CN218581665U - Low-pressure last-stage moving blade of steam turbine - Google Patents
Low-pressure last-stage moving blade of steam turbine Download PDFInfo
- Publication number
- CN218581665U CN218581665U CN202222875904.1U CN202222875904U CN218581665U CN 218581665 U CN218581665 U CN 218581665U CN 202222875904 U CN202222875904 U CN 202222875904U CN 218581665 U CN218581665 U CN 218581665U
- Authority
- CN
- China
- Prior art keywords
- blade
- root
- blade body
- section
- steam turbine
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Active
Links
Images
Landscapes
- Turbine Rotor Nozzle Sealing (AREA)
Abstract
The utility model discloses a low-pressure last-stage moving blade of a steam turbine, which relates to the technical field of steam turbine blades, aims at the problem that the last-stage blade for a high-rotating-speed industrial steam turbine is not enough, aims at an industrial steam turbine unit with rotating speed and power which are more than ten thousand, provides an autonomously developed last-stage moving blade with excellent variable working condition pneumatic performance and strength vibration performance, and is suitable for industrial steam turbines with the backpressure of 5-30 KPa, the speed regulation range of 6000 rpm-9000 rpm and the steam discharge flow of 55 t/h; the inclined three-tooth longitudinal tree-shaped blade root and the semi-split loose lacing wire full-circle connecting structure are adopted, the pneumatic performance under the variable working condition is excellent, the strength is high, the damping characteristic is good, the blade and the rotor are firmly and stably combined, and the safety requirement of the blade can be met.
Description
Technical Field
The utility model relates to a steam turbine blade technical field, concretely relates to steam turbine low pressure last stage moving blade.
Background
The industrial steam turbine has the characteristics of flexibility, stability and reliability, is widely applied to the fields of petroleum, chemical industry, metallurgy, electric power, textile industry and the like, and plays a considerable role in national economy. Meanwhile, in various production processes of modern enterprises, a large number of links of power and heat energy of byproducts exist, the cascade utilization of the waste heat of the byproducts can be fully realized by reasonably configuring corresponding industrial turbines in the production processes, the heat energy is converted into electric energy by the aid of the working of the turbines or power support is provided for equipment such as fans, pumps, presses and other process flow devices, so that the purposes of improving energy utilization rate and fully saving energy are achieved, and the industrial turbines in the market have wide requirements.
The overall single-machine power grade of the industrial steam turbine is far lower than that of a generator set, and the direction of the industrial steam turbine is to develop towards high rotating speed on the basis of ensuring reliability and maintain higher efficiency. Meanwhile, the operation speed of the industrial steam turbine is mainly determined by a driven device, the rotation speed can reach 7000-10000r/min, the operation is usually variable speed, and the power is from thousands of kilowatts to tens of thousands of kilowatts. The characteristics of high rotating speed and large and frequent operating condition change range of the industrial steam turbine bring great difficulty to the pneumatic and structural design of the low-pressure through-flow last-stage blade, and the high-performance last-stage blade can be designed only by taking overall consideration into consideration, and various factors such as rationality of material selection, manufacturing difficulty and the like are also considered.
In recent years, with the continuous development of industries, the market has a great demand on industrial turbines with thousands to tens of thousands of kilowatts, the final stage blade module system of the existing turbine is mainly below 6000rpm, and the requirement on the steam exhaust area of the small-power high-rotation-speed industrial turbine in modern industries can not be met aiming at a large-power unit with the power of more than 20 MW.
SUMMERY OF THE UTILITY MODEL
The utility model aims to provide an: aiming at the existing problems, the utility model provides a steam turbine low pressure last stage moving blade, aiming at the problem that the last stage blade that the above-mentioned high rotational speed industrial steam turbine used is not enough, with the industrial steam turbine set that rotational speed and power are two too many ten thousand as the target, provide a steam turbine low pressure last stage moving blade that has good variable working condition aerodynamic performance and intensity vibration performance who independently develops, be applicable to the backpressure 5 ~ 30KPa, the speed governing scope 6000rpm ~ 9000rpm, the steam extraction flow volume ~ 55t/h industrial steam turbine within range; the inclined three-tooth longitudinal tree-shaped blade root and the semi-split loose lacing wire full-circle connecting structure are adopted, the pneumatic performance under the variable working condition is excellent, the strength is high, the damping characteristic is good, the blade and the rotor are firmly and stably combined, and the safety requirement of the blade can be met.
