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
  • F01D5/00—Blades; Blade-carrying members; Heating, heat-insulating, cooling or antivibration means on the blades or the members
  • F01D5/02—Blade-carrying members, e.g. rotors
  • F01D5/08—Heating, heat-insulating or cooling means
  • F01D5/085—Heating, heat-insulating or cooling means cooling fluid circulating inside the rotor
• • 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
  • F01D5/00—Blades; Blade-carrying members; Heating, heat-insulating, cooling or antivibration means on the blades or the members
  • F01D5/02—Blade-carrying members, e.g. rotors
  • F01D5/08—Heating, heat-insulating or cooling means
  • F01D5/085—Heating, heat-insulating or cooling means cooling fluid circulating inside the rotor
  • F01D5/088—Heating, heat-insulating or cooling means cooling fluid circulating inside the rotor in a closed cavity
• • 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
  • F05D2260/00—Function
  • F05D2260/20—Heat transfer, e.g. cooling
  • F05D2260/205—Cooling fluid recirculation, i.e. after cooling one or more components is the cooling fluid recovered and used elsewhere for other purposes
• • 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
  • F05D2260/232—Heat transfer, e.g. cooling characterized by the cooling medium
  • F05D2260/2322—Heat transfer, e.g. cooling characterized by the cooling medium steam

