EP3219911A1 - Rotor d'une turbine a gaz comprenant des disques rotoriques visses - Google Patents

Rotor d'une turbine a gaz comprenant des disques rotoriques visses Download PDF

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Publication number
EP3219911A1
EP3219911A1 EP16160875.7A EP16160875A EP3219911A1 EP 3219911 A1 EP3219911 A1 EP 3219911A1 EP 16160875 A EP16160875 A EP 16160875A EP 3219911 A1 EP3219911 A1 EP 3219911A1
Authority
EP
European Patent Office
Prior art keywords
rotor
fastening
disks
rotor according
spur
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Withdrawn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
EP16160875.7A
Other languages
German (de)
English (en)
Inventor
Karsten Kolk
Peter Kury
Dirk Springborn
Vyacheslav Veitsman
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
Original Assignee
Siemens AG
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 filed Critical Siemens AG
Priority to EP16160875.7A priority Critical patent/EP3219911A1/fr
Publication of EP3219911A1 publication Critical patent/EP3219911A1/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Withdrawn legal-status Critical Current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
    • 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
    • F01D5/06—Rotors for more than one axial stage, e.g. of drum or multiple disc type; Details thereof, e.g. shafts, shaft connections
    • F01D5/066—Connecting means for joining rotor-discs or rotor-elements together, e.g. by a central bolt, by clamps
    • 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
    • F05D2260/30—Retaining components in desired mutual position
    • F05D2260/36—Retaining components in desired mutual position by a form fit connection, e.g. by interlocking
    • 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
    • F05D2260/40—Transmission of power
    • F05D2260/403—Transmission of power through the shape of the drive components
    • F05D2260/4031—Transmission of power through the shape of the drive components as in toothed gearing

