EP0575659A1 - Enveloppe d'admission pour turbine à gaz - Google Patents

Enveloppe d'admission pour turbine à gaz Download PDF

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Publication number
EP0575659A1
EP0575659A1 EP92110887A EP92110887A EP0575659A1 EP 0575659 A1 EP0575659 A1 EP 0575659A1 EP 92110887 A EP92110887 A EP 92110887A EP 92110887 A EP92110887 A EP 92110887A EP 0575659 A1 EP0575659 A1 EP 0575659A1
Authority
EP
European Patent Office
Prior art keywords
housing
feeds
tangential
inlet
dimensioned
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.)
Withdrawn
Application number
EP92110887A
Other languages
German (de)
English (en)
Inventor
Jakob Dr. Keller
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
ABB Asea Brown Boveri Ltd
ABB AB
Original Assignee
ABB Asea Brown Boveri Ltd
Asea Brown Boveri AB
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by ABB Asea Brown Boveri Ltd, Asea Brown Boveri AB filed Critical ABB Asea Brown Boveri Ltd
Priority to EP92110887A priority Critical patent/EP0575659A1/fr
Priority to JP15209193A priority patent/JPH0658103A/ja
Publication of EP0575659A1 publication Critical patent/EP0575659A1/fr
Withdrawn legal-status Critical Current

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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
    • F01D9/00—Stators
    • F01D9/02—Nozzles; Nozzle boxes; Stator blades; Guide conduits, e.g. individual nozzles
    • F01D9/04—Nozzles; Nozzle boxes; Stator blades; Guide conduits, e.g. individual nozzles forming ring or sector
    • F01D9/047—Nozzle boxes

Definitions

  • the invention relates to an inlet housing for a single-flow, axially flowed high-pressure steam turbine with at least two separate inlets.
  • the power control of steam turbines today takes place either by adapting or throttling the live steam pressures, known as sliding pressure control or throttle control, or by partially applying a specially designed constant pressure stage via individual sectors of a nozzle ring that can be switched off and regulated.
  • This type of regulation known as nozzle group regulation, is usually superior to the purely throttle regulation, but leads to an increase in the loss shares known under the designation “partial loading losses” when the load is reduced and thus the load is applied. If the flow in the adjoining wheel chamber is not completely mixed, partial loading of the subsequent reaction blading can also occur and thus additional, large flow losses.
  • Entry housings with concentric ring channels are known from FR-A-2 351 249.
  • the steam flows into an action wheel from two axially directed concentric ring channels, which form a nozzle box.
  • the nozzles are arranged within the ring channels. It is a classic constant pressure control stage.
  • the ring channels are fed separately.
  • One of the two ring channels has two inflow lines, each of which leads to half a ring circumference.
  • the second ring channel has four inflow lines for its four segments.
  • Turbine output is increased from idling to nominal load by first feeding a ring channel over the entire circumference and then opening the various sectors of the second ring channel one after the other. With this arrangement, there should be no vibration problems on the first row of runs when partially loaded.
  • An inlet housing with a nested double spiral leads to a type of control that has better efficiencies over the entire load range than with pure nozzle group regulation.
  • Such an inlet housing is known from CH-A-654 625. Due to the fact that it is subjected to a 360 ° extent with different mass flows depending on the load, the control stage, consisting of a nozzle box and a constant pressure wheel, can be dispensed with at low load. Particular advantages of a constructive nature can be seen in the fact that such spiral housings have a short axial length and that only two steam lines provided with terminating and regulating elements are required.
  • the cross sections of the volute casing are dimensioned for different mass flow rates, in addition to the full load, at least two partial load points can be throttled and thus run with little loss.
  • a deflection grid can be installed in front of the first row of turbine blades to be dispensed with. Steam velocities higher than usual are permitted in the inflow pipes, since kinetic energy can be fully utilized for the swirl generation. As a result, the inflow lines can be made with small cross sections and therefore cheaper.
  • the invention has for its object to be able to maintain the advantages of simple control and the previous classic design with a control wheel working on the same pressure principle in an inlet housing of the type mentioned avoiding the disadvantages of the spiral solution.
  • the advantage of the invention can be seen in particular in the fact that the flow inside the housing always remains subcritical.
  • the new measure already involves the impulse exchange in the swirl chamber of the torus.
  • the critical cross-section is passed through as it exits the housing or as it enters the turbine blades.
  • the compensating piston required for single-flow turbine parts can be arranged in the free space within the toroidal housing due to the large diameter of the control wheel, which has a favorable effect on the axial overall length of the system.
  • the inlet housing the steam flows through the pipe bends 8 and 9 to.
  • the closing and regulating elements arranged in the pipe bends 8 and 9 are not shown.
  • the inlet housing essentially consists of a rotationally symmetrical torus 4.
  • the working fluid flows tangentially into the torus.
  • the cross sections of the tangential feeds 1, 2 are dimensioned for different mass flow rates;
  • the feeds 1 are designed, for example, for 30%, the feeds 2 for 70% of the amount of steam.
  • the interior of the torus forms a swirl chamber for the tangentially flowing working fluid.
  • the outlet of the torus is provided with an annular cross section 5. This is dimensioned such that the working medium flowing into the blading has a tangential component which is of the order of magnitude of the peripheral speed of the blade sector of the first stage acted upon by the working medium, regardless of the load being driven. There is thus an axial steam inflow into the turbine from the vortex chamber in the projection.
  • the usual wheel space 16 is located between the control wheel 13 and the guide row of the first stage.
  • the radially inner boundary wall of the toroidal housing runs in the plane of the compensating piston 17 and is provided on the outside with a labyrinth-like shaft seal which is part of the gland portion 11 mentioned.
  • Reduction pieces 6, 7 are provided between the inlet openings of the two feeds, which are located in the horizontal parting plane (in contrast to the illustration in FIG. 1, where they are located in the drawing plane for reasons of clarity) and the pipe bends 8, 9.
  • the working fluid is accelerated from, for example, 60 m / sec to approx. 150 m / sec. It goes without saying that speeds higher than the stated 60 m / sec are also permissible in the pipe bends 8 and 9. This is particularly true because the kinetic energy is fully usable for swirl generation.
  • it is an optimization problem in which the higher friction losses due to increased speed have to be countered by material savings due to smaller cross-sections.
  • the speed of, for example, 280 m / sec required at the turbine inlet, in this case in front of the control wheel 13, is reached in the critical cross section immediately before the turbine inlet.
  • the swirl is generated in the vortex chamber of the torus.
  • the inlet cross-sections of the tangential feeds 1, 2 arranged in pairs are offset from one another by 180 ° and directed in such a way that the torus flows through in the same direction.
  • the vortex which causes the flow to swirl upstream of the turbine inlet, is built up when one of the feeds is open.
  • duplex control is particularly suitable in the part-load behavior of the turbine, where it has very considerable advantages over the classic nozzle group control. This is because the inflow to the first row of blades always takes place over a 360 ° circumference with every load.
  • the embodiment variant shown in FIG. 2 is characterized in that a dead space 20 for a compensating flow is provided in the radially inner part of the swirl chamber. A subcritical hollow vortex is created there with a core in the form of a detachment bubble with secondary flow.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Control Of Turbines (AREA)
  • Turbine Rotor Nozzle Sealing (AREA)
EP92110887A 1992-06-26 1992-06-26 Enveloppe d'admission pour turbine à gaz Withdrawn EP0575659A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP92110887A EP0575659A1 (fr) 1992-06-26 1992-06-26 Enveloppe d'admission pour turbine à gaz
JP15209193A JPH0658103A (ja) 1992-06-26 1993-06-23 蒸気タービン用の入口ケーシング

