WO1998019081A1 - Arbre de transmission et transmission pour vitesses de rotation elevees - Google Patents

Arbre de transmission et transmission pour vitesses de rotation elevees Download PDF

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Publication number
WO1998019081A1
WO1998019081A1 PCT/DE1997/002445 DE9702445W WO9819081A1 WO 1998019081 A1 WO1998019081 A1 WO 1998019081A1 DE 9702445 W DE9702445 W DE 9702445W WO 9819081 A1 WO9819081 A1 WO 9819081A1
Authority
WO
WIPO (PCT)
Prior art keywords
shaft
end part
transmission
main axis
gear shaft
Prior art date
Application number
PCT/DE1997/002445
Other languages
German (de)
English (en)
Inventor
Bernard Becker
Bernhard Walter
Original Assignee
Siemens Aktiengesellschaft
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 Aktiengesellschaft filed Critical Siemens Aktiengesellschaft
Publication of WO1998019081A1 publication Critical patent/WO1998019081A1/fr

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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
    • F01D15/00—Adaptations of machines or engines for special use; Combinations of engines with devices driven thereby
    • F01D15/12—Combinations with mechanical gearing
    • 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
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
    • F16H55/02—Toothed members; Worms
    • F16H55/12—Toothed members; Worms with body or rim assembled out of detachable parts