Definitions

  • the invention relates to a rotor of a gas turbine, which has a compressor section, a central section and a turbine section, wherein at least in the turbine section a plurality of rotor disks are present.
  • a rotor of a gas turbine which has a compressor section, a central section and a turbine section, wherein at least in the turbine section a plurality of rotor disks are present.
  • at least two rotor disks are connected to each other by means of fastening bolts.
  • the rotor of a gas turbine usually has a compressor section, a central section and a turbine section.
  • the compressor section in this case regularly comprises in several stages successively arranged compressor blade rings.
  • the turbine section is also mapped in a known manner of several stages, wherein also in each stage, a plurality of turbine blades are arranged distributed in the circumference. It is customary here for the turbine blades to be attached interchangeably to the respective turbine stage.
  • connection of the individual turbine stages of the turbine section with each other can also take place here in different ways.
  • embodiments are also known in which a plurality of turbine disks are used, each with one or two blade rings.
  • the turbine disks must be connected to each other in such a way that both a sufficient bending stiffness of the rotor is ensured, and the torque can be transmitted from one turbine disk to the next turbine disk.
  • a turbine disk is usually provided with an annular contact shoulder in each case, in which engages a collar on the subsequently flanged turbine disk.
  • the individual turbine disks can be reliably connected to each other by means of screwing, the problem nevertheless arises in the production of the rotor that the individual turbine disks are to be centered as precisely as possible on each other and, to that extent, the tolerance between the plant shoulder and the collar is kept as low as possible. Furthermore, the transmission of the torque via frictional engagement requires a correspondingly high pressure in the screw connection of the turbine disks.
  • Object of the present invention is therefore to reduce the effort to connect the turbine disks.
  • the stated object is achieved by an embodiment according to the invention according to the teaching of claim 1.
  • the generic rotor initially serves for use in a gas turbine.
  • the rotor has a compressor section, a center section, and a turbine section.
  • At least the turbine section in this case again has at least two, advantageously a plurality, of rotor letters, wherein a plurality of rotor blades are distributed in the circumference on at least one rotor disk.
  • the compressor section is made in one piece or analogous to the turbine section also has a plurality of rotor disks is initially irrelevant. At least it is necessary for two adjacent rotor disks to have positive-locking and / or frictional torque-transmitting means on mutually facing end faces.
  • the adjacent rotor disks have a plurality of circumferentially distributed mounting holes. It is provided that the adjacent rotor disks are connected to each other by means of the mounting holes penetrating fastening bolts.
  • the adjacent rotor disks are connected to each other by means of the mounting holes penetrating fastening bolts.
  • two rotor disks are connected to one another by means of the fastening bolts.
  • another rotor disk is arranged without blades, wherein by means of fastening bolts these three rotor disks are screwed together at the same time.
  • the transmission of the torque between the individual bolted rotor disks is thereby improved by using an end toothing between the bolted rotor letters as the torque transmission means.
  • the spur toothing is executed in a particularly advantageous manner such that it causes a centering of the rotor disks to one another.
  • a Hirth toothing can be used in a particularly advantageous manner. By using the Hirth toothing, a direct centering of the rotor disks bolted together takes place. Thus, the need for a fit between the individual rotor discs is unnecessary. Likewise, the use of Curvic gearing is possible.
  • the fastening bolts are arranged in the region of the spur toothing. This means that the fastening bolts are at least in the immediate vicinity of the spur toothing. This is the case if the distance between the spur toothing and the fastening bolts is not greater than corresponds to the radial width of the spur toothing.
  • Advantageous for this purpose is a distance which is smaller than corresponds to the diameter of the fastening bolt. It is particularly advantageous if the fastening bolts penetrate the spur toothing at least in sections.
  • the fastening bores in a rotor disk or alternately the fastening bores in both rotor disks as threaded bores into which the fastening bolts are screwed directly.
  • the mounting holes as through holes, wherein at the end of the fastening bolt either an integral screw head or a fastening nut is arranged.
  • a screw head or a fastening nut is provided in a particularly advantageous manner on the mounting hole facing side directly or indirectly has a dome-shaped collar surface , Due to the dome-shaped collar surface, an angular offset between the plane perpendicular to the axis of rotation and the axis of the fastening bolt is made possible.
  • dome-shaped collar surface surrounding the fastening bolt is arranged directly on the screw head or on the fastening nut or whether it is advantageously arranged on a washer, which consequently has a planar surface on the side facing the screw head or fastening nut Can have surface.
  • the screw head on a dome-shaped collar surface while on the other hand, a dome-shaped washer is arranged on the fastening nut.
  • the rotor disk directly or indirectly on a dome-shaped contact surface complementary to the collar surface. It is also initially irrelevant whether the dome-shaped contact surface is integrated directly surrounding the mounting hole in the surface of the rotor disk or whether in this case a washer is used in an advantageous manner, on which the contact surface is arranged. In that sense, the dome-shaped contact surface are formed both by the washer and by an integrated on the rotor disc Kalotten reduction. Insofar as the manufacturing methods allow, a Kalottensenkung is advantageous over a washer.
  • the spur gearing is arranged, initially irrelevant. At least this is to be arranged for the advantageous transmission of torque to the largest possible diameter.
  • the fastening bolts are arranged at a distance from the spur toothing for connecting the fastening flanges, it is furthermore particularly advantageous if there is a free space between the fastening flanges and the adjacent rotor disks in the region of the fastening bores. Whether this space is provided in two mounting flanges or is only arranged in a mounting flange, this is irrelevant. It is necessary that the mounting flanges adjacent to the free space opposite to the spur toothing again abut each other.
  • a heating process occurs in the rotor and thus in the rotor disks. This heating does not take place uniformly over all rotor disks, but individual rotor disks are subjected to a greater thermal expansion than adjacent rotor disks. This leads in a natural way to a shift within the spur toothing of the adjacent rotor discs together.
  • a limiting ring is used in an advantageous manner, which engages with radial play in opposing limiting grooves present in the fastening flanges. If the thermal expansion of a rotor disk, in contrast to the adjacent rotor disk, reaches an inadmissibly high value, the limiting ring is abutted on opposite flanks of the opposite limiting grooves.
  • the spur toothing does not start from an end face which is planar in the simplest case, but that at least one end face, from which the spur toothing is machined in the rotor disc, has a position changing in the axial direction.
