CN215890101U - Penult-stage moving blade, moving blade group and steam turbine - Google Patents

Abstract

The embodiment of the application relates to the technical field of machinery, in particular to a penult-stage moving blade, a moving blade group and a steam turbine; the penultimate moving blade comprises a blade body, a blade root and a shroud, wherein the blade root is connected to the root of the blade body, and the shroud is connected to the top of the blade body; for example, when a super (sub) critical 300MW grade wet cooling unit operates at low-pressure through-flow zero flow, the original final-stage moving blade has poor adaptability and anti-flutter performance, and the operation safety of the unit at zero flow is influenced. According to the embodiment of the application, a new penultimate moving blade is designed, under the working rotating speed, the shroud bands of adjacent blades are attached to each other, positive pressure and friction force are generated, and the damping of a system is increased; meanwhile, the whole circle of the blades is grouped, the vibration performance of the blades is improved, and the dynamic stress borne by the blades is reduced.

Description

Penult-stage moving blade, moving blade group and steam turbine

Technical Field

The embodiment of the application relates to the technical field of machinery, in particular to a penult-stage moving blade, a moving blade group and a steam turbine.

Background

The steam turbine is also called as a steam turbine engine, and is a rotary steam power device.A high-temperature high-pressure steam passes through a fixed nozzle to become an accelerated steam flow and then is sprayed onto blades, so that a rotor provided with blade rows rotates, and simultaneously, the rotor does work outwards.

In general, blades of a steam turbine mounted on a wheel are called as rotor blades, and the rotor blades mainly function to convert kinetic energy of steam into mechanical energy of a rotor. In order to meet the new requirements of flexible operation of a power plant on low-pressure long blades, various penultimate moving blades need to be continuously developed so as to meet the increasing requirements on intensity vibration, safety performance, pneumatic efficiency and the like of the penultimate moving blades.

In the low-pressure through-flow zero-flow operation process, the secondary-final movable blade can be at extremely low flow, that is, along with the reduction of the load factor of the unit, the steam inlet parameter of the low-pressure cylinder of the steam turbine is reduced, the volume flow is greatly reduced, so that the unit operates under the condition of small volume flow, as the original pneumatic design flow field is damaged, the thermodynamic parameters of the final movable and stationary blades along the blade height are redistributed, and a large-scale backflow vortex is formed in a through-flow area. Meanwhile, when the steam flows through the last-stage and last-stage long blade areas, the blades are not pushed to do work any more, but mechanical work is consumed, the steam flows are pressed out of the movable blade flow passages, and the blowing phenomenon occurs. When the air blowing state is entered, since the existing penultimate moving blade is a free blade and is very sensitive to frequency change, when the temperature of the air blowing is increased, the frequency of the penultimate moving blade may fall into a resonance region, and thus a large potential safety hazard exists.

Disclosure of Invention

The embodiment of the application provides a penultimate moving blade, a moving blade group and a steam turbine, and aims to at least solve the problem that the safety of the penultimate moving blade is endangered due to overlarge dynamic stress generated by sudden irregular excitation under the working condition of small volume flow operation of the penultimate moving blade in the prior art.

In a first aspect, an embodiment of the present application provides a penultimate moving blade, including:

a blade root;

the blade root is arranged at the root of the blade body;

the shroud ring is arranged at the top of the blade body and is provided with a contact part and a spacing part, and the contact part is connected with the spacing part;

when the surrounding belt is in a static state, the contact part and the spacing part are spaced from the adjacent surrounding belt;

when the shroud is in an operating state, the contact surfaces of the contact portions are abutted.

In one implementation, the height of the blade body is 520mm to 550mm, the root diameter of the blade body is 1650mm to 1670mm, the axial width of the root of the blade body is 170.05mm, and the axial width of the top of the blade body is 35.71mm to 40.57 mm;

the height of the shroud ring is 7.1mm, the inclination angle of a shroud ring steam passage is 20 degrees, and the axial width of the shroud ring is 44 mm.