Definitions

  • the invention relates to a transmission shaft for high rotational speeds and a transmission for transmitting the rotation of a turbine to a generator with a first transmission shaft for high rotational speeds and with a second transmission shaft, which are interlocked with one another via gear teeth oriented essentially parallel to the main axis.
  • a shaft is described, which is composed of several interconnectable washers.
  • Each ring disk here has a plurality of through bores distributed over the circumference and a plurality of threaded bores.
  • each wave washer can hereby be individually attached to the adjacent wave washer.
  • three wave washers are combined into a package and fastened to one another by a plurality of fastening screws. Staggered in each case, a next fastening screw engages in a package of wave washers further below.
  • the preferred area of use for such a shaft composed of a plurality of shaft washers is the formation of filter packets of pressure rotary filters. It is essential here that a medium enters the inside of the shaft from an area outside the shaft and from there can again be guided outside into a corresponding vessel. This results in the need to design the shaft as a hollow shaft.
  • DE 38 05 775 C2 describes a built transmission shaft in which individual drive elements, in particular gearwheels, are fixed in a rotationally fixed manner on a hollow shaft.
  • the connection between the hollow shaft and a drive element takes place here by friction, the hollow shaft being plastically widened and the drive element being elastically pretensioned.
  • the drive element has at least two toothed disks of different diameters connected by a sleeve in a one-piece construction. This means that the two toothed disks are designed with the sleeve as a single, completely connected component.
  • This one-piece drive element is preferably made of a cast material, in particular malleable cast iron.
  • a transmission shaft for high speeds is used, for example, in a transmission for transmitting the rotation of a turbine to a generator.
  • a transmission for transmitting the rotation of a turbine to a generator.
  • such a transmission can have two transmission shafts which are interlocked and one of which is connected to a turbine shaft and the other to a generator shaft.
  • each gear shaft has a correspondingly large diameter, gear teeth being arranged on the outer circumference.
  • internal tensile stresses arise during the hardening process in the interior of the shaft during the manufacture of the gear shaft, which are superimposed by the transient thermal stresses at start-up and by centrifugal stresses at high speeds of rotation of the gear shaft. These tensions increase with increasing diameter of the gear shaft.
  • the object of the invention is to provide a gear shaft for high rotational speeds in which thermomechanical stresses are kept low.
  • Another object of the invention is to provide a transmission for transmitting the rotation of a turbine to a generator.
  • a gear shaft has a hollow cylindrical center part directed along a main axis has, which has on its outer circumference substantially parallel to the main axis gear teeth and adjoins the central part, a first end part which is connected to the central part with at least one tie rod.
  • a hollow, toothed middle section achieves an overall tension level which is significantly lower than that of a gear shaft made as a solid body. This enables the production of a gear shaft at a low voltage level with a large diameter, which ensures the transmission of very high power.
  • the thermomechanical load on the gear teeth is significantly lower than a critical load due to the large diameter due to the corresponding size of the gear teeth.
  • the wall thickness of the hollow cylindrical middle part can be relatively small, in particular less than 20% of the diameter, for example 10% of the diameter.
  • the diameter of the hollow cylindrical middle part can be approximately 1 m.
  • the gear teeth can have a height of 5 cm to 10 cm, for example.
  • the gear teeth can also be directed along an axis which axis is oblique to the main axis. This is encompassed by the phrase "essentially parallel to the main axis".
  • the first end part is preferably non-rotatably connected to the middle part, thereby ensuring an essentially rigid connection between the end part and the middle part in the circumferential direction even at a high rotational speed.
  • the anti-rotation device is preferably designed so that the middle part and the end part center to one another are and can expand radially independently of each other at the same time. This makes it possible to use different materials, metals or alloys which meet the respective requirements, for the middle part and the end part. As a result, the end part and the middle part can also have different temperature distributions, in particular caused by a mechanical load, without the formation of additional thermomechanical stresses.
  • the wall thickness of the hollow cylindrical middle part can be determined largely without taking into account the dimensions of the first end part and / or a second end part.
  • the expected total thermal stresses such as residual stress from the hardening process, tooth stresses, centrifugal stresses and transient thermal stresses, must be taken into account, depending on the requirements.
  • the total voltage level in the middle part which is exposed to a high thermomechanical load via the gear teeth when transmitting power to another gear shaft, can thus be determined largely independently of further power transmission parts adjoining the middle part.
  • the total voltage level is significantly reduced compared to a solid shaft gearbox. At a given speed (rotational speed) of the gear shaft, a large diameter can be achieved with little load on the gear teeth.
  • the twist-proof connection is preferably carried out via a spur tooth coupling, a serration, which is also referred to as a Hirth serration.
  • a spur tooth coupling a serration
  • rotationally symmetrical coupling elements here the middle part and the end part, can be essentially connected in a rotationally secure manner on their end faces.
  • the coupling elements can either be designed with an inclined or with a straight and inclined tooth base.
  • the interlocking teeth of a plank notch are arranged on a circle and directed radially inwards. With an outside diameter of the circle (the gear shaft) of between 600 mm and 1200 mm, 48 or 72 teeth are preferably provided.
  • the tooth height for a tapered tooth base is between 3.7% and 5.6% of the diameter.
  • spur tooth coupling achieves a self-centering, torsionally rigid connection of rotating machine parts. With a spur tooth coupling, a non-positive and positive transmission of a torque takes place.
  • straight spur gearing or curved spur gearing can also be used.
  • a twist-proof connection can also be established, for example, using radial bolts.
  • a radial pin engages e.g. into corresponding, mutually associated radial grooves of both the middle part and the end part.
  • Such a radial bolt can engage in the central part on the inner circumference or on the outer circumference and is secured there if necessary against falling out.
  • a second end part is preferably arranged on the middle part, so that the middle part is held against rotation between the first and the second end part.
  • the second end part can be connected to the middle part in a rotationally secure manner via a spur tooth coupling or, for example, by radial bolts. It is also possible to connect the second end part to the central part so that it cannot rotate by forging.
  • the first end part and the second end part each have essentially the same diameter as the central part in the area of the non-rotatable connection, but at a distance from the central part a significantly smaller diameter.
  • the first end part and the second end part can each be stored in a bearing with a small diameter spaced apart from the central part. Even with a large diameter of the middle part and thus corresponding power transmission of the gear shaft, compact bearings can therefore be used for mounting the gear shaft.
  • First End part and second end part preferably taper in the axial direction with increasing distance from the middle part.