The low-pressure last-stage moving blade of the steam turbine comprises a single blade, wherein the single blade comprises a blade root and a blade body; the blade root is positioned at the root of the blade body, the blade root and the blade body are of an integral structure, and the blade body is a special-shaped body formed by superposing a plurality of characteristic sections according to a specific rule; the profile line of the characteristic section is a closed curve formed by an inner arc curve and a back arc curve, and has characteristic parameters: a blade profile mounting angle C, a blade body section chord length B, a blade body section maximum thickness W, a blade body section axial width Xa and a blade body section area A; the superposition rule of characteristic sections is that each section is in continuous and smooth transition from the root end of a blade body to the top end of the blade body along the blade height direction, the root part of the blade body is in a subsonic blade profile, the middle part of the blade body is in a transonic blade profile, the top part of the blade body is in a supersonic blade profile, the blade height Ld of the blade body is 180mm, and the root diameter Dr is 500mm; the relative value of the leaf height Ld monotonically increases from 0.0 to 1.0; correspondingly, the blade profile installation angle C is monotonically reduced from 72.21 degrees to 35.61 degrees; the relative change rule of the blade body section area A from the root section to the top section is monotonically reduced from 2.61 to 1.0; the relative change rule of the axial width Xa of the blade body section from the root section to the top section is monotonically reduced from 2.12 to 1.0; the relative change rule of the chord length B of the blade body section from the root section to the top section is monotonically reduced from 1.30 to 1.0; the relative change rule of the maximum thickness W of the blade body section from the root section to the top section is monotonically reduced from 1.62 to 1.0, the blade profile of the single blade is monotonically twisted and formed along the height, the relative value of the outlet geometric angle alpha 1 is monotonically reduced from 1.795 to 1.0 along the height direction from the blade root to the blade top, and the calculation process of the outlet geometric angle alpha 1 is shown in the following formula (1):
α1＝sin -1 (O/T) (1)
in formula 1, O is the width of the throat of the blade body section outlet, i.e., the minimum distance between the blade profile steam outlet edge F and the back arc D of the adjacent blade body section, and T is the circumferential installation distance of the profile section of the same height of the two adjacent single blades.
Furthermore, a lacing wire hole is formed in the blade body, and the height Lj of the center of the lacing wire hole satisfies the relation that Lj/Ld is more than or equal to 0.68 and less than or equal to 0.825; the diameter phi of the lacing hole satisfies the relational expression of 6.5 mm-10 mm.
Further, the inner arc E and the back arc D of the blade body have a thickness strengthening area which tends to be smooth in the areas matched with the lacing wire holes along the axial direction and the blade height direction of the lacing wire holes.
Due to the adoption of the technical scheme, the weakening condition of the cross section where the lacing wire hole is located can be effectively compensated, and the stress concentration of the joint area of the lacing wire hole and the blade profile is reduced.
Further, the pull rod also comprises a loose pull rod which can penetrate through the pull rod holeAnd is matched with the lacing hole, the diameter of the loose lacing wire
Satisfies the relation:
the length L satisfies the relational expression of 6.7. T1 is more than or equal to L and less than or equal to 6.95. T1; the loose lacing wire forms an arc-shaped structure along the length L direction according to the radius R, and the calculation process of the radius R is shown as the following formula (2):
R＝(Dr/2+Lj) (2)
in formula 2, dr is the blade root diameter, i.e., the diameter of a circle where the root section of the blade body of the single blade is located after the single blade is mounted on the rotor, and Lj is the height position of the lacing hole on the blade body.
