EP3147458B1 - Système basse pression pour une turbine à vapeur et turbine à vapeur - Google Patents

Système basse pression pour une turbine à vapeur et turbine à vapeur Download PDF

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Publication number
EP3147458B1
EP3147458B1 EP16177412.0A EP16177412A EP3147458B1 EP 3147458 B1 EP3147458 B1 EP 3147458B1 EP 16177412 A EP16177412 A EP 16177412A EP 3147458 B1 EP3147458 B1 EP 3147458B1
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EP
European Patent Office
Prior art keywords
low
deflection
pressure system
turbine
flow
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.)
Not-in-force
Application number
EP16177412.0A
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German (de)
English (en)
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EP3147458A1 (fr
Inventor
Ingo Stephan
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Siemens AG
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Siemens AG
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Publication of EP3147458A1 publication Critical patent/EP3147458A1/fr
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Publication of EP3147458B1 publication Critical patent/EP3147458B1/fr
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Anticipated expiration legal-status Critical

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Classifications

    • 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
    • F01D17/00—Regulating or controlling by varying flow
    • F01D17/10—Final actuators
    • F01D17/12—Final actuators arranged in stator parts
    • F01D17/14—Final actuators arranged in stator parts varying effective cross-sectional area of nozzles or guide conduits
    • F01D17/16—Final actuators arranged in stator parts varying effective cross-sectional area of nozzles or guide conduits by means of nozzle vanes
    • F01D17/162—Final actuators arranged in stator parts varying effective cross-sectional area of nozzles or guide conduits by means of nozzle vanes for axial flow, i.e. the vanes turning around axes which are essentially perpendicular to the rotor centre line
    • 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
    • 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
    • F01K7/165—Controlling means specially adapted therefor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2220/00—Application
    • F05D2220/30—Application in turbines
    • F05D2220/31—Application in turbines in steam turbines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2240/00—Components
    • F05D2240/10—Stators
    • F05D2240/12—Fluid guiding means, e.g. vanes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2270/00—Control
    • F05D2270/01—Purpose of the control system
    • F05D2270/20—Purpose of the control system to optimize the performance of a machine

