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EP1655458A1 - Diffuseur pour une turbine à vapeur - Google Patents

Diffuseur pour une turbine à vapeur Download PDF

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Publication number
EP1655458A1
EP1655458A1 EP04026196A EP04026196A EP1655458A1 EP 1655458 A1 EP1655458 A1 EP 1655458A1 EP 04026196 A EP04026196 A EP 04026196A EP 04026196 A EP04026196 A EP 04026196A EP 1655458 A1 EP1655458 A1 EP 1655458A1
Authority
EP
European Patent Office
Prior art keywords
diffuser
flow
coolant
wall
medium
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Withdrawn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
EP04026196A
Other languages
German (de)
English (en)
Inventor
Heinrich Dr. Stüer
Thomas Dr. Thiemann
Frank Truckenmüller
Thorsten Wolf
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.)
Siemens AG
Siemens Corp
Original Assignee
Siemens AG
Siemens Corp
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 Siemens AG, Siemens Corp filed Critical Siemens AG
Priority to EP04026196A priority Critical patent/EP1655458A1/fr
Publication of EP1655458A1 publication Critical patent/EP1655458A1/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Withdrawn legal-status Critical Current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
    • 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
    • F01D25/00—Component parts, details, or accessories, not provided for in, or of interest apart from, other groups
    • F01D25/08—Cooling; Heating; Heat-insulation
    • F01D25/12—Cooling
    • 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
    • F05D2240/14—Casings or housings protecting or supporting assemblies within
    • 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
    • F05D2250/00—Geometry
    • F05D2250/50—Inlet or outlet
    • F05D2250/52—Outlet
    • 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
    • F05D2260/00—Function
    • F05D2260/20—Heat transfer, e.g. cooling
    • 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
    • F05D2260/00—Function
    • F05D2260/20—Heat transfer, e.g. cooling
    • F05D2260/201—Heat transfer, e.g. cooling by impingement of a fluid