In one implementation, the transverse cross-section of the blade body is twisted unidirectionally from the root to the tip of the blade body and decreases monotonically in area;

from the root part to the top part of the blade body, the axial width of the transverse section is monotonically reduced from 170.05mm to 35.71 mm-40.57 mm, the chord length of the transverse section is monotonically reduced from 171.33mm to 123.23 mm-125.67 mm, the installation angle of the transverse section is monotonically reduced from 80.43 degrees to 16.57-18.58 degrees, and the inlet angle of the transverse section is monotonically increased from 41.81 degrees to 149.55-154.98 degrees.

In one implementation, the main blade body includes, but is not limited to, a profile made up of the following sections:

the blade comprises a first transverse section, a second transverse section and a third transverse section, wherein the first transverse section is formed at the position of the blade body with the height of 0, and the axial width, the chord length, the installation angle and the inlet angle of the first transverse section are 170.05 degrees, 171.33 degrees, 80.43 degrees and 41.81 degrees respectively;

the second transverse section is formed at the position where the height of the blade body is 49mm, and the axial width, the chord length, the installation angle and the inlet angle of the second transverse section are 157.19 degrees, 162.78 degrees, 74.98 degrees and 38.46 degrees respectively;

the third transverse section is formed at the position where the height of the blade body is 91mm, and the axial width, the chord length, the installation angle and the inlet angle of the third transverse section are respectively 150.88 degrees, 160.60 degrees, 70.04 degrees and 41.67 degrees;

the fourth transverse section is formed at the position where the height of the blade body is 133mm, and the axial width, the chord length, the installation angle and the inlet angle of the fourth transverse section are 143.17 degrees, 158.22 degrees, 64.90 degrees and 47.30 degrees respectively;

a fifth transverse cross section formed at a blade body height of 175mm, the fifth transverse cross section having an axial width, a chord length, a setting angle, and an inlet angle of 134.10, 155.66, 59.58, and 55.29 degrees, respectively;

the sixth transverse section is formed at the position where the height of the blade body is 217mm, and the axial width, the chord length, the installation angle and the inlet angle of the sixth transverse section are 123.79 degrees, 152.95 degrees, 54.12 degrees and 65.34 degrees respectively;

a seventh transverse section formed at a blade body height of 259mm, the axial width, chord length, stagger angle, and inlet angle of the seventh transverse section being 112.45 °, 150.14, 48.57 °, 76.93 °, respectively;

the eighth transverse section is formed at the position where the height of the blade body is 301mm, and the axial width, the chord length, the installation angle and the inlet angle of the eighth transverse section are 100.30 degrees, 147.16 degrees, 43.02 degrees and 88.50 degrees respectively;

a ninth transverse section formed at a blade height of 343mm, the axial width, chord length, setting angle, inlet angle of the ninth transverse section being 87.52 °, 143.43 °, 37.62 °, 100.60 ° respectively;

a tenth transverse section formed at a blade height of 385mm, the tenth transverse section having an axial width, a chord length, a mounting angle, and an inlet angle of 74.74 °, 139.18 °, 32.45 °, 113.86 °, respectively;

the eleventh transverse section is formed at the position where the height of the blade body is 427mm, and the axial width, the chord length, the installation angle and the inlet angle of the eleventh transverse section are respectively 62.55 degrees, 134.68 degrees, 27.56 degrees and 126.22 degrees;

a twelfth transverse section which is formed at the position where the height of the blade body is 469mm, and the axial width, the chord length, the installation angle and the inlet angle of the twelfth transverse section are 51.53 degrees, 130.44 degrees, 23.10 degrees and 137.24 degrees respectively;

a thirteenth transverse section, formed at the position where the height of the blade body is 511mm, and the axial width, the chord length, the installation angle and the inlet angle of the thirteenth transverse section are 42.30 degrees, 126.47 degrees, 19.29 degrees and 147.61 degrees respectively;

the fourteenth transverse section is formed at the position of the blade body with the height of 520 mm-550 mm, and the axial width, the chord length, the installation angle and the inlet angle of the fourteenth transverse section are respectively 35.71 mm-40.57 mm, 123.23 mm-125.67 mm, 16.57-18.58 degrees and 149.55-154.98 degrees.

In one implementation, the blade root is a circular arc fir tree blade root; the axial width of the blade root is 180mm and the total height of the blade root is 72.35 mm.