Definitions

  • the present invention relates to a low-pressure system for a steam turbine. Furthermore, the invention relates to a steam turbine having a low-pressure system according to the invention.
  • Turbines are turbomachines designed to convert internal energy of a flowing fluid into mechanical energy.
  • Known turbines have a turbine shaft rotatably mounted in a turbine shaft with a plurality of blades.
  • Modern turbines have vanes in the turbine housing configured to divert the flowing fluid to provide more efficient flow of the blades. This impingement of the blades creates a torque that rotates the turbine shaft. This mechanical energy can be converted, for example, via a generator into electrical energy.
  • cost-optimized steam turbines In order to reduce investment costs and space requirements, cost-optimized steam turbines, in contrast to conventional steam turbines at the same or almost the same power a relatively greatly reduced footprint or a relatively greatly reduced volume. To achieve the same performance, a stronger deflection of the steam flow in the cost-optimized steam turbine is required. Outflow surfaces at the end of the low-pressure stage are thus formed relatively small at cost-optimized steam turbines. Furthermore, such steam turbines are operated with overload, ie above their rated load in order to achieve the same power. Nominal load is a load condition in which the turbine is operated with its capacity for swallowing. This leads to an increase in the outflow velocity and an enlargement of a velocity component of the vapor flow in the circumferential direction. In other words, an exhaust steam of a cost-optimized steam turbine has a greater swirl than a conventional, in particular an efficiency-optimized, steam turbine. Such a twist has a negative effect in particular on the efficiency of the steam turbine.
  • Another negative effect of the spin is its effect on blade dynamics of the low pressure stage due to aerodynamic feedback. This is effected in particular by a radial flow component of the exhaust steam flow and, in particular, relates to a last blade of the low-pressure stage in the flow direction of the steam turbine. A thus caused varying pressure distribution over the circumference of the blade blading vibrates the blades, which also reduce efficiency and wear-promoting effect and lead to increased noise.
  • the object is achieved by a low-pressure system for a steam turbine, which is flowed through by a vapor stream in a flow direction for generating a rotational movement.
  • the low pressure system includes a low pressure stage having a turbine housing, at least one turbine shroud arranged on the turbine housing, a turbine shaft having a shaft longitudinal axis, the turbine shaft being rotatable about the shaft longitudinal axis relative to the turbine housing, and at least one blade ring disposed on the turbine shaft.
  • a first deflecting grid is arranged downstream of the low-pressure stage in the flow-through direction, the first deflecting grid having a plurality of deflecting elements arranged such that a vapor stream flowing through the first deflecting grid in the throughflow direction with a circumferential flow component through the deflecting elements into one first deflecting direction is deflected, wherein the first deflecting direction crosses a direction parallel to the shaft longitudinal axis and wherein the low pressure system comprises a second deflecting arranged in the flow direction behind the first deflecting and for deflecting the steam flow in a second deflection opposite to the first deflection direction for Wiedereh submittedrn the Abdampfstromes a direction is formed parallel to the shaft longitudinal axis.
  • a low-pressure system is a combination of a low-pressure stage and a downstream in the flow direction first deflecting grid.
  • the low-pressure stage is formed, for example, according to a conventional low-pressure stage of a cost-optimized steam turbine, which preferably has a plurality of vane ring-vane pairs, wherein a vane ring is connected upstream of an associated blade ring.
  • the first deflecting grid has an arrangement of deflecting elements which are shaped, for example, in the manner of a turbine blade.
  • the deflection elements are designed to divert a Abdampfstrom after leaving the last stage of the low-pressure stage.
  • the deflection is preferably carried out by laminar or substantially laminar inflow and outflow of the deflecting elements.
  • the first deflection grille is preferably held rigidly or substantially rigidly relative to the blade rings like a blade ring of the low-pressure stage and thus preferably can not be rotated about the turbine longitudinal axis.
  • the deflecting elements preferably have a material which corresponds to or essentially corresponds to a material of the guide vanes or rotor blades.