Furthermore, the loose lacing wire is divided into equal half lacing wires along the radial direction, and the two half lacing wires can be mutually folded and pass through the lacing wire hole.
Furthermore, it is a plurality of monomer blade encircles the rotor round and the equipartition in the rotor excircle, the blade root limits in the impeller groove on the rotor excircle, the pine lacing wire passes a plurality of blade bodies of lacing wire hole connection, the pine lacing wire encircles the rotor round and forms ring structure.
Furthermore, a blade grid channel is formed between two adjacent single blades, the half lacing bars on the same side are matched with each other to form a half lacing bar ring, and the two half lacing bar rings on the opposite side are combined to form a loose lacing bar ring; in same half lacing wire ring, adjacent half lacing wire terminal surface cooperatees in cascade passageway middle part and forms the handing-over region, handing-over region department is provided with handing-over clearance Ga, and the handing-over region in the two halves lacing wire ring of offside sets up in the cascade passageway of difference.
By adopting the technical scheme, the length of the cantilever at the overhanging end formed by the half lacing wire end part extending out of the lacing wire hole can be effectively adjusted by controlling the cross-connecting gap Ga, so that the safety of the cantilever at the overhanging end of the half lacing wire is ensured.
Furthermore, the end part of the half lacing wire is provided with a limiting part which can be limited in the lacing wire hole.
By adopting the technical scheme, the end parts of the half lacing wires are locally positioned to prevent the half lacing wires from greatly moving in the circumferential direction, so that the whole circle of blade bodies are connected to achieve the effect of loop-forming damping connection.
The blade root is an inclined three-tooth longitudinal tree-shaped blade root; the axial width Bg of the blade root satisfies the relation: bg is more than or equal to 75mm and less than or equal to 100mm.
Further, the horizontal included angle between the blade root center line and the rotor central axis U shaft is D1, and the included angle D1 satisfies the relation: d1 is more than or equal to 0 degree and less than or equal to 35 degrees.
To sum up, owing to adopted above-mentioned technical scheme, the beneficial effects of the utility model are that:
1. the utility model is suitable for an industrial steam turbine with backpressure of 5-30 KPa, speed regulation range of 6000 rpm-9000 rpm and exhaust steam flow within 55 t/h; under medium temperature middling pressure, high temperature high pressure and high temperature superhigh pressure steam environment, the pure power of condensing of unit has covered 4MW ~ 15MW, can satisfy the chemical industry field to near 10MW grade steam turbine model's demand well, has satisfied the demand of domestic market to the high-power industrial steam turbine of high rotational speed, has promoted the competitiveness in international market, has wide market perspective.
2. The utility model discloses a tree type blade root is indulged to formula tridentate to the slant and whole circle connection structure of tie bar is opened to half section, has good variable working condition aerodynamic performance, and intensity is high, damping characteristic is good, and the blade combines firmly, stably with the rotor, can satisfy the security requirement of blade.
3. The utility model discloses higher economic nature and reliability have.
4. The utility model discloses can effectively compensate weakening condition, reduction lacing wire hole and the regional stress concentration of blade profile handing-over of lacing wire hole place cross-section.
5. The utility model discloses can prevent that half lacing wire from drunkenness by a wide margin at the circumferencial direction to couple together the blade body of whole circle, reach the effect that the lopping damping is connected.
Drawings
FIG. 1 is a schematic view of a single blade;
FIG. 2 is a schematic cross-sectional view of a blade body;
FIG. 3 is a schematic view of a blade root configuration;
FIG. 4 is a front view of the loose tie assembly;
FIG. 5 is a schematic view of a loose tie assembly;
fig. 6 is a schematic view of the loose lacing wire assembled along the leaf height.
The mark in the figure is: 1-blade root, 2-blade body, 3-thickness strengthening area, 4-lacing hole, 5-half lacing, 6-blade grid channel and 7-limiting part.
Detailed Description
The present invention will be described in detail with reference to the accompanying drawings.
In order to make the objects, technical solutions and advantages of the present invention more clearly understood, the present invention will be further described in detail with reference to the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are merely illustrative of the invention and are not intended to limit the invention.