  • the end face corresponds to a circumferential around the rotor axis waveform.
  • the mounting holes are arranged in a direction away from the opposite rotor disk trough the front side, while the intermediate peaks of the front side are arranged at the greatest distance between two mounting holes.
  • the tooth height of the spur toothing is advantageously carried out in accordance with the spur toothing in a planar end face, only just starting from the wave-shaped end face. That in the non-bolted state, the spur gear is in the range of the greatest distance between the mounting holes, while with increasing approach to the mounting holes, an increasing gap occurs within the spur gear teeth.
  • the rotor disc opposite a machining by milling or grinding by means of a revolving eccentric or other actuating means in the direction of the machining tool during rotation of the rotor disc at the same time according to the waveform of the front side is raised and lowered by the amount required to adjust the position of the teeth.
  • the fastening nut has a bearing ring on the side facing the contact surface, which has an enlarged inner diameter relative to the fastening bore. This means that the fastening nut rests only on the outer periphery on the contact surface. In the case of a convexly curved contact surface, this leads to the effect that expansion of the fastening nut takes place on the side facing the contact surface, whereby the otherwise highly loaded thread near the contact surface is relieved.
  • the newly created embodiment makes it possible to use a proven screwing of the individual rotor disks and yet to accomplish a problem-free structure of a rotor without major effort with respect to the centering of the individual rotor disks to each other by an advantageous self-centering spur gearing.
  • Farther is achieved by the direct screwing of the rotor disks by means arranged in the region of the spur gearing mounting bolts best possible load transfer both in terms of torque to be transmitted as well as with respect to a bending load of the rotor.
  • FIG. 1 By way of example, the screw connection of rotor disks 01 of a rotor of a gas turbine is outlined. In the following FIG. 2 the example turns off FIG. 1 shown in perspective view.
  • the rotor has at least two rotor disks 01, which each have a plurality of circumferentially distributed blades, which are fastened to the blade carrier portion 03.
  • the gear section 04 Following the blade carrier section 03 is the gear section 04, which 04 establishes the connection between the individual rotor disks 01 and the torque is transmitted via the 04.
  • the stabilizing section 05 connects, which 05 is to prevent deformation, in particular bending or torsion of the individual rotor disks 01.
  • Each rotor disk 01 has on both sides a front side 07 facing the following rotor disk 01.
  • a Hirth serration 08 is arranged in this embodiment in each case (being omitted for reasons of simplified illustration on the representation of the Hirth serration on the right and left end).
  • the Hirth serration 08 causes both a centering of each successive rotor disks 01 to each other and also the torque from one rotor disk 01 to the subsequent rotor disk 01 can be transmitted.
  • each rotor disk has an attachment flange 10 which extends outward on the end face 07. In these 10 are distributed in the circumference, a plurality of mounting holes 11 through which 11 each a fastening bolt 15 is inserted. By means of fastening nuts 20 a screwing of the rotor disks 01 takes place.
  • FIGS. 3 and 4 Now show a first embodiment of the realization of the screw connection between the individual rotor disks 01st
  • FIG. 3 shows here in detail the adjacent rotor disks 01 with the respective mounting flange 10, in which the mounting hole 10 is 10.
  • Through the mounting hole 11 in the mounting flange 10 through the fastening bolt 15 extends, wherein at both ends of the fastening bolt 15 each fastening nuts 20 are arranged.
  • Hirth serration 08 is between the respective mounting flange 10 and the fastening nuts 20 is a dome-shaped washer 14 and a dome-shaped washer 22.
  • a concave washer 22a has a concave collar surface 21a on the left-hand side. Complementary to this is the convex contact surface 13b on the convex washer 14b.
  • the analogous example is shown with the concave washer 14a, which has the concave bearing surface 13a, for which purpose the convex washer 22b with the convex collar surface 21b is arranged below the fastening nut 20.
  • FIGS. 5 and 6 becomes analogous to FIGS. 3, 4 an alternative embodiment for screwing the rotor disks 01 sketched.
  • a fastening bolt 16 is used in this case, which 16 is provided with a convex screw head 17.
  • the fastening nut 20 with the convex washer 22b is located at the opposite end.
  • the fastening bolt 16 in this case has on the convex screw head 17 on the convex collar surface 21b.
  • the mounting flange 10 directly by means of a concave Kalottensenkung 12, the concave contact surface 13 a.
  • the fastening nut 20 is used with the convex washer 22b analogous to the previous embodiment.
  • FIGS. 7 and 8 a further embodiment of a rotor with rotor disks 31 screwed together is sketched in section or in perspective analogous to the previous views.
  • These rotor disks initially correspond to the previous embodiment with a Hirth toothing 33 for transmitting torque between the two rotor disks 31.
  • the rotor disks 31 are connected in the same way by a fastening bolt in the region of the fastening flanges 32.
  • This 35 is limited to the outer periphery by a support ring 34, at the 34, the mounting flanges 32 in turn abut each other. Now takes the attachment of the rotor disks 31 to each other, leads in an obvious way, the clamping of the mounting bolt to a support of the mounting rings 34 and the Hirth gear 33 to each other. Thus, a better pressure in the Hirth serration 33 can be achieved.
  • FIG. 9 a further embodiment of a rotor according to the invention with the rotor disks 41 is sketched.
  • these in the region of the Hirth toothing 43, these have a delimiting ring 45, which engages in the opposite rotor disks 41 in each case into a delimiting groove 44.
  • the limiting ring 45 is mounted with radial clearance in the Begrenzungsnut 44. If thermal expansions occur in a rotor disk 41 in contrast to the adjacent rotor disk 41, then the limiting ring 45 leads to a limitation of the thermal expansion of the rotor disks 41 relative to one another.
  • FIG. 10 a particular embodiment of an advantageous fastening nut 25 is outlined.
  • the fastening nut 25 does not rest on the support surface 13b over its full area, but rather only with a support ring 26.
  • This support ring 26 has a relation to the fastening bore 11 enlarged inner diameter, so that a reduced outer annular bearing surface is formed.
  • the contact surface 13b on the rotor disk 04 has an outwardly convex convex shape.
  • the annular bearing surface 26 initially leads generally due to the increased inner diameter and in particular due to the convex shape of the contact surface 13b to a widening of the fastening nut 25 at the end of the fastening nut 25 facing the contact surface 13b in turn leads to a relief of the thread in the region of the contact surface 13b, so that a more uniform transmission of the tensile force over the entire length of the thread in the fastening nut 25 is achieved.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Turbine Rotor Nozzle Sealing (AREA)
EP16160875.7A 2016-03-17 2016-03-17 Rotor d'une turbine a gaz comprenant des disques rotoriques visses Withdrawn EP3219911A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP16160875.7A EP3219911A1 (fr) 2016-03-17 2016-03-17 Rotor d'une turbine a gaz comprenant des disques rotoriques visses