  • An optimal first deflection direction is particularly dependent on a load state of the steam turbine.
  • a first deflection direction approximates a direction of the wavelength axis, in particular parallel to the wavelength axis.
  • a pressure build-up is effected by the deflecting grid.
  • the first deflection direction preferably away from the direction of the wavelength axis.
  • a pressure drop is caused by the deflecting grid.
  • an average to higher load is essentially dealt with, since these operating conditions are of particular importance for operation of a steam turbine.
  • the first deflection direction is therefore preferably approximated to the direction of the wavelength axis.
  • the turbine housing of the low pressure stage surrounds the entire low-pressure system in the radial direction and thus seals radially outward.
  • the turbine housing of the low-pressure stage or of the low-pressure system preferably forms a section of a steam turbine housing of a steam turbine.
  • the low-pressure system has the advantage over conventional low-pressure stages that an exhaust stream of the low-pressure system has a smaller swirl component in the circumferential direction than a conventional low-pressure stage.
  • the low-pressure system has the first deflecting grid, by means of which the vapor stream can be deflected in a first deflection direction.
  • the first deflection direction outside the invention is preferably a direction that approximates a direction of the wavelength axis.
  • a further advantage is that an aerodynamic feedback can be reduced by the first deflection grille, as this is achieved by reducing the circumferentially acting Swirl component harmonizing acts on the steam flow.
  • fewer oscillations are thus transferred from the exhaust steam flow to the rotor blades, in particular the last rotor blades in the flow direction, to the low-pressure stage. This leads to improved efficiency as well as reduced wear and reduced noise emissions.
  • the low-pressure system according to the invention thus enables an improvement of cost-optimized steam turbines in terms of efficiency, wear, performance and noise emissions.
  • the low-pressure system preferably has a second deflecting grid, which is arranged downstream of the first deflecting grid and is designed to divert the steam flow into a second deflecting direction.
  • the second deflecting grid preferably has one of the features described above for the first deflecting grid.
  • the second deflecting grid can be designed similarly to the first deflecting grid or the first deflecting grid.
  • a second or further deflection grating has the advantage that a deflection of the exhaust steam flow can take place in two stages.
  • a steam flow that is too weakly deflected further in particular in a direction parallel to the turbine longitudinal axis, can be deflected via the second deflecting grid. In this way, a fine adjustment of the deflection of the exhaust steam of the low-pressure system in an advantageous manner possible.
  • the second deflecting grid is designed to divert the steam flow in the second deflection direction.
  • the first deflecting grid is preferably designed to deflect the exhaust steam flow in the first deflecting direction, wherein the first deflecting direction crosses a direction parallel to the turbine longitudinal axis. Due to the second deflection grille, the exhaust steam flow can be deflected in a second deflection direction opposite to the first deflection direction and thereby approachable again in a direction parallel to the turbine longitudinal axis. In this way, for example, depending on a load condition of a steam turbine, a particularly favorable pressure distribution in the low-pressure system can be achieved.
  • the first deflecting grid is designed in accordance with a blading of a compressor stage, so that the vapor stream is compressed in the direction of flow when it flows through the first deflecting grid.
  • the deflection elements correspond to the compressor blades of the compressor stage. Accordingly, the deflecting elements, in contrast to guide blades or rotor blades, are made slimmer and preferably have a smaller curvature.
  • the deflecting grid is thus designed in such a way that an exhaust steam stream flowing through the deflecting grid is deflected towards the longitudinal axis of the shaft and thereby compressed.
  • the low-pressure system comprises a diffuser, which is arranged adjacent to the blade ring in the flow direction behind the blade ring.
  • a diffuser causes a slowdown and a pressure increase of the exhaust steam, so that in a steam turbine with a high-pressure stage and a low-pressure stage, a larger pressure is degraded. As a result, the efficiency of a steam turbine can be improved.
  • the first deflecting grid is arranged in the diffuser.