Example 1
A low-pressure final-stage moving blade of a steam turbine, as shown in FIGS. 1 to 6, comprises a single blade, which comprises a blade root 1 and a blade body 2; the blade root 1 is positioned at the root of the blade body 2, the blade root 1 and the blade body 2 are of an integral structure, and the blade body 2 is a special-shaped body formed by superposing a plurality of characteristic sections according to a specific rule; the profile line of the characteristic section is a closed curve formed by an inner arc curve and a back arc curve, and has characteristic parameters: the blade profile mounting angle C, the blade body section chord length B, the maximum blade body section thickness W, the axial width Xa of the blade body section and the blade body section area A; the superposition rule of characteristic sections is that each section is in continuous smooth transition from the root end of the blade body 2 to the top end of the blade body 2 along the blade height direction, the root part of the blade body 2 is in a subsonic blade profile, the middle part of the blade body is in a transonic blade profile, the top part of the blade body is in a supersonic blade profile, the blade height Ld of the blade body 2 is 180mm, and the root diameter Dr is 500mm; the relative value of the leaf height Ld monotonically increases from 0.0 to 1.0; correspondingly, the blade profile installation angle C is monotonically reduced from 72.21 degrees to 35.61 degrees; the relative change rule of the blade body section area A from the root section to the top section is monotonically reduced from 2.61 to 1.0; the relative change rule of the axial width Xa of the blade body section from the root section to the top section is monotonically reduced from 2.12 to 1.0; the relative change rule of the chord length B of the blade body section from the root section to the top section is monotonically reduced from 1.30 to 1.0; the relative change rule of the maximum thickness W of the blade body section from the root section to the top section is monotonically reduced to 1.0 from 1.62, the blade profile of the single blade is monotonically twisted and formed along the height, the relative value of the outlet geometric angle alpha 1 is monotonically reduced to 1.0 from 1.795 from the root to the blade top along the height direction, and the calculation process of the outlet geometric angle alpha 1 is shown in the following formula (1):
α1＝sin -1 (O/T) (1)
in formula 1, O is the width of the throat of the cross section outlet of the blade body 2, i.e., the minimum distance between the steam outlet edge F of the blade profile and the back arc D of the cross section of the adjacent blade body 2, and T is the installation distance of the profile cross section of the same height of the two adjacent single blades in the circumferential direction.
The blade body 2 is provided with a lacing wire hole 4, and the height Lj of the center of the lacing wire hole 4 satisfies the relation that Lj/Ld is more than or equal to 0.68 and less than or equal to 0.825; the diameter phi of the lacing hole 4 satisfies the relational expression of 6.5 mm-phi less than or equal to 10mm.
And the inner arc E and the back arc D of the blade body 2 are provided with a smooth thickness strengthening area 3 in the area matched with the lacing hole 4 along the axial direction and the blade height direction of the lacing hole 4. Particularly, the weakening condition of the cross section where the lacing hole 4 is located can be effectively compensated, and the stress concentration of the connecting area of the lacing hole 4 and the profile of the blade body 2 is reduced.
The pull rod also comprises a loose pull rod, the loose pull rod can penetrate through the pull rod hole 4 and is matched with the pull rod hole 4, and the diameter of the loose pull rod
Satisfy the relation:
the length L satisfies the relation that L is more than or equal to 6.7. T1 and less than or equal to 6.95. T1; the loose lacing wire forms an arc-shaped structure along the length L direction according to the radius R, and the calculation process of the radius R is shown as the following formula (2):
R＝(Dr/2+Lj) (2)
in formula 2, dr is the root diameter of the blade, i.e., the diameter of a circle where the root section of the blade body 2 is located after the single blade is mounted on the rotor, and Lj is the height position of the lacing hole 4 on the blade body 2.
As shown in fig. 4-6, the loose lacing wire is divided into equal half lacing wires 5 along the radial direction, and the two half lacing wires 5 can be mutually folded and pass through the lacing wire holes 4.