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP16160875.7A EP3219911A1 (fr) 2016-03-17 2016-03-17 Rotor d'une turbine a gaz comprenant des disques rotoriques visses

Publications (1)

Publication Number Publication Date
EP3219911A1 true EP3219911A1 (fr) 2017-09-20

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EP16160875.7A Withdrawn EP3219911A1 (fr) 2016-03-17 2016-03-17 Rotor d'une turbine a gaz comprenant des disques rotoriques visses

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EP (1) EP3219911A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3470625A1 (fr) * 2017-10-13 2019-04-17 Doosan Heavy Industries & Construction Co., Ltd Ensemble de disque de rotor pour turbine à gaz
CN113155014A (zh) * 2021-03-15 2021-07-23 清华大学 一种周向拉杆转子拉杆动态应变测量系统
EP4343113A1 (fr) * 2022-09-23 2024-03-27 Pratt & Whitney Canada Corp. Système de fixation

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH234848A (de) * 1943-02-09 1944-10-31 Tech Studien Ag Läufer für Kreiselmaschinen mit axial nebeneinander angeordneten, durch Schrauben miteinander verbundenen Drehkörpern.
DE2507695A1 (de) * 1974-02-25 1975-08-28 Gen Electric Verfahren zum auswuchten eines gasturbinentriebwerkes
DE2844746A1 (de) * 1977-10-17 1979-04-19 Gen Electric Rotorscheibenkupplung fuer gasturbinenverdichter
JPS62165403U (fr) * 1986-04-10 1987-10-21
US20040101384A1 (en) * 2002-11-27 2004-05-27 Schilling Jan Christopher Bolting arrangement for minimizing bolt bending
WO2005093219A1 (fr) * 2004-03-17 2005-10-06 Siemens Aktiengesellschaft Turbomachine et rotor de turbomachine

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH234848A (de) * 1943-02-09 1944-10-31 Tech Studien Ag Läufer für Kreiselmaschinen mit axial nebeneinander angeordneten, durch Schrauben miteinander verbundenen Drehkörpern.
DE2507695A1 (de) * 1974-02-25 1975-08-28 Gen Electric Verfahren zum auswuchten eines gasturbinentriebwerkes
DE2844746A1 (de) * 1977-10-17 1979-04-19 Gen Electric Rotorscheibenkupplung fuer gasturbinenverdichter
JPS62165403U (fr) * 1986-04-10 1987-10-21
US20040101384A1 (en) * 2002-11-27 2004-05-27 Schilling Jan Christopher Bolting arrangement for minimizing bolt bending
WO2005093219A1 (fr) * 2004-03-17 2005-10-06 Siemens Aktiengesellschaft Turbomachine et rotor de turbomachine

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3470625A1 (fr) * 2017-10-13 2019-04-17 Doosan Heavy Industries & Construction Co., Ltd Ensemble de disque de rotor pour turbine à gaz
US11280207B2 (en) 2017-10-13 2022-03-22 Doosan Heavy Industries & Construction Co., Ltd. Rotor disk assembly for gas turbine
CN113155014A (zh) * 2021-03-15 2021-07-23 清华大学 一种周向拉杆转子拉杆动态应变测量系统
EP4343113A1 (fr) * 2022-09-23 2024-03-27 Pratt & Whitney Canada Corp. Système de fixation

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