  • the deflection elements are pivotable about a Umlenkelementachse extending radially or substantially radially to the shaft longitudinal axis.
  • the first deflection direction can thus be influenced or changed by pivoting or rotating the deflecting elements around the deflecting element axis.
  • exhaust steam flows can be deflected depending on a load state of the steam turbine. This has the advantage that the positive effects of the deflecting grid can be optimized by demand or load-oriented alignment of the deflecting elements.
  • the deflection elements are designed as deflection vanes.
  • Such deflecting elements have an airfoil-shaped cross section with a rounded first tip, a second tip and a curvature formed between the tips.
  • the cross section has a relatively high magnification in a first section starting from the first point and a slight taper formed in a second section to the second point of the cross section.
  • the second portion preferably has a width that is a multiple of a width of the first portion.
  • the curvature preferably extends between 25 ° and 50 °, in particular between 30 ° and 45 °.
  • a maximum thickness of the deflecting element is preferably between 1/10 and 1/20, in particular between 1/14 and 1/16 of a width of the deflecting element.
  • a length of the deflecting element extends along the Umlenkelementachse.
  • the object is achieved by a steam turbine with a high pressure stage and a low pressure stage.
  • the steam turbine has a low-pressure system according to the invention, the low-pressure stage being designed as part of the low-pressure system.
  • the steam turbine according to the invention is preferably designed as a cost-optimized steam turbine and has at the highest possible power on a small size and small outflow surfaces of the low-pressure stage.
  • the steam turbine according to the invention has the same advantages as the low-pressure system according to the invention.
  • a section of a low pressure system 1 is shown.
  • the low-pressure system 1 has a low-pressure stage 3 with a turbine housing 4 and a turbine shaft 6 arranged in the turbine housing 4 with a shaft longitudinal axis 7.
  • the turbine shaft 6 is mounted rotatable about the shaft longitudinal axis 7 relative to the turbine housing 4.
  • the low-pressure stage 3 has a stator blades 5 a having vane ring 5, which is held on the turbine housing 4.
  • the low pressure stage 3 in the flow direction D behind the vane ring 5 a rotor blades 8 a having blade ring 8, which is held on the turbine shaft 6.
  • a lying in the flow direction D of a steam flow end of the low-pressure stage 3 is indicated by a dashed line.
  • the low-pressure system 1 In the flow direction D behind the low-pressure stage 3, the low-pressure system 1, a first deflecting grid 9 with a plurality of deflecting elements 9a, which are distributed uniformly over the circumference of the first deflecting grid 9.
  • the deflection elements 9a are about a Umlenkelementachse 9b relative to Turbine housing 4 rotatable.
  • a side of the first deflecting grid 9 facing away from the turbine shaft 6 is held on the turbine housing 4; a diffuser inner wall 11 is arranged on a side of the first deflecting grid 9 facing the turbine shaft 6.
  • the turbine housing 4 and the diffuser inner wall 11 form a diffuser 10 of the low-pressure system 1.
  • a vapor stream flowing in the flow direction D through the low pressure system 1 is deflected such that a swirl component of the vapor stream is reduced in the circumferential direction.
  • the efficiency of the low pressure system 1 can be improved and aerodynamic feedback of the steam flow to the low pressure stage 3 can be reduced.
  • Fig. 2 schematically shows a plan view of the low-pressure system 1 according to the invention in a first load state.
  • the steam turbine 2 In the first load state, the steam turbine 2 is operated with nominal load or low overload.
  • a steam flow At rated load, a steam flow has a size at which a capacity of the steam turbine 2 is reached.
  • the absorption capacity of the steam turbine 2 is exceeded.
  • the vapor stream has at the end of the low-pressure stage 3 a high swirl component, which is reduced by the downstream deflector 9.
  • Operating a conventional, identical low-pressure stage 3 with such a vapor stream is characterized by high outlet losses at the end of the low-pressure stage 3, since no deflecting grid 9 is present for reducing the swirl component.
  • An efficiency of the low-pressure system 1 according to the invention is thus higher in the vapor stream of the first load state than an efficiency of a conventional, otherwise identical low-pressure stage 3, which is acted upon by an equal-sized vapor stream.
  • the vapor stream leaves the vane ring 5 at a first absolute speed c1, which is composed of a first relative speed w1 and a first peripheral speed u1, and strikes the blade ring 8, causing it to rotate.