In one implementation mode, a water erosion preventing part is arranged at the top back arc of the blade body; the water erosion preventing portion is formed by intermediate frequency quenching, or the water erosion preventing portion is formed by laser hardening (laser quenching).

In a second aspect, embodiments of the present application provide a rotor blade row including the penultimate rotor blade described above.

In one implementation, the number of penultimate moving blades is plural.

In one implementation, the number of penultimate moving blades is 68.

In a third aspect, embodiments of the present application provide a steam turbine, including the above-mentioned moving blade group.

Advantageous effects

The embodiment of the application sets up contact site and interval portion on the shroud, through setting up the contact site of laminating mutually with adjacent shroud, be in quiescent condition at the shroud, contact site and interval portion all have the interval with adjacent shroud, through setting up the interval, thereby the torsion amplitude that takes place for the blade body provides enough space, so that be in the operation in-process when the shroud, that is to say, in steam turbine operation, through centrifugal force realize uniting between the adjacent penultimate stage moving blade, specifically speaking, be in the operation in-process at the shroud, adjacent shroud offsets, thereby produce pressure (like positive pressure) and frictional force, the damping of system has been increased, realize that the blade is whole circle is uniting simultaneously, improve the vibration performance of blade, in order to reduce the dynamic stress that the blade received, and then solve the penultimate stage moving blade among the prior art under little volume flow operation condition, receive the dynamic stress that unexpected irregular excitation produced too big and endanger the problem of the safety of penultimate stage moving blade.

Drawings

In order to more clearly illustrate the embodiments of the present application or the technical solutions in the prior art, the drawings needed to be used in the embodiments or the prior art descriptions will be briefly described below, and it is obvious that the drawings in the following description are some embodiments of the present application, and other drawings can be obtained by those skilled in the art without creative efforts.

FIG. 1 is a schematic view of a penultimate rotor blade at an angle according to an embodiment of the present application;

FIG. 2 is a schematic view of a penultimate rotor blade at another angle according to an embodiment of the present application;

FIG. 3 is a schematic view of a penultimate rotor blade at yet another angle according to an embodiment of the present application;

FIG. 4 is a stacked schematic view of the transverse cross-sections of FIG. 1 at fourteen different heights of the blade body of the penultimate moving blade;

FIG. 5 is a schematic diagram of the structure of the transverse cross section of FIG. 2;

FIG. 6 is a partial schematic view of FIG. 3;

FIG. 7 is a schematic structural diagram of a shroud of a penultimate moving blade set in a static state according to an embodiment of the present disclosure;

fig. 8 is a schematic structural diagram of a penultimate moving blade group according to an embodiment of the present application.

Description of reference numerals:

1. a blade root; 11. a tooth-shaped portion;

2. a leaf body;

3. a shroud ring; 31. a contact portion; 32. a spacer section.

Detailed Description

The technical solutions of the embodiments of the present application will be described clearly and completely with reference to the following embodiments, and it should be understood that the described embodiments are a part of the embodiments of the present application, and not all of the embodiments. All other embodiments obtained by a person of ordinary skill in the art based on the embodiments in the present application without any creative effort belong to the protection scope of the embodiments in the present application.

In the description of the embodiments of the present application, it is to be understood that the terms "center", "longitudinal", "lateral", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "clockwise", "counterclockwise", and the like, indicate orientations and positional relationships based on the orientations and positional relationships shown in the drawings, and are only used for convenience in describing the embodiments of the present application and for simplification of description, but do not indicate or imply that the devices or elements referred to must have a specific orientation, be configured and operated in a specific orientation, and thus, should not be construed as limiting the embodiments of the present application.

Furthermore, the terms "first", "second" and "first" are used for descriptive purposes only and are not to be construed as indicating or implying relative importance or implicitly indicating the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include one or more features. In the description of the embodiments of the present application, "a plurality" means two or more unless specifically defined otherwise. Furthermore, the terms "mounted," "connected," and "connected" are to be construed broadly and may, for example, be fixedly connected, detachably connected, or integrally connected; can be mechanically or electrically connected; they may be connected directly or indirectly through intervening media, or they may be interconnected between two elements. Specific meanings of the above terms in the embodiments of the present application can be understood in specific cases by those of ordinary skill in the art.