Definitions

  • the invention relates to a diffuser for pressure recovery in the outflow region of a steam turbine, with an inlet and a housing wall for limiting a flow medium.
  • the invention also relates to a method for producing a diffuser comprising an inlet and a housing wall for limiting a flow medium.
  • a turbomachine is z.
  • a diffuser is connected downstream to increase the efficiency of a steam turbine as an embodiment of a turbomachine of a final stage.
  • kinetic energy is converted into pressure.
  • the static pressure at the blade outlet can be lowered below the condenser pressure. This allows a greater pressure gradient in the final stage and thus a higher power output of the steam turbine. Without a diffuser, the pressure difference would be lower.
  • a diffuser is understood as meaning a flow channel through which a flow medium can be flowed, wherein the flow medium has a pressure increase in a flow direction. In this case, a conversion of kinetic energy into potential energy takes place. This energy conversion is desirable in many technical applications. So z. B. the Diffuser of a compressor to convert the high kinetic energy of the flow medium at the impeller outlet as completely as possible and low-loss in static pressure.
  • the achievable in a diffuser flow pressure recovery depends on several parameters. It is influenced by the diffuser opening angle as well as the flow conditions and the boundary layer thickness in the diffuser inlet.
  • Diffusers are known with a conical surface which widens in the direction of flow ("axial diffuser").
  • the opening angle of such a diffuser is usually not more than 15 °, since above this opening angle, the flow separates from the walls of the diffuser, which leads to strong flow losses and causes flow noise. In addition, the unsteady flow due to the separation leads to an increased structural load on the diffuser.
  • diffusers with a maximum opening angle of 15 ° are too long, their installation in existing installations is more difficult.
  • axial diffusers also axial-radial and radial diffusers are used. In the case of the axial-radial diffuser, the inflow takes place axially and the outflow radially. The radial diffuser is flowed through purely radially. All other considerations include these designs.
  • the flow separation on the diffuser wall is caused by the friction of decelerated fluid particles of the flow medium. These braked fluid particles no longer have sufficient kinetic energy to overcome a pressure increase. In extreme cases, fluid particles on the wall can reverse their direction of flow. The diffuser would therefore be ineffective.
  • diffusers without measures affecting the boundary layer are executed and essentially by means of empirical Experiences designed. Design parameters here are the opening angle and the cross-sectional profile. In part, baffles are used to favorably influence the flow in the diffuser.
  • Diffusers with high pressure recovery require the largest possible ratio of exit area to entrance area.
  • a known technical solution to increase the pressure recovery is to open the diffusers strong, but to prevent the flow separation by a Grenz fürabsaugung or -blasblasung. This requires a suction device which leads to a pressure sink on the diffuser wall, wherein the achievable by the suction pressure should be below the wall pressure.
  • the object of the invention is to provide a diffuser with which a high pressure recovery is possible.
  • a further object of the invention is to provide a method for producing a diffuser, with which it is possible to achieve a high pressure recovery.
  • the object directed towards the diffuser is achieved by a diffuser for pressure recovery in the outflow region of a steam turbine, having an inlet and a housing wall for defining a flow medium, the diffuser having coolant for cooling partial regions of the housing wall, wherein the coolant is designed such that the flow medium condenses during operation on the housing wall.
  • the invention is based on the fact that the flow medium can be locally condensed in the case of diffusers in the vicinity of the housing wall.
  • the strong increase in density resulting from the condensation acts like a boundary layer suction.
  • the increase in density can be at a factor of 30,000.
  • the invention further assumes that the subregions of the housing wall are cooled to a temperature below the saturation temperature. Thermal energy is withdrawn near slow flow of fluid from the housing wall, causing it to condense on the housing wall.
  • the condensed fluid particles can hardly obstruct or block the flow. The condensation of slow fluid particles affects the flow boundary layer of the flow.
  • Another advantage of the diffuser according to the invention is that the total volume can be reduced, since the boundary layer influencing by local condensation of the diffuser can be built shorter.
  • the invention assumes that even at low condensation rates, which lead to small pressure sinks, a significant increase in the ratio of exit to the inlet surface of the diffuser is possible by increasing the ratio of exit to the entrance surface, a higher pressure recovery is possible.
  • the coolant can flow through channels with cold medium on an inside or outside of the housing wall.
  • the coolant with a spray device for spraying an inside or outside of the housing wall formed with a cold medium.
  • cold water is used as the medium.
  • the cold water can z. B. be taken from the cooling water circuit of the entire power plant.
  • the second object is achieved by a method for producing a diffuser comprising an inlet and a housing wall for limiting a flow medium, wherein cooling means are attached to the diffuser for cooling partial regions of the housing wall.
  • channels through which cold medium can flow are arranged on an inside or outside of the housing wall.
  • a spraying device for spraying the inside or outside of the housing wall with a cold medium is arranged.
  • water is used as the cold medium.
  • a flow medium flows through a flow channel 3 which has a substantially widening flow cross-section and comprises guide vanes 4 and rotor blades 5 via an inlet channel 2, which is not illustrated in more detail.
  • the blades 5 are fixedly mounted on a rotor 6.
  • the rotor 6 is rotatably supported via a bearing device 7.
  • the rotor 6 is set by a relaxation of the flow medium and subsequent energy conversion in a rotation through which a generator, not shown, can be driven to generate electricity.
  • a diffuser 9 is arranged.
  • the diffuser 9 is used to convert the kinetic energy of the flow medium into pressure energy. This conversion should take place as far as possible with low energy losses.
  • FIG. 2 shows a section through a diffuser 9 according to the prior art.
  • the diffuser 9 essentially has a hub-side wall 10 and an outer housing wall 11.
  • the rotor 6 is rotatably mounted about a rotation axis 12.
  • FIG. 2 only one moving blade 5 is shown by way of example.
  • a fluid particle flowing out after an output stage 8 flows along a movement path (trajectory).
  • FIG. 2 several trajectories 13 are shown by way of example.
  • On the outer housing wall can be formed by a detachment, a trajectory 13 ', which is characterized by a reversal of the Direction of movement of the fluid particle back to the power amplifier 8 is characterized. This trajectory 13 'is undesirable.
  • FIG. 3 shows a diffuser 9 according to the invention.
  • the diffuser 9 is arranged in the outflow region 14 of the steam turbine 1.
  • the diffuser has an inlet 15 and a hub-side wall 10 and a housing wall 11 for limiting a flow medium.
  • the diffuser 9 is characterized by a coolant 16 for cooling.
  • the coolant comprises a pipe 19 which is flowed through by a cold medium.
  • the coolant 16 is in this case designed such that the flow medium condenses during operation of the steam turbine 1 on the surface of the pipe 19, and thus generates a pressure sink.
  • the pipe 19 should be mounted in a near area to the diffuser 9 for this purpose.
  • the coolant 16 can in this case be arranged in such a way that it has channels through which cold medium can flow. Furthermore, the channel through which the cold medium can flow can be arranged on an inner side of the hub-side wall 10 or the housing wall 11.
  • the embodiments of the coolant shown in Figures 3 and 4 are arranged for clarity, only the outer housing wall 11. Of course, the coolant 16 may be disposed on the hub side wall 10.
  • the through-flowable with cold medium channel can also be arranged on an outer side 18 of the hub-side wall 10 or the outer housing wall 11.
  • the coolant 16 can be applied to the locations in the diffuser where release of the flow medium is to be expected.
  • FIG. 4 shows a further embodiment of the coolant 16.
  • the coolant 16 is in this case formed as a spraying device for spraying the hub-side wall 10 or housing wall 11 with a cold medium.
  • the cooling means 16 designed as a spraying device is designed in such a way that the cold medium is sprayed onto the inside 17 of the housing wall.
  • the coolant 16 designed as a spraying device can be designed such that the cold medium is sprayed onto the outside 18 of the housing wall 11.
  • coolant 16 designed as a spraying device can also be arranged on the hub-side wall 10.
  • cold water can be removed from the cooling water circuit.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
EP04026196A 2004-11-04 2004-11-04 Diffuseur pour une turbine à vapeur Withdrawn EP1655458A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP04026196A EP1655458A1 (fr) 2004-11-04 2004-11-04 Diffuseur pour une turbine à vapeur