It is a plurality of the monomer blade encircles rotor round and equipartition in the rotor excircle, blade root 1 limits in the impeller groove on the rotor excircle, the pine lacing wire passes lacing wire hole 4 and connects a plurality of blade bodies 2, the pine lacing wire encircles the rotor round and forms circular ring shaped structure.
A blade grid channel 6 is formed between two adjacent single blades, the half lacing wires 5 on the same side are matched with each other to form a half lacing wire ring, and the two half lacing wire rings on the opposite side are combined to form a loose lacing wire ring; in the same half lacing wire ring, the end surfaces of the adjacent half lacing wires 5 are matched with each other in the middle of the blade cascade channel 6 to form a cross-over area, a cross-over gap Ga is arranged at the cross-over area, and the cross-over areas in the two half lacing wire rings on the opposite side are arranged in different blade cascade channels 6.
Specifically, by controlling the handover gap Ga, the length of the cantilever at the overhanging end formed by the end of the half lacing wire 5 extending out of the lacing wire hole 4 can be effectively adjusted, thereby ensuring the safety of the cantilever at the overhanging end of the half lacing wire 5.
The end part of the half lacing wire 5 is provided with a limiting part 7 which can be limited in the lacing wire hole, preferably, the limiting part 7 is a bulge which is spot-welded on the end part of the half lacing wire 5.
Specifically, the end portions of the half-lacing wires 5 are locally positioned to prevent the half-lacing wires 5 from greatly shifting in the circumferential direction, so that the whole circle of the blade body 2 is connected, and the effect of the looped damping connection is achieved.
The blade root 1 is an inclined three-tooth longitudinal tree-shaped blade root; the axial width Bg of the blade root 1 satisfies the relation that Bg is more than or equal to 75mm and less than or equal to 100mm.
The horizontal included angle of the central line of the blade root 1 and the U shaft of the central axis of the rotor is D1, and the included angle D1 meets the relation: d1 is more than or equal to 0 degree and less than or equal to 35 degrees.
The stress distribution of the single blade and the wheel groove and the loose lacing wire matched with the single blade is uniform, no obvious stress singular area exists, the strength performance of the material is reasonably utilized, and the requirement of the running speed can be met by selecting the conventional movable blade material.
The single blade of the embodiment has uniform flow field distribution, can well adapt to the working condition change in a speed regulation range, and has excellent pneumatic performance.
The principles and embodiments of the present invention have been explained herein using specific examples, which are presented only to aid in understanding the methods and their core concepts. It should be noted that, for those skilled in the art, without departing from the principle of the present invention, the present invention can be further modified and modified, and such modifications and modifications also fall within the protection scope of the appended claims.
In the description of the present invention, it should be noted that the terms "center", "upper", "lower", "left", "right", "vertical", "horizontal", "inner", "outer", and the like indicate the position or positional relationship based on the position or positional relationship shown in the drawings, or the position or positional relationship which is usually placed when the product of the present invention is used, and are only for convenience of description and simplification of the description, but do not indicate or imply that the device or element referred to must have a specific position, be constructed and operated in a specific orientation, and thus, should not be construed as limiting the present invention.
In the description of the present invention, it should also be noted that, unless otherwise explicitly specified or limited, the terms "disposed," "mounted," "connected," and "connected" are to be construed broadly, e.g., as meaning either a fixed connection, a removable connection, or an integral connection; can be mechanically or electrically connected; they may be connected directly or indirectly through intervening media, or they may be interconnected between two elements. The specific meaning of the above terms in the present invention can be understood as a specific case by those skilled in the art.