Steam turbines are the main equipment of modern thermal power plants, and are also used in the metallurgical industry, chemical industry and ship power plants.

The steam turbine is also called as a steam turbine engine, and is a rotary steam power device.A high-temperature high-pressure steam passes through a fixed nozzle to become an accelerated steam flow and then is sprayed onto blades, so that a rotor provided with blade rows rotates, and simultaneously, the rotor does work outwards.

In general, blades mounted on a turbine wheel are called rotor blades, and the rotor blades mainly function to convert kinetic energy of steam into mechanical energy of a rotor. In order to meet the new requirements of flexible operation of a power plant on low-pressure long blades, various penultimate moving blades need to be continuously developed so as to meet the increasing requirements on intensity vibration, safety performance, pneumatic efficiency and the like of the penultimate moving blades.

In the low-pressure through-flow zero-flow operation process, the secondary-final movable blade can be at extremely low flow, that is, along with the reduction of the load factor of the unit, the steam inlet parameter of the low-pressure cylinder of the steam turbine is reduced, the volume flow is greatly reduced, so that the unit operates under the condition of small volume flow, as the original pneumatic design flow field is damaged, the thermodynamic parameters of the final movable and stationary blades along the blade height are redistributed, and a large-scale backflow vortex is formed in a through-flow area. Meanwhile, when the steam flows through the last-stage and last-stage long blade areas, the blades are not pushed to do work any more, but mechanical work is consumed, the steam flows are pressed out of the movable blade flow passages, and the blowing phenomenon occurs. When the air blowing state is entered, since the existing penultimate moving blade is a free blade and is very sensitive to frequency change, when the temperature of the air blowing is increased, the frequency of the penultimate moving blade may fall into a resonance region, and thus a large potential safety hazard exists.

In order to solve the above problems, embodiments of the present application provide a penultimate moving blade, a moving blade group, and a steam turbine, in which a contact portion that is attached to an adjacent shroud is provided, when the shroud ring is in a static state, the contact part and the spacing part are spaced from the adjacent shroud ring, and by arranging the spacing, thereby providing sufficient space for the torsional amplitudes of the blade body to occur to facilitate grouping of adjacent penultimate moving blades by centrifugal force while the shroud is in operation, and, in particular, when the shroud is in operation, the adjacent shrouds are abutted, thereby generating pressure (such as positive pressure) and friction force, increasing the damping of the system, meanwhile, the complete circle grouping of the blades is realized, the vibration performance of the blades is improved, the dynamic stress borne by the blades is reduced, and then solve the problem that the secondary final stage moving blade in the prior art is endangered by overlarge dynamic stress generated by sudden irregular excitation under the working condition of small volume flow operation.

The penultimate rotor blade according to the embodiments of the present application will be described in detail below with reference to the accompanying drawings.

FIG. 1 is a schematic view of a penultimate rotor blade at an angle according to an embodiment of the present application;

FIG. 2 is a schematic view of a penultimate rotor blade at another angle according to an embodiment of the present application; FIG. 3 is a schematic view of a penultimate rotor blade at yet another angle according to an embodiment of the present application; FIG. 4 is a stacked schematic view of the transverse cross-sections of FIG. 1 at fourteen different heights of the blade body of the penultimate moving blade;

FIG. 5 is a schematic diagram of the structure of the transverse cross section of FIG. 2; FIG. 6 is a partial schematic view of FIG. 3; FIG. 7 is a schematic structural diagram of a shroud of a penultimate moving blade set in a static state according to an embodiment of the present disclosure; fig. 8 is a schematic structural diagram of a penultimate moving blade group according to an embodiment of the present application. Referring to fig. 1 and 8 in combination, an embodiment of the present application provides a penultimate moving blade, which includes a blade root 1, a blade body 2 and a shroud 3, wherein the blade root 1 is arranged at the root of the blade body 2; the shroud 3 is arranged on the top of the blade body 2, the shroud 3 is provided with a contact portion 31 and a spacing portion 32, and the contact portion 31 is connected with the spacing portion 32.