  • the vapor stream leaves the blade ring 8 with a second absolute speed c2, which is composed of a second relative speed w2 and a second peripheral speed u2.
  • the steam flow thus has, after the blade ring 8 and in front of the first deflection grille 9, a high swirl component counter to the circumferential direction, this is also referred to as a counter-swirl.
  • the deflecting elements 9a of the first deflecting grid 9 are aligned for the first load state such that the vapor stream is deflected in the first deflecting direction R1, wherein the first deflecting direction R1 of the flow direction D is approximated. Accordingly, the vapor flow after the first deflecting grid 9 has a smaller swirl component in the circumferential direction than immediately before the first deflecting grid 9.
  • a third pressure p3 immediately after the first deflecting grid 9 is higher than a second pressure p2 immediately before the first deflecting grid 9.
  • Fig. 3 schematically shows a plan view of the low-pressure system 1 according to the invention in a second load state.
  • the steam turbine 2 In the second load state, the steam turbine 2 is operated with medium load. At medium load, a steam flow is in a range that is below the intake capacity of the steam turbine 2 and above a light load.
  • the efficiency of the low-pressure system 1 according to the invention is lower in the steam flow of the second load state than at rated load but higher than in a conventional, otherwise identical low-pressure stage 3, which is acted upon by an equal-sized vapor stream.
  • the vapor stream leaves the vane ring 5 at a first absolute speed c1, which is composed of a first relative speed w1 and a first peripheral speed u1, and strikes the blade ring 8, causing it to rotate.
  • the vapor stream leaves the blade ring 8 at a second absolute speed c2 resulting from a second relative speed w2 and a second peripheral speed u2 is composed.
  • the steam flow thus has, after the blade ring 8 and before the first deflecting grid 9, a small swirl component counter to the circumferential direction (counter-swirl).
  • the deflecting elements 9a of the first deflecting grid 9 are aligned for the second load state such that the vapor stream is deflected in the first deflecting direction R1, wherein the first deflecting direction R1 of the flow direction D closely approximates or parallel or almost parallel to this. Accordingly, the vapor flow after the first deflecting grid 9 has a significantly smaller swirl component in the circumferential direction than immediately before the first deflecting grid 9.
  • a third pressure p3 immediately after the first deflecting grid 9 is higher than a second pressure p2 immediately before the first deflecting grid 9.
  • Fig. 4 shows schematically in a plan view the low-pressure system 1 according to the invention in a third load state.
  • the steam turbine 2 is operated with a light load.
  • a steam flow is in a range which is far below the absorption capacity of the steam turbine 2.
  • the efficiency of the low-pressure system 1 according to the invention is substantially lower than the rated load but higher than in the case of a conventional, otherwise identical low-pressure stage 3, which is charged with an equal-sized steam flow.
  • the vapor stream leaves the vane ring 5 at a first absolute speed c1, which is composed of a first relative speed w1 and a first peripheral speed u1, and strikes the blade ring 8, causing it to rotate.
  • the vapor stream leaves the blade ring 8 at a second absolute speed c2, which is composed of a second relative speed w2 and a second peripheral speed u2.
  • the steam flow points towards the blade ring 8 and before the first deflecting 9 thus a small swirl component in the circumferential direction, this is also referred to as Mitdrall.
  • the deflecting elements 9a of the first deflecting grid 9 are aligned for the third load state such that the vapor stream is deflected in the first deflecting direction R1, the first deflecting direction R1 pointing farther away from the throughflow direction D than the second absolute velocity c2.
  • a third pressure p3 immediately after the first deflecting grid 9 is less than a second pressure p2 immediately before the first deflecting grid 9.
  • Fig. 5 schematically shows the structure of a steam turbine according to the invention 2.
  • the steam turbine 2 has a high pressure stage 12, in addition to the flow direction D a low pressure system 1 according to the invention with a low pressure stage 3 and a diffuser 10 is arranged.
  • a first deflecting grid 9 is arranged in the diffuser 10.
  • the first deflecting grid 9 is arranged between the low-pressure stage 3 and the diffuser 10.
  • a second deflecting grid is arranged behind the first deflecting grid 9 in the throughflow direction D.