Claims (10)
1. The low-pressure last-stage moving blade of the steam turbine comprises a single blade, wherein the single blade comprises a blade root and a blade body; the blade root is positioned at the root of the blade body, the blade root and the blade body are of an integral structure, and the blade body is a special-shaped body formed by superposing a plurality of characteristic sections according to a specific rule; the profile line of the characteristic section is a closed curve formed by an inner arc curve and a back arc curve, and has characteristic parameters: a blade profile mounting angle C, a blade body section chord length B, a blade body section maximum thickness W, a blade body section axial width Xa and a blade body section area A; the superposition law of characteristic sections is that each section is in continuous and smooth transition from the root end of the blade body to the top end of the blade body along the blade height direction, and is characterized in that the root of the blade body is in a subsonic blade profile, the middle of the blade body is in a transonic blade profile, the top of the blade body is in a supersonic blade profile, the blade height Ld of the blade body is 180mm, and the root diameter Dr is 500mm; the relative value of the leaf height Ld is monotonically increased from 0.0 to 1.0; correspondingly, the blade profile installation angle C is monotonically reduced to 35.61 degrees from 72.21 degrees; the relative change rule of the blade body section area A from the root section to the top section is monotonically reduced from 2.61 to 1.0; the relative change rule of the axial width Xa of the blade body section from the root section to the top section is monotonically reduced from 2.12 to 1.0; the relative change rule of the chord length B of the blade body section from the root section to the top section is monotonically reduced from 1.30 to 1.0; the relative change rule of the maximum thickness W of the blade body section from the root section to the top section is monotonically reduced from 1.62 to 1.0, the blade profile of the single blade is monotonically twisted and formed along the height, the relative value of the outlet geometric angle alpha 1 is monotonically reduced from 1.795 to 1.0 along the height direction from the blade root to the blade top, and the calculation process of the outlet geometric angle alpha 1 is shown in the following formula (1):
α1＝sin -1 (O/T) (1)
in formula 1, O is the width of the throat of the blade body section outlet, i.e., the minimum distance between the blade profile steam outlet edge F and the back arc D of the adjacent blade body section, and T is the circumferential installation distance of the profile section of the same height of the two adjacent single blades.
2. The steam turbine low pressure last stage moving blade according to claim 1, wherein said blade body has a tiepiece hole, and a height Lj of a center of said tiepiece hole satisfies a relation of 0.68 ≦ Lj/Ld ≦ 0.825; the diameter phi of the lacing hole satisfies the relational expression that phi is more than or equal to 6.5mm and less than or equal to 10mm.
3. The steam turbine low pressure last stage moving blade of claim 2, wherein said inner arc E and said back arc D of said blade body have a thickness reinforcement area which tends to be smooth in the axial direction of said lacing hole and in the blade height direction in the area where said blade body is fitted with said lacing hole.
4. The steam turbine low pressure last stage moving blade of claim 2, further comprising a loose tie bar, the loose tie bar being capable of passing through and mating with a tie bar hole, the loose tie bar having a diameter
Satisfies the relation:
the length L satisfies the relation that L is more than or equal to 6.7. T1 and less than or equal to 6.95. T1; the loose lacing wire forms an arc-shaped structure along the length L direction according to the radius R, and the calculation process of the radius R is shown as the following formula (2):
R＝(Dr/2+Lj) (2)
in formula 2, dr is the blade root diameter, i.e., the diameter of a circle where the root section of the blade body of the single blade is located after the single blade is mounted on the rotor, and Lj is the height position of the lacing hole on the blade body.
5. The steam turbine low pressure last stage moving blade of claim 4, wherein said loose lacing wire is divided into equal half lacing wires along a radial direction, and two of said half lacing wires are mutually folded to pass through the lacing wire holes.
6. The low pressure last stage moving blade of steam turbine as claimed in claim 5, wherein a plurality of said single blades are uniformly distributed around the outer circumference of the rotor, said blade roots are confined in the grooves of the impeller on the outer circumference of the rotor, said loose tie bar passes through the tie bar hole to connect a plurality of blade bodies, said loose tie bar forms a circular ring structure around the circumference of the rotor.
7. The steam turbine low pressure last stage moving blade of claim 6, wherein a cascade channel is formed between two adjacent single blades, the half lacing wires on the same side are matched with each other to form a half lacing wire ring, and the two half lacing wire rings on the opposite side are matched to form a loose lacing wire ring; in same half lacing wire ring, adjacent half lacing wire terminal surface cooperatees in cascade passageway middle part and forms the handing-over region, handing-over region department is provided with handing-over clearance Ga, and the handing-over region in the two halves lacing wire ring of offside sets up in the cascade passageway of difference.
