder 1 is a double-layer cylinder structure, the outer cylinder adopts a traditional split high-narrow flange bolt sealing structure, the inner cylinder adopts a novel cylindrical drying lantern ring sealing structure, the through-flow pressure level of the high-pressure cylinder 1 is reversely arranged, and 35-level small enthalpy drop reaction type blades are arranged. The first bearing, the second bearing and the thrust bearing of the high-pressure rotor 8 are welded with low-Cr alloy to form a monobloc forging rotor. The adjusting end of the medium and low pressure cylinder 2 is of a double-layer cylinder structure, the through-flow pressure level of the inner cylinder is reversely arranged, the total 14-level small enthalpy drop reaction type blades are arranged, 14-level rear steam flows around to the front of the 15 th level pressure level of the medium and low pressure through an interlayer between the inner cylinder and the outer cylinder, the 15 th level rear of the medium and low pressure cylinder 2 is of a single-layer cylinder structure, and the 15 th to 25 th level pressure levels are arranged in the forward direction. The middle and low pressure rotor 9 is a two-section butt joint structure, both are integrally forged rotors, and the two sections of rotors are made of different materials and are respectively used in high and low temperature regions.
The second embodiment is as follows: the embodiment is described with reference to fig. 1, in the embodiment, two high-pressure steam supply ports 1-3 and two balance hub steam leakage ports 1-4 are installed on the high-pressure cylinder 1, the two high-pressure steam supply ports 1-3 are symmetrically installed on the top end and the bottom end of the high-pressure cylinder 1, the two balance hub steam leakage ports 1-4 are symmetrically installed on the top end and the bottom end of the high-pressure cylinder 1, the bottom of the high-pressure cylinder 1 is provided with a high-pressure steam exhaust port 1-1 and a first steam extraction port 1-2, and the balance hub steam leakage port 1-4, the high-pressure steam supply port 1-3, the first steam extraction port 1-2 and the high-pressure steam extraction port 1-1 are sequentially arranged close to the first bearing 10 from left to right. The two balance hub steam leakage openings 1-4 are connected with a steam turbine bypass system to lead out high-temperature steam in the high-pressure cylinder balance hub and reduce the steam leakage temperature of the end steam seal of the high-pressure cylinder.
Other components and connections are the same as those in the first embodiment.
The third concrete implementation mode: the embodiment is described with reference to fig. 1, and in the embodiment, the bottom of the medium and low pressure cylinder 2 is provided with an eighth steam extraction port 2-1, a seventh steam extraction port 2-2, a sixth steam extraction port 2-3, a fifth steam extraction port 2-4, a third steam extraction port 2-5 and a fourth steam extraction port 2-6 in sequence from left to right.
Other components and connection relationships are the same as those in the first or second embodiment.
The fourth concrete implementation mode: the embodiment is described with reference to fig. 1, and the embodiment further includes a high-pressure main steam adjusting combination valve 6, the high-pressure main steam adjusting combination valve 6 is disposed on the right side of the high-pressure cylinder 1 and is located on the main steam pipeline, and a valve housing of the high-pressure main steam adjusting combination valve 6 is directly connected with the high-pressure cylinder 1 by a flange bolt.
The high-pressure main steam regulating combined valve 6 comprises a high-pressure main steam valve, a high-pressure steam supplementing valve and a high-pressure regulating valve, the high-pressure main steam valve is connected with a steam inlet of the steam turbine, the high-pressure regulating valve is connected with a main steam inlet of a cylinder body of the steam turbine, and the high-pressure steam supplementing valve is connected with the high-pressure steam supplementing ports 1-3. And the steam turbine unit is put into use when exceeding the rated working condition.
Other components and connection relationships are the same as those in the first, second or third embodiment.
The fifth concrete implementation mode: this embodiment is described with reference to fig. 1, and: the double-cylinder reheating steam turbine further comprises two reheating main steam adjusting combined valves 7, the two reheating main steam adjusting combined valves 7 are respectively located on the left side and the right side of the middle and low pressure cylinder 2, and the two reheating main steam adjusting combined valves 7 are respectively connected with a reheating steam pipeline of the middle and low pressure cylinder 2. The reheating main steam adjusting combined valve 7 adopts three-point floating support, and reserves enough joint allowable force and allowable moment for a reheating steam pipeline.
Other components and connections are the same as those of the first, second, third or fourth embodiments.
The sixth specific implementation mode: the present embodiment will be described with reference to fig. 1, and all the moving and stationary blades of the high-pressure portion according to the present embodiment are of an assembled structure.
All the moving and static blades of the high-pressure part and the rest moving and static blades of the middle-low pressure part except the last two stages of static blades are all in an assembled structure. Compared with the existing welding partition plate, the assembly type structure has no welding line, avoids welding deformation and better ensures the through-flow precision.
Other components and connection relationships are the same as those in the first, second, third, fourth, or fifth embodiment.
The seventh embodiment: referring to fig. 1, the adjusting end of the middle/low pressure cylinder 2 and the middle bearing housing 4 are fixedly connected by an i-beam, the middle bearing housing 4 and the high pressure cylinder 1 are fixedly connected by an i-beam, and the high pressure cylinder 1 and the front bearing housing 3 are fixedly connected by an i-beam.
Other components and connection relationships are the same as those in the first, second, third, fourth, fifth or sixth embodiment.
Although the present invention has been described with reference to a preferred embodiment, it should be understood that various changes, substitutions and alterations can be made herein without departing from the spirit and scope of the invention as defined by the appended claims.