  • the tie rod is preferably arranged centrally to the main axis. It is preferably firmly connected to the second end part, in particular by a thread, and has a thread in the region of the first end part. Via a clamping nut engaging in the thread, a firm bracing between the first end part and the middle part and thus a twist-proof connection can be established. If the middle part and the second end part are also releasably connected to one another, a tension-proof connection between the second end part and the middle part is also achieved by tightening the clamping nut.
  • an intermediate shaft can also be arranged centrally to the main axis, which can be connected at one end to a generator or turbine shaft and at its other end to the first end part or the second end part.
  • the intermediate shaft can thus be slightly axially and possibly also radially movable relative to the central part, as a result of which different thermal expansions can be compensated for.
  • This allows the use of different materials for the intermediate shaft, the first end part and the second end part and the middle part.
  • the material for each of these parts can therefore be designed essentially independently of the materials of the other parts in accordance with the required thermomechanical properties.
  • the object directed to a transmission for transmitting the rotation (torque, power) of a turbine to a generator is achieved in that a first transmission shaft for a high rotational speed and a second transmission shaft are provided, at least the first gear shaft has a hollow cylindrical middle part directed along a main axis, the gear teeth on its outer circumference essentially parallel to the main axis and a first end part adjoining the middle part, which is connected to the middle part with at least one tie rod.
  • the first transmission shaft can be connected to the generator and the second transmission shaft to the turbine.
  • the formulation of the gear teeth essentially parallel to the main axis also includes gear teeth which are directed slightly obliquely to the main axis.
  • the gearbox converts the speed of the turbine to the required speed of the generator even when a high torque is transmitted.
  • the diameter of each transmission shaft can be larger than that of a corresponding transmission shaft made of solid material at a significantly lower level of the total thermomechanical stresses, in particular on the outer circumference. Due to the dimensioning of the middle part and the end part, which can be carried out essentially independently of one another, the transmission can have compact, structurally simple to control bearings.
  • the transmission is characterized by a low overall voltage level and by a lightweight construction.
  • a speed of a gas turbine of over 5000 rpm, e.g. 5400 rpm, a reduction to a generator speed of 3000 rpm (corresponding to 50 Hz) or 3600 rpm (corresponding to 60 Hz) is guaranteed even with large outputs of over 100 MW.
  • the first gear shaft has a significantly larger diameter than the second gear shaft. Due to the smaller diameter of the second gear shaft, it can also be made from a solid material.
  • Each gear shaft preferably has two toothed axially spaced middle parts, the gear teeth being directed along an axis which is parallel to the main axis or at an acute angle with the main axis the gear shaft forms.
  • the gear shaft is therefore straight, helical or double helical.
  • the two middle parts form a single middle part, they directly adjoin one another without an assembly or machining gap.
  • a twist-proof connection between the two directly adjoining middle parts is preferably made by a spur gear coupling, a face serration or other construction elements already described above.
  • the middle parts are therefore arranged concentrically and centered against each other.
  • a circumferential groove that was previously required between the toothed middle parts in the case of double helical gear shafts as a tool outlet can be omitted here.
  • FIG. 4 shows a cut-away top view of a transmission between a gas turbine and a generator
  • 5 to 7 show a longitudinal section through a gear shaft with two middle parts.
  • 1 to 3 each show in a longitudinal section a gear shaft 1 comprising a central part 3 directed along a main axis 2, which is clamped between a first end part 6a and a second end part 6b.
  • the gear shaft 1 which is essentially symmetrical to the main axis, is only shown above the main axis 2 in FIGS. 1 to 3.
  • the middle part 3 On its outer circumference 4, the middle part 3 has gear teeth 5, which are each directed essentially parallel to the main axis 2. For the sake of clarity, only one gear tooth 5 is also shown.
  • a non-rotatable connection is made by a spur tooth coupling 19, in particular a serration (Hirth toothing).
  • the corresponding teeth of the respective spur tooth coupling 19 are not shown in detail.
  • FIG. 1 shows a central tie rod 7 directed along the main axis 2, which is fixed to the second one
  • End part 6b is connected and has a thread 21 projecting beyond the first end part 6a.
  • a clamping nut 20 is placed, which is in contact with the first end part 6a and braces it.
  • Middle part 3 and go into a diameter which is significantly smaller than the diameter of the middle part 3 given by the outer circumference 4. With this small diameter, they are directed as a shaft segment along the main axis 2.
  • the first end part 6a and the second end part 6b can be mounted on a corresponding respective bearing, not shown. the.
  • the second end part 6b has at its end opposite the middle part 3a a flange 18 for attachment to a shaft of a turbine 16a or a generator 16b.
  • the first end part 6a and the second end part 6b each pass at a distance from the middle part 3 into a solid shaft region of smaller diameter, in which the gear shaft 1 is supported.
  • the second end part 6b has a flange 18.
  • the middle part 3 is clamped and thus fastened between the first end part 6a and the second end part 6b by a plurality of tie rods 17.
  • These tie rods 17, of which only one is shown for the sake of clarity, are directed along the main axis 2 and from it spaced apart, preferably symmetrical. Compared to a single central tie rod 7 (see FIG. 1), these tie rods 17 each have a smaller diameter.
  • the tie rods 17 can be braced by a corresponding clamping nut 20 both in the region of the second end part 6b and in the region of the first end part 6a.
  • FIG. 3 shows a gear shaft 1, which has a plurality of tie rods 17 analogous to the exemplary embodiment according to FIG. 2. Furthermore, the transmission shaft 1 has a centrally arranged intermediate shaft 10 which extends along the main axis 2 and is preferably made of solid material. This intermediate shaft 10 is toothed in a first end region 14 via a corresponding gear coupling with the first end part 6a. In a second end region 15 assigned to the second end part 6b, it has a flange 18 for attachment to a turbine or generator shaft 16a, 16b.
  • the intermediate shaft 10 is fixed axially and radially with respect to the first end part 6a. Due to its length, the intermediate shaft 10 can compensate for height differences, for example from relative thermal expansions between the transmission and the coupled machine.
  • FIG. 1 shows a gear shaft 1, which has a plurality of tie rods 17 analogous to the exemplary embodiment according to FIG. 2. Furthermore, the transmission shaft 1 has a centrally arranged intermediate shaft 10 which extends along the main axis 2 and is
  • FIG. 4 shows a perspective top view of a transmission 8 with a first transmission shaft 1 and a second transmission shaft 11.
  • the first transmission shaft 1 is connected to a turbine shaft 16a of a gas turbine 12 via a flange 18 and the second transmission shaft 11 is also connected to a generator shaft via a flange 18 16b of a generator 13 connected.
  • Each gear shaft 1, 11 has two toothed middle parts 3a, 3b which are axially spaced apart.
  • the gear teeth 5 of each middle part 3 are oblique with respect to the
  • the gear teeth 5 of the first gear shaft 1 engage in the associated gear teeth 5 of the second gear shaft 11.
  • the two middle parts 3a, 3b of the first gear shaft 1 have a smaller diameter than the two middle parts 3a, 3b of the second gear shaft 11.
  • a respective middle part 3 is clamped non-rotatably and non-positively between a first end part 6a and a second end part 6b via a plurality of tie rods 17 analogously to the exemplary embodiment according to FIG.
  • tie rods 17 analogously to the exemplary embodiment according to FIG