When the shroud ring 3 is in a static state, the contact portion 31 and the spacing portion 32 are spaced from the adjacent shroud ring 3;

as can be seen in particular in fig. 7, in the operating state of the shroud 3, the contact surfaces of the contact portions 31 abut, that is to say the AB surfaces of the contact portions 31 abut.

Continuing to refer to fig. 7, for example, the contact portion 31 may be a protruding structure, such as a protrusion, and the cross section of the protrusion may be substantially triangular, but the cross section of the contact portion 31 may also be other suitable shapes, such as a quadrilateral, a pentagon, etc., or a shape with arc sides, and is not limited in particular.

In a specific application, the blade root 1, the blade body 2 and the shroud 3 may be provided as a single body, i.e. as a single body, and when the shroud 3 is in a static state, the contact portion 31 and the spacing portion 32 are spaced from the adjacent shroud 3, and the spacing provides sufficient space for the amplitude of the torsion of the blade body 2.

When the shroud ring 3 is in a running state, AB surfaces of the contact parts 31 are abutted to realize grouping between adjacent penultimate moving blades, specifically, when the shroud ring 3 is in a running state, AB surfaces of the contact parts 31 are abutted to generate pressure (such as positive pressure) and friction force, thereby increasing the damping of a system, realizing grouping of the whole circle of the blades simultaneously, improving the vibration performance of the blades to reduce the dynamic stress borne by the blades, and further solving the problem that the safety of the penultimate moving blades is endangered due to overlarge dynamic stress generated by sudden irregular excitation under the working condition of small volume flow running of the penultimate moving blades in the prior art.

Referring to fig. 1 to 3, embodiments of the present application provide a penultimate rotor blade in which a transverse cross-section of a blade body 2 may be twisted in one direction from a root to a tip of the blade body 2 and monotonically decreases in area.

For example, from the root to the tip of the blade body 2, the axial width V1 of the transverse cross section monotonically decreases from 170.05mm to 35.71mm to 40.57mm, the chord length b of the transverse cross section monotonically decreases from 171.33mm to 123.23mm to 125.67mm, the installation angle α 2 of the transverse cross section monotonically decreases from 80.43 ° to 16.57 ° to 18.58 °, and the inlet angle α 1 of the transverse cross section monotonically increases from 41.81 ° to 149.55 ° to 154.98 °.

This application embodiment is through the root with blade 2 to the top one-way torsion and the area monotonous reduction of transverse section from blade 2 to make blade 2 along the torsion and the area change law of transverse section of direction of height, when guaranteeing that blade 2 is reasonable along each heating power parameter distribution law of self direction of height, compromise the quiet intensity requirement of blade, and then make the blade have better aerodynamic performance, with the little volume flow operating mode of better adaptation.

Referring to fig. 4, the main blade body 2 (including but not limited to a profile consisting of a first transverse section through a fourteenth transverse section), for example, may be included.

Hereinafter, the axial width, chord length, inlet angle, and mounting angle of each transverse section (e.g., the first transverse section) may be referred to by the corresponding reference numerals V1, b, α 1, α 2, respectively.

A first transverse section formed at a position where the height of the blade body 2 is 0, and the axial width, chord length, mounting angle and inlet angle of the first transverse section are 170.05mm, 171.33mm, 80.43 degrees and 41.81 degrees respectively;

a second transverse cross section formed at a position of the blade body 2 where the height is 49mm, and the axial width, chord length, mounting angle and inlet angle of the second transverse cross section are 157.19mm, 162.78mm, 74.98 degrees and 38.46 degrees respectively;

a third transverse section, which is formed at the position where the height of the blade body 2 is 91mm, and the axial width, the chord length, the installation angle and the inlet angle of the third transverse section are respectively 150.88mm, 160.60mm, 70.04 degrees and 41.67 degrees;

a fourth transverse section, which is formed at the position where the height of the blade body 2 is 133mm, and the axial width, the chord length, the installation angle and the inlet angle of the fourth transverse section are 143.17mm, 158.22mm, 64.90 degrees and 47.30 degrees respectively;