8. The steam turbine low pressure last stage moving blade of claim 7, wherein the end of said half lacing wire is provided with a stopper portion which is restricted to the lacing wire hole.
9. The steam turbine low pressure last stage moving blade according to any one of claims 6 to 8, further comprising a rotor, wherein said blade root is an inclined three-tooth longitudinal tree blade root; the axial width Bg of the blade root satisfies the relation: bg is more than or equal to 75mm and less than or equal to 100mm.
10. The steam turbine low pressure last stage moving blade of claim 9, wherein the horizontal included angle between the blade root center line and the rotor central axis U-axis is D1, and the included angle D1 satisfies the relation: d1 is more than or equal to 0 degree and less than or equal to 35 degrees.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202222875904.1U CN218581665U (en) | 2022-10-31 | 2022-10-31 | Low-pressure last-stage moving blade of steam turbine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202222875904.1U CN218581665U (en) | 2022-10-31 | 2022-10-31 | Low-pressure last-stage moving blade of steam turbine |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN218581665U true CN218581665U (en) | 2023-03-07 |
Family
ID=85377730
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202222875904.1U Active CN218581665U (en) | 2022-10-31 | 2022-10-31 | Low-pressure last-stage moving blade of steam turbine |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN218581665U (en) |
-
2022
- 2022-10-31 CN CN202222875904.1U patent/CN218581665U/en active Active
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN201581936U (en) | Special last-stage vane for large-scale 60Hz turbine | |
| CN108119187B (en) | Low-pressure-stage moving blade of industrial steam turbine with variable rotation speed and large flow | |
| CN113236607B (en) | Design method of large-scale engineering pump volute and volute thereof | |
| CN109026186B (en) | Multi-element coupling passive control technology for inhibiting clearance flow loss of top of radial turbine blade | |
| CN114483204B (en) | Stationary blade suitable for radial-axial vertical non-vertical air inlet | |
| CN109707462B (en) | 1450mm titanium alloy final-stage blade of full-speed steam turbine | |
| CN102434223A (en) | Low-pressure stage final blade of large-flow air-cooled steam turbine | |
| CN218581665U (en) | Low-pressure last-stage moving blade of steam turbine | |
| CN101749052B (en) | Last-stage moving blade of air-cooling feed pump turbine | |
| CN115653693A (en) | Last-stage moving blade | |
| CN108590775B (en) | Industrial steam turbine high-load efficient regulation stage moving blade | |
| CN110242355B (en) | 645mm last-stage moving blade for industrial steam turbine | |
| CN108194150B (en) | Large-load efficient regulating-stage stationary blade of industrial steam turbine | |
| CN212716770U (en) | 450mm final-stage moving blade for 50MW full-speed air-cooled steam turbine | |
| CN212054821U (en) | Last-stage moving blade structure and blade group suitable for high-power air turbine | |
| CN210714784U (en) | Energy-saving tail gas turbine | |
| CN109117552B (en) | Turbine blade variable load flow pattern design method | |
| CN108266234B (en) | Efficient rotary drum-level stator blade of industrial steam turbine | |
| CN109101722B (en) | Composite forming design method for turbine blade | |
| CN111852576B (en) | Last-stage moving blade for water supply pump steam turbine | |
| CN213039329U (en) | Last-stage moving blade for water supply pump steam turbine | |
| CN108194149B (en) | High-efficient rotary drum level moving blade of industrial steam turbine | |
| CN118148714A (en) | Low-pressure final stage moving blade of ultrahigh-speed variable-speed industrial steam turbine | |
| CN216691182U (en) | 2.5m2Air cooling final-stage movable vane for grade industrial steam turbine | |
| CN111963252A (en) | Secondary and final moving blade and blade assembly of variable-rotating-speed large-flow industrial steam turbine |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| GR01 | Patent grant | ||
| GR01 | Patent grant |