Definitions

• the invention relates to a steam turbine comprising a housing and a rotor, wherein the housing has a passage for the passage of external Kuhlmedium, wherein the rotor is at least partially hollow.
• a steam turbine is understood to mean any turbine or sub-turbine through which a working medium in the form of steam flows.
• gas turbines are traversed with gas and / or air as a working medium, but that is subject to completely different temperature and pressure conditions than the steam in a steam turbine.
• gas turbines for steam turbines has eg a turbine inflow end ⁇ working medium with the highest temperature at the same time the highest pressure.
• An open cooling system, as in gas turbines, is therefore not feasible without external supply.
• a steam turbine typically includes a vaned rotatably mounted rotor disposed within a casing shell.
• a vane is usually held at a first location along an inside of the steam turbine house. It is usually part of a Blade which comprises a number of vanes arranged along an inner circumference on the inside of the steam turbine housing. Each vane has its blade radially inward. A vane ring at a location along the axial extent is also referred to as a vane row. Usually, a plurality of vane rows are arranged one behind the other.
• the rotatably mounted in the steam turbine steam turbine rotors are subjected to thermal stress during operation.
• the development and production of a steam turbine rotor is both expensive and time consuming.
• the steam turbine rotors are considered the most stressed and expensive components of a steam turbine. This increasingly applies to high steam turbines.
• a characteristic of the steam turbine rotor is that they do not have any significant heat sink. Therefore, the cooling of the blades arranged on the steam turbine rotor is difficult.
• Piston area is to be understood as the area of a thrust balance piston.
• the thrust balance piston acts in a steam turbine such that a force caused by the working medium force is formed on the rotor in one direction counter-force in the opposite direction.
• Rotor through which a cooling medium can flow, carried out.
• a disadvantage here is felt that between two ver ⁇ different expansion sections no controllable bypass can be formed from ⁇ .
• problems in on-site operation are possible.
• the object of the invention is therefore to provide a steam turbine, which can be operated at high steam temperatures.
• a steam turbine comprising a housing and a rotor, wherein the housing has a fürfuh ⁇ tion for carrying out external Kuhlmedium, wherein the rotor is at least partially hollow, with a Supply line for passing the external Kuhlmediums is provided in the cavity of the rotor.
• Cooling medium is guided to a suitable location of the rotor.
• the cavity is used as a suitable location.
• the cavity is expediently attached to the places which are exposed to a high thermal load.
• the hitherto known method in which the external cooling medium is flowed into the steam turbine and immediately cools thermally stressed parts such as the thrust balance piston, is therefore improved by the cooling medium is guided by the housing in the cavity of the rotor after the passage.
• the cooling steam must have a higher pressure than at the inflow, so that it can be guided into the cavity.
• An advantage of this cooling principle according to the invention is that the temperature of the cooling medium can be adjusted.
• Steam turbines are usually used at different loads. So a steam turbine at full load operation ⁇ or Operalastbet ⁇ eb example operated.
• the cooling requirements for the various load operations are different, so the requirement for the cooling of the steam turbine in part load operation is lower than in full load operation.
• the invention is advantageously developed further, if the rotor is designed such that the cooling medium via rotor Cooling lines rst from the cavity rst.
• the Kuhlmedrum first flows through external lines through the housing in the cavity of the rotor and then flows at appropriate points from the rotor back into the main flow.
• the cooling medium flows and cools the rotor from the inside.
• the outflow of Kuhlmediums from the rotor takes place at one or more downstream locations.
• the cooling medium fulfills two tasks, so to speak, on the one hand, the cooling medium cools the rotor at appropriate locations and on the other, the Kuhlmedium contributes to the efficiency in which it is fed back into the main flow and performed on the guide and moving blades work.
• the supply line is arranged in the region of a steam flow range. As a result, a suitable point for the supply line is found, since it is precisely the area of the steam inflow area which is exposed to very high thermal loads and therefore requires a preferred cooling.
• the supply line is arranged next to a thrust balance piston.
• the cooling medium before it is guided into the cavity of the rotor, to cool the thrust balance piston.
• the thrust balance piston is subject to high thermal loads, especially at full load.
• the rotor has rotor blades which are designed such that the cooling medium can flow through the rotor blades.
• This provides the advantage that in addition to the rotor and the blades can be cooled.
• it is preferred to use the film cooling of the rotor blades known from gas turbine technology. In this way, the blade foot or can be cooled effectively at ⁇ particular thermally stressed regions of the rotor.
• the rotor is made of disk rotors and braced with a tie rod.
• the disk rotor is formed with a toothing for transmitting a torque.
• the rotor made of different materials can be formed from ⁇ . It is conceivable, for example, that a disk runner, which is exposed to lower thermal loads than a disk runner, which is exposed to high thermal stress, is performed with a material which is kos ⁇ ten redesigner and yet withstand the thermal loads.
• the toothing is designed such that the cooling medium can flow between two adjacent disk rotors.
• the toothing is formed such that the toothing fürt ⁇ tts- openings.
• channels can be provided in the so-called Hirth toothing. Through these channels, the cooling medium is strombar.
• FIG. 2 shows a cross section of a rotor of a steam turbine and a part of a housing