Claims (7)

1. A supercritical 145MW grade once intermediate reheating reaction type steam turbine is characterized in that: the high-pressure oil pump comprises a high-pressure cylinder (1), a medium-low pressure cylinder (2), a front bearing box (3), a middle bearing box (4), a rear bearing box (5), a high-pressure rotor (8), a medium-low pressure rotor (9), a first bearing (10), a second bearing (11), a third bearing (12), a main oil pump (13), a thrust bearing (14) and two sliding mechanisms (15), wherein the medium-low pressure rotor (9) and the high-pressure rotor (8) are sequentially connected from left to right, the medium-low pressure cylinder (2) is sleeved on the medium-low pressure rotor (9), the high-pressure cylinder (1) is sleeved on the high-pressure rotor (8), the electric end of the medium-low pressure rotor (9) is sleeved with the third bearing (12), the electric end and the adjusting end of the high-pressure rotor (8) are respectively sleeved with the second bearing (11) and the first bearing (10), the first bearing (10) is positioned in the front bearing box (3), the second bearing (11) is positioned in the middle bearing box (4), the bottom of the front bearing box (3) and the bottom of the middle bearing box (4) are respectively provided with a two-sliding mechanism (15), the third bearing (12) is positioned in the rear bearing box (5), and the adjusting end and the electric end of the high-pressure cylinder (1) are respectively supported on the front bearing box (3) and the middle bearing box (4); the adjusting end of the medium and low pressure cylinder (2) is supported on a middle bearing box (4), the electric end is supported on the basis, a thrust bearing (14) is arranged in the middle bearing box (4), the thrust bearing (14) is installed on a rotor thrust disc outside a high-pressure rotor (8), a main oil pump (13) is installed in a front bearing box (3), and the main oil pump (13) is connected with the front bearing box (3), the middle bearing box (4), a rear bearing box (5) and the thrust bearing (14) through pipelines and supplies oil to the front bearing box (3), the middle bearing box (4), the rear bearing box (5) and the thrust bearing (14).
2. The supercritical 145MW class single intermediate reheat reaction steam turbine of claim 1, wherein: the high-pressure steam leakage device is characterized in that two high-pressure steam compensating ports (1-3) and two balance hub steam leakage ports (1-4) are arranged on the high-pressure cylinder (1), the two high-pressure steam compensating ports (1-3) are symmetrically arranged at the top end and the bottom end of the high-pressure cylinder (1), the two balance hub steam leakage ports (1-4) are symmetrically arranged at the top end and the bottom end of the high-pressure cylinder (1), a high-pressure steam exhaust port (1-1) and a first steam exhaust port (1-2) are arranged at the bottom of the high-pressure cylinder (1), and the balance hub steam leakage ports (1-4), the high-pressure steam compensating ports (1-3), the first steam exhaust port (1-2) and the high-pressure steam exhaust port (1-1) are sequentially close to the first bearing (10) from left to right.
3. The supercritical 145MW class single intermediate reheat reaction steam turbine of claim 1, wherein: the bottom of the medium and low pressure cylinder (2) is provided with an eight steam extraction port (2-1), a seven steam extraction port (2-2), a six steam extraction port (2-3), a five steam extraction port (2-4), a three steam extraction port (2-5) and a four steam extraction port (2-6) from left to right in sequence.
4. The supercritical 145MW class single intermediate reheat reaction steam turbine of claim 1, wherein: the utility model provides a super critical 145MW grade is reheat reaction type steam turbine in middle of once still includes high pressure main vapour adjusting union valve (6), and high pressure main vapour adjusting union valve (6) set up on the right side of high pressure jar (1), and are located the main steam pipeline, and the valve casing of high pressure main vapour adjusting union valve (6) and high pressure jar (1) are with flange bolt lug connection.
5. The supercritical 145MW class single intermediate reheat reaction steam turbine of claim 1, wherein: the supercritical 145MW grade single intermediate reheat reaction type steam turbine further comprises two reheat main steam adjusting combined valves (7), the two reheat main steam adjusting combined valves (7) are respectively located on the left side and the right side of the middle and low pressure cylinder (2), and the two reheat main steam adjusting combined valves (7) are respectively connected with a reheat steam pipeline of the middle and low pressure cylinder (2).
6. The supercritical 145MW class single intermediate reheat reaction steam turbine of claim 1, wherein: all the stator blades of the high-pressure rotor (8) adopt an assembly type structure.
7. The supercritical 145MW class single intermediate reheat reaction steam turbine of claim 1, wherein: the adjusting end of the middle and low pressure cylinder (2) is fixedly connected with the middle bearing box (4) through an I-beam, the middle bearing box (4) is fixedly connected with the high pressure cylinder (1) through an I-beam, and the high pressure cylinder (1) is fixedly connected with the front bearing box (3) through an I-beam.
CN202111604146.3A 2021-12-24 2021-12-24 Supercritical 145MW grade single intermediate reheating reaction type steam turbine Pending CN114483227A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN202111604146.3A CN114483227A (en) 2021-12-24 2021-12-24 Supercritical 145MW grade single intermediate reheating reaction type steam turbine

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CN202111604146.3A CN114483227A (en) 2021-12-24 2021-12-24 Supercritical 145MW grade single intermediate reheating reaction type steam turbine

Publications (1)

Publication Number Publication Date
CN114483227A true CN114483227A (en) 2022-05-13

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Application Number Title Priority Date Filing Date
CN202111604146.3A Pending CN114483227A (en) 2021-12-24 2021-12-24 Supercritical 145MW grade single intermediate reheating reaction type steam turbine

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CN (1) CN114483227A (en)

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