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP92110887A EP0575659A1 (fr) 1992-06-26 1992-06-26 Enveloppe d'admission pour turbine à gaz

Publications (1)

Publication Number Publication Date
EP0575659A1 true EP0575659A1 (fr) 1993-12-29

Family

ID=8209752

Family Applications (1)

Application Number Title Priority Date Filing Date
EP92110887A Withdrawn EP0575659A1 (fr) 1992-06-26 1992-06-26 Enveloppe d'admission pour turbine à gaz

Country Status (2)

Country Link
EP (1) EP0575659A1 (fr)
JP (1) JPH0658103A (fr)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2078821A1 (fr) * 2008-01-10 2009-07-15 Siemens Aktiengesellschaft Turbine à vapeur
CN108643978A (zh) * 2018-07-17 2018-10-12 中国船舶重工集团公司第七0三研究所 一种新型调节级喷嘴
CN109209514A (zh) * 2017-06-30 2019-01-15 曼柴油机和涡轮机欧洲股份公司 涡轮增压器的轴流式涡轮机的涡轮机流入壳体
CN109386312A (zh) * 2017-08-04 2019-02-26 曼柴油机和涡轮机欧洲股份公司 涡轮增压器的轴向涡轮的涡轮流入壳体
CN110761844A (zh) * 2019-11-29 2020-02-07 重庆江增船舶重工有限公司 一种高效率汽轮机

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2351249A1 (fr) * 1976-05-14 1977-12-09 Europ Turb Vapeur Perfectionnement a un dispositif d'admission du fluide moteur dans une turbine de grande puissance
CH654625A5 (de) * 1981-11-30 1986-02-28 Bbc Brown Boveri & Cie Einlassgehaeuse einer dampfturbine.

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2351249A1 (fr) * 1976-05-14 1977-12-09 Europ Turb Vapeur Perfectionnement a un dispositif d'admission du fluide moteur dans une turbine de grande puissance
CH654625A5 (de) * 1981-11-30 1986-02-28 Bbc Brown Boveri & Cie Einlassgehaeuse einer dampfturbine.

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2078821A1 (fr) * 2008-01-10 2009-07-15 Siemens Aktiengesellschaft Turbine à vapeur
CN109209514A (zh) * 2017-06-30 2019-01-15 曼柴油机和涡轮机欧洲股份公司 涡轮增压器的轴流式涡轮机的涡轮机流入壳体
CN109386312A (zh) * 2017-08-04 2019-02-26 曼柴油机和涡轮机欧洲股份公司 涡轮增压器的轴向涡轮的涡轮流入壳体
CN108643978A (zh) * 2018-07-17 2018-10-12 中国船舶重工集团公司第七0三研究所 一种新型调节级喷嘴
CN110761844A (zh) * 2019-11-29 2020-02-07 重庆江增船舶重工有限公司 一种高效率汽轮机

Also Published As

Publication number Publication date
JPH0658103A (ja) 1994-03-01

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