a fifth transverse cross-section formed at a height of 175mm of the blade body 2, the fifth transverse cross-section having an axial width, a chord length, a setting angle, and an inlet angle of 134.10mm, 155.66mm, 59.58 °, and 55.29 °, respectively;

a sixth transverse section formed at the position where the height of the blade body 2 is 217mm, and the axial width, chord length, mounting angle and inlet angle of the sixth transverse section are 123.79mm, 152.95mm, 54.12 degrees and 65.34 degrees respectively;

a seventh transverse section formed at a height of 259mm of the blade body 2, the seventh transverse section having an axial width, a chord length, a setting angle, and an inlet angle of 112.45mm, 150.14mm, 48.57 °, and 76.93 °, respectively;

an eighth transverse section formed at a position where the height of the blade body 2 is 301mm, and the axial width, chord length, mounting angle and inlet angle of the eighth transverse section are 100.30mm, 147.16mm, 43.02 degrees and 88.50 degrees respectively;

a ninth transverse section formed at a position where the height of the blade body 2 is 343mm, and the axial width, chord length, mounting angle, and inlet angle of the ninth transverse section are 87.52mm, 143.43mm, 37.62 °, 100.60 °, respectively;

a tenth transverse section formed at a height of 385mm of the blade body 2, and having an axial width, a chord length, a mounting angle, and an inlet angle of 74.74mm, 139.18mm, 32.45 °, and 113.86 °, respectively;

an eleventh transverse section formed at a height of 427mm of the blade body 2, the eleventh transverse section having an axial width, a chord length, a setting angle, and an entrance angle of 62.55mm, 134.68mm, 27.56 °, 126.22 °;

a twelfth transverse section, formed at 469mm of the height of the blade body 2, the axial width, chord length, mounting angle and inlet angle of the twelfth transverse section being 51.53mm, 130.44mm, 23.10 ° and 137.24 ° respectively;

a thirteenth transverse section formed at the position of 511mm in height of the blade body 2, the thirteenth transverse section having an axial width, a chord length, a setting angle, and an inlet angle of 42.30mm, 126.47mm, 19.29 °, 147.61 °, respectively;

a fourteenth transverse section formed at the position of the blade body 2 with the height of 520 mm-550 mm, and the axial width, chord length, installation angle and inlet angle of the fourteenth transverse section are respectively 35.71 mm-40.57 mm, 123.23 mm-125.67 mm, 16.57-18.58 degrees and 149.55-154.98 degrees.

With continued reference to fig. 8, the blade root 1 may be a circular arc fir tree type (see detail bottom position in fig. 8) blade root 1; the axial width of the blade root 1 is 180mm and the total height L of the blade root 1 is 72.35 mm. For example, the blade root 1 may comprise a blade root 1 body and a plurality of teeth 11 connected to both sides of the blade root 1 body in the thickness direction, the thickness of the top of the blade root 1 body being greater than the thickness of the bottom of the blade root 1 body. Alternatively, the blade root 1 is a tridentate fir-tree blade root 1, i.e. the body of the blade root 1 may be connected with three teeth 11 on both sides in the thickness direction.

The blade root 1 is set to be the arc fir tree blade root 1, for example, the multi-tooth fir tree blade root 1, so that the rotor of the last-stage moving blade and the steam turbine is convenient and reliable to assemble, the bearing capacity is high, the stress concentration is low, the width of the root blade shape is reduced, the multi-tooth fir tree blade root can be widely applied to the steam turbine, such as a full-speed steam turbine, under the same operation condition, the longitudinal tree blade root 1 is compared with the fork blade root 1, the width of the root blade shape of the blade can be reduced by 20%, the friction loss of the wall surface of a root channel is reduced, certain adaptability is realized for the operation under small volume flow, on the premise of meeting the mechanical requirement, the cost is reduced as much as possible, and the multi-tooth fir tree blade root 1 is limited to be the three-tooth fir tree blade root 1.

In one implementation, a water erosion prevention part can be arranged at the top back arc of the blade body 2; the water erosion preventing portion is formed by intermediate frequency quenching, or the water erosion preventing portion is formed by laser hardening (laser quenching).