• 3 shows a cross section through a rotor
• FIG. 5 shows a cross section of a toothing in an alternative embodiment.
• FIG. 1 shows a section through a high-pressure partial turbine 1 according to the prior art.
• the high-pressure partial turbine 1 as an embodiment of a steam turbine comprises an outer housing 2 and an inner housing 3 arranged therein.
• a rotor 5 is rotatably mounted about a rotation axis 6.
• the rotor 5 comprises blades 7 arranged in grooves on a surface of the rotor 5.
• the inner housing 3 has guide vanes 8 arranged in grooves on its inner surface.
• the guide 8 and blades 7 are arranged such that in a flow direction 13, a flow channel 9 is formed.
• the high-pressure partial turbine 1 has a flow-in region 10, through which live steam flows into the high-pressure partial turbine 1 during operation.
• the live steam may have steam parameters above 300 bar and above 620 ° C.
• the live steam relaxing in the flow direction 13 alternately flows past the guide vanes 8 and rotor blades 7, relaxes and cools down.
• the steam loses in this case to internal energy, which is converted into rotational ⁇ energy of the rotor 5.
• the rotation of the rotor 5 finally drives a generator, not shown, for power supply.
• the high pressure part turbine 1 may drive other plant components other than a generator, such as a compressor, a propeller, or the like.
• the steam flows through the flow channel 9 and flows out of the high-pressure part of the turbine 1 from the outlet 33.
• the steam in this case exerts a force action ⁇ 11 in the direction of flow.
• FIG 2 a section of a steam turbine 1 is shown.
• the steam turbine has a housing 39.
• the housing 39 could be a réellegehause 3 or 2.05.gehause.
• the steam turbine according to FIG. 2 is designed in such a way that the housing 39 has a passage 20 for the passage of external cooling medium 21.
• the rotor 5 is in this case at least partially hollow.
• the rotor 5 therefore has a cavity 22.
• the rotor 5 has a supply line 23 for passing through the external cooling medium 21.
• the cooling medium 21 is guided via the passage 20 and the supply line 23 into the cavity 22.
• a first cooling effect of the cooling medium 21 is already achieved in the housing 39 in the region of the passage 20.
• the passage 20 is arranged in the vicinity of the inflow region 10.
• the inflow region 10 is particularly thermally stressed, since there flows in the live steam.
• the cooling medium is guided by the passage 20 to the supply line 23 and flows into the cavity 22.
• the cooling medium 21 must in this case have a corresponding pressure.
• the supply line 23 can be made by radial bores. Other embodiments such as inclined leads are conceivable. For the sake of clarity, neither guide 8 nor moving blades 7 are shown in FIG.
• the rotor 5 is designed such that the cooling medium 21 can be flowed out of the cavity 22 via rotor cooling lines 24.
• the supply line 23 can be arranged next to a compensating piston 4. Since the balance piston is particularly thermally stressed, this would be an advantageous embodiment.
• the cooling medium 21 flowing out of the rotor cooling duct 24 mixes with the working medium coming from the inflow region 10, which as a rule is a vapor.
• the cooling medium 21 cools, inter alia, from the supply line 23, the rotor 5 on an inner surface 25 of the cavity 22nd
• the steam turbine 1 can be designed in such a way that the rotor 5 has blades 7, which are designed in such a way that the cooling medium 21 can flow through the blade 7. As a result, the rotor blade 7 are cooled.
• the rotor blades 7 in this case have individual fürerieso réelleen.
• the blades 7 are cooled by the so-called film cooling.
• the film cooling is known from gas turbine technology.
• the rotor 5 is formed such that the blade root, the balance piston 4 or other kriti ⁇ cal areas that are thermally loaded, are cool.
• the m rotor 2 shown m FIG 2 is welded to a weld 26 of two sub-rotors 27, 28.
• a rotor is shown, which is constructed from three disk rotors 29, 30, 31.
• the rotor may in alternative forms Ausfuh approximately ⁇ are remote from only two Scheibenlau-. 5
• the three disk runners 29, 30, 31 are clamped firmly together by means of a tie rod 32.
• the tie rod at its ends a thread 34.
• a movement of the tie rod 32 takes place in the rotation axis direction, which leads to the fact that the three disc rotors 29, 30, 31 are printed together.
• the disk runners 29, 30, 31 at their points of contact 35, 36 have a toothing for transmitting a torque.
• the toothing can be designed as a Hirth, rectangular or trapezoidal toothing.
• the toothing 37, 38 is designed as a triangular toothing 37.
• the toothing 37 is designed such that a supply line 23 is formed. Through the supply line 23, the cooling medium 21 is strombar.
• FIG. 5 shows an alternative embodiment of a toothing 37, 38 is shown.
• the toothing 38 shown in FIG. 5 is designed as a trapezoid toothing 38.
• the trapezoidal toothing 38 is designed in such a way that supply lines 23 are formed, through which the cooling medium 21 can flow.

Landscapes

• Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• General Engineering & Computer Science (AREA)
• Turbine Rotor Nozzle Sealing (AREA)
• Details And Applications Of Rotary Liquid Pumps (AREA)
• Structures Of Non-Positive Displacement Pumps (AREA)
• Rotary Pumps (AREA)

Priority Applications (1)

Applications Claiming Priority (3)

Publications (2)

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ID=37872372

Family Applications (2)

Family Applications Before (1)

Country Status (5)

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Family Cites Families (10)

• 2006
  • 2006-10-09 EP EP06021139A patent/EP1911933A1/fr not_active Withdrawn
• 2007
  • 2007-09-25 WO PCT/EP2007/060141 patent/WO2008043663A1/fr active Application Filing
  • 2007-09-25 AT AT07803598T patent/ATE458125T1/de active
  • 2007-09-25 EP EP07803598A patent/EP2078137B1/fr not_active Not-in-force
  • 2007-09-25 JP JP2009530848A patent/JP4990365B2/ja not_active Expired - Fee Related
  • 2007-09-25 DE DE502007002883T patent/DE502007002883D1/de active Active

Non-Patent Citations (1)

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