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP04026196A EP1655458A1 (fr) 2004-11-04 2004-11-04 Diffuseur pour une turbine à vapeur

Publications (1)

Publication Number Publication Date
EP1655458A1 true EP1655458A1 (fr) 2006-05-10

Family

ID=34927239

Family Applications (1)

Application Number Title Priority Date Filing Date
EP04026196A Withdrawn EP1655458A1 (fr) 2004-11-04 2004-11-04 Diffuseur pour une turbine à vapeur

Country Status (1)

Country Link
EP (1) EP1655458A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2010242759A (ja) * 2009-04-07 2010-10-28 General Electric Co <Ge> 排出損失を減少させるための冷却式排出フードプレート

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE907180C (de) * 1951-03-08 1954-03-22 Rolf Roeder Dipl Ing Auslassdiffusor kurzer Baulaenge fuer Dampfturbinen
FR1209527A (fr) * 1958-08-12 1960-03-02 Westinghouse Electric Corp Appareil de contrôle d'écoulement
CH388986A (de) * 1960-12-05 1965-03-15 Licentia Gmbh Anordnung zum Mischkühlen des aus der Endstufe von Dampfturbinen austretenden Dampfes
EP0600129A1 (fr) * 1992-01-13 1994-06-08 BRANDON, Ronald E. Diffuseur-condenseur pour la vapeur saturée

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE907180C (de) * 1951-03-08 1954-03-22 Rolf Roeder Dipl Ing Auslassdiffusor kurzer Baulaenge fuer Dampfturbinen
FR1209527A (fr) * 1958-08-12 1960-03-02 Westinghouse Electric Corp Appareil de contrôle d'écoulement
CH388986A (de) * 1960-12-05 1965-03-15 Licentia Gmbh Anordnung zum Mischkühlen des aus der Endstufe von Dampfturbinen austretenden Dampfes
EP0600129A1 (fr) * 1992-01-13 1994-06-08 BRANDON, Ronald E. Diffuseur-condenseur pour la vapeur saturée

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2010242759A (ja) * 2009-04-07 2010-10-28 General Electric Co <Ge> 排出損失を減少させるための冷却式排出フードプレート

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