In specific application, the top back arc of the blade body 210 is the position with the largest water erosion risk, and the water erosion preventing part is arranged in a targeted manner, so that the cost is saved on the basis of effectively avoiding water erosion.

Referring to fig. 8, the embodiment of the present application further provides a moving blade group, and the number of the penultimate moving blades may be plural. Such as 68.

In the moving blade group according to the embodiment of the present application, by providing the penultimate moving blade described above, on the one hand, by providing the contact portion 31 that is in contact with the adjacent shroud 3, the contact portion 31 and the spacing portion 32 are spaced from the adjacent shroud 3 when the shroud 3 is in the stationary state, and by providing the spacing, a sufficient space is provided for the amount of twist of the blade body 2. When the shroud 3 is in the operation process, grouping between adjacent penultimate moving blades is realized through centrifugal force, specifically speaking, when the shroud 3 is in the operation state, AB surfaces of the contact parts 31 are abutted, so that pressure (such as positive pressure) and friction force are generated, the damping of the system is increased, meanwhile, grouping of the blades in a whole circle is realized, the vibration performance of the blades is improved, the dynamic stress borne by the blades is reduced, and the problem that the safety of the penultimate moving blades is endangered due to overlarge dynamic stress generated by sudden irregular excitation under the operation condition of small volume flow of the penultimate moving blades in the prior art is solved.

The embodiment of the application also provides a steam turbine, which comprises the movable blade group.

The steam turbine that this application embodiment provided includes can be one or two or more, through adopting foretell movable vane group, because of the stability of above-mentioned movable vane group is good, and can reduce the dynamic stress that the blade received, and then solve the next last movable blade among the prior art under little volume flow operating condition, receive the too big problem that endangers the safety of next last movable blade of dynamic stress that produces of sudden irregular excitation.

Finally, it should be noted that: the above embodiments are only used for illustrating the technical solutions of the embodiments of the present application, and are not limited thereto; although the embodiments of the present application have been described in detail with reference to the foregoing embodiments, those skilled in the art will understand that: the technical solutions described in the foregoing embodiments may still be modified, or some or all of the technical features may be equivalently replaced; and the modifications or the substitutions do not make the essence of the corresponding technical solutions depart from the scope of the technical solutions of the embodiments of the present application.

Claims (10)

1. A penultimate moving blade, comprising:

a blade root (1);

a blade body (2), the blade root (1) being arranged at the root of the blade body (2);

the shroud ring (3), the shroud ring (3) is arranged on the top of the blade body (2), the shroud ring (3) is provided with a contact part (31) and a spacing part (32), and the contact part (31) is connected with the spacing part (32);

when the shroud band (3) is in a static state, the contact part (31) and the spacing part (32) are spaced from the adjacent shroud band (3);

when the shroud band (3) is in an operating state, the contact surfaces of the contact portions (31) abut against each other.

2. The penultimate moving blade as claimed in claim 1,

the height of the blade body (2) is 520-550 mm, the root diameter of the blade body (2) is 1650-1670 mm, the axial width of the root of the blade body (2) is 170.05mm, and the axial width of the top of the blade body (2) is 35.71-40.57 mm;

the height of the shroud ring (3) is 7.1mm, the steam passage dip angle of the shroud ring (3) is 20 degrees, and the axial width of the shroud ring (3) is 44 mm.

3. The penultimate moving blade as claimed in claim 1,

the transverse section of the blade body (2) is twisted in a single direction from the root to the top of the blade body (2) and the area of the transverse section is monotonically reduced;

from the root to the top of the blade body (2), the axial width of the transverse cross section is monotonically reduced from 170.05mm to 35.71-40.57 mm, the chord length of the transverse cross section is monotonically reduced from 171.33mm to 123.23-125.67 mm, the installation angle of the transverse cross section is monotonically reduced from 80.43 degrees to 16.57-18.58 degrees, and the entrance angle of the transverse cross section is monotonically increased from 41.81 degrees to 149.55-154.98 degrees.