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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)

Claims (7)

  1. Système basse pression (1) pour une turbine à vapeur (2), qui peut être traversé par un flux de vapeur dans une direction de traversée (D) en vue de la génération d'un mouvement de rotation, présentant un étage de basse pression (3) avec un corps de turbine (4), au moins une couronne d'aubes directrices (5) disposée au niveau du corps de turbine (4), un arbre de turbine (6) avec un axe longitudinal d'arbre (7), dans lequel l'arbre de turbine (6) est monté autour de l'axe longitudinal d'arbre (7) de manière rotative par rapport au corps de turbine (4), et au moins une couronne d'aubes mobiles (8) qui est disposée sur l'arbre de turbine (6), dans lequel est disposée de manière adjacente à la couronne d'aubes mobiles (8) dans la direction de traversée (D) derrière l'étage de basse pression (3) une première grille de déviation (9), dans lequel la première grille de déviation (9) présente une pluralité d'éléments de déviation (9a) qui sont disposés de telle sorte qu'un flux de vapeur s'écoulant dans la direction de traversée (D) à travers la première grille de déviation (9) est dévié par le biais des éléments de déviation (9a) dans une première direction de déviation (R1) avec un composant d'écoulement agissant dans la direction périphérique, dans lequel la première direction de déviation croise une direction parallèle à l'axe longitudinal d'arbre (7), caractérisé en ce que le système basse pression (1) présente une deuxième grille de déviation qui est disposée dans la direction de traversée (D) derrière la première grille de déviation (9) et est réalisée en vue de la déviation du flux de vapeur dans une deuxième direction de déviation opposée à la première direction de déviation en vue du rapprochement du flux de vapeur d'évacuation d'une direction parallèle à l'axe longitudinal d'arbre (7).
  2. Système basse pression (1) selon l'une des revendications précédentes, caractérisé en ce que la première grille de déviation (9) est réalisée en fonction d'un aubage d'un étage de condensateur, de sorte que le flux de vapeur est condensé lors de la traversée de la première grille de déviation (9) dans la direction de traversée (D).
  3. Système basse pression (1) selon l'une des revendications précédentes, caractérisé en ce que le système basse pression (1) présente un diffuseur (10) qui est disposé de manière adjacente à la couronne d'aubes mobiles (8) dans la direction de traversée (D) derrière la couronne d'aubes mobiles (8).
  4. Système basse pression (1) selon la revendication 3, caractérisé en ce que la première grille de déviation (9) est disposée dans le diffuseur (10).
  5. Système basse pression (1) selon l'une des revendications précédentes, caractérisé en ce que les éléments de déviation (9a) peuvent pivoter autour d'un axe d'éléments de déviation (9b) s'étendant dans le sens radial ou pour l'essentiel dans le sens radial par rapport à l'axe longitudinal d'arbre (7).
  6. Système basse pression (1) selon l'une des revendications précédentes, caractérisé en ce que les éléments de déviation (9a) sont réalisés en tant qu'aubes de déviation.
  7. Turbine à vapeur (2) présentant un étage de haute pression (12) et un étage de basse pression (3), caractérisé en ce que la turbine à vapeur (2) présente un système basse pression (1) qui est réalisé selon l'une des revendications 1 à 6.
EP16177412.0A 2015-09-25 2016-07-01 Système basse pression pour une turbine à vapeur et turbine à vapeur Not-in-force EP3147458B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102015218493.5A DE102015218493A1 (de) 2015-09-25 2015-09-25 Niederdrucksystem und Dampfturbine

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EP3147458A1 EP3147458A1 (fr) 2017-03-29
EP3147458B1 true EP3147458B1 (fr) 2018-09-12

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DE (1) DE102015218493A1 (fr)

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CN110500140A (zh) * 2019-09-22 2019-11-26 中国航发沈阳发动机研究所 一种静子叶片

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Publication number Priority date Publication date Assignee Title
CH582823A5 (fr) 1975-03-06 1976-12-15 Bbc Brown Boveri & Cie
DE59001693D1 (de) * 1989-09-12 1993-07-15 Asea Brown Boveri Axialdurchstroemte turbine.
DE4422700A1 (de) * 1994-06-29 1996-01-04 Abb Management Ag Diffusor für Turbomaschine
JP2006138259A (ja) 2004-11-12 2006-06-01 Mitsubishi Heavy Ind Ltd 軸流タービン
JP4848440B2 (ja) 2009-03-03 2011-12-28 株式会社日立製作所 軸流タービン
US20140314549A1 (en) * 2013-04-17 2014-10-23 General Electric Company Flow manipulating arrangement for a turbine exhaust diffuser
JP6125351B2 (ja) 2013-06-27 2017-05-10 株式会社東芝 蒸気タービン

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EP3147458A1 (fr) 2017-03-29

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