4. Penult rotor blade according to claim 1, characterized in that the blade body (2) comprises:

a first transverse cross-section formed at a height of 0 of the main blade body (2), the axial width, chord length, stagger angle, inlet angle of the first transverse cross-section being 170.05 °, 171.33 °, 80.43 °, 41.81 ° respectively;

a second transverse cross-section formed at a height of 49mm of the blade body (2), the axial width, chord length, stagger angle, inlet angle of the second transverse cross-section being 157.19 °, 162.78 °, 74.98 °, 38.46 °;

a third transverse cross-section formed at a height of 91mm of the blade body (2), the axial width, chord length, stagger angle, inlet angle of the third transverse cross-section being 150.88 °, 160.60 °, 70.04 °, 41.67 ° respectively;

a fourth transverse cross-section formed at a height of 133mm of the blade body (2), the axial width, chord length, stagger angle, inlet angle of the fourth transverse cross-section being 143.17 °, 158.22 °, 64.90 °, 47.30 ° respectively;

a fifth transverse cross-section formed at a height of 175mm of the blade body (2), the fifth transverse cross-section having an axial width, chord length, stagger angle, inlet angle of 134.10, 155.66, 59.58 °, 55.29 ° respectively;

a sixth transverse cross-section formed at the height of the blade body (2) of 217mm, the axial width, chord length, stagger angle, inlet angle of the sixth transverse cross-section being 123.79 °, 152.95 °, 54.12 °, 65.34 °, respectively;

a seventh transverse cross-section formed at a height of 259mm of the blade body (2), the axial width, chord length, stagger angle, inlet angle of the seventh transverse cross-section being 112.45 °, 150.14, 48.57 °, 76.93 ° respectively;

an eighth transverse cross-section formed at a height of 301mm of the blade body (2), the axial width, chord length, stagger angle, inlet angle of the eighth transverse cross-section being 100.30, 147.16, 43.02 °, 88.50 ° respectively;

a ninth transverse cross-section formed at the height 343mm of the blade body (2), the axial width, chord length, stagger angle, inlet angle of the ninth transverse cross-section being 87.52 °, 143.43 °, 37.62 °, 100.60 °, respectively;

a tenth transverse cross-section formed at a height of 385mm of the blade body (2), the tenth transverse cross-section having an axial width, chord length, stagger angle, inlet angle of 74.74 °, 139.18 °, 32.45 °, 113.86 °, respectively;

an eleventh transverse cross-section formed at a height of 427mm of the blade body (2), the eleventh transverse cross-section having an axial width, chord length, stagger angle, inlet angle of 62.55 °, 134.68 °, 27.56 °, 126.22 °;

a twelfth transverse cross-section formed at a height of 469mm of the blade body (2), the axial width, chord length, stagger angle, inlet angle of the twelfth transverse cross-section being 51.53 °, 130.44 °, 23.10 °, 137.24 ° respectively;

a thirteenth transverse cross-section formed at a height of 511mm of the blade body (2), the thirteenth transverse cross-section having an axial width, chord length, stagger angle, inlet angle of 42.30 °, 126.47 °, 19.29 °, 147.61 ° respectively;

a fourteenth transverse section formed at the position where the height of the blade body (2) is 520 mm-550 mm, and the axial width, chord length, installation angle and inlet angle of the fourteenth transverse section are 35.71 mm-40.57 mm, 123.23 mm-125.67 mm, 16.57-18.58 degrees and 149.55-154.98 degrees respectively.

5. Penult rotor blade according to claim 1, characterized in that the blade root (1) is a circular arc fir tree blade root (1); the axial width of the blade root (1) is 180mm and the total height of the blade root (1) is 72.35 mm.

6. Penult rotor blade according to claim 1, characterized in that a water erosion prevention part is provided at the top back arc of the blade body (2); the water erosion preventing portion is formed by intermediate frequency quenching, or the water erosion preventing portion is formed by laser hardening.

7. A rotor blade row, characterized by comprising the penultimate rotor blade of any one of claims 1 to 6.

8. The moving blade group as claimed in claim 7, wherein said penultimate moving blade is plural in number.

9. The moving blade row as claimed in claim 7, wherein the number of said penultimate moving blades is 68.

10. A steam turbine, characterized by comprising a moving blade row according to any one of claims 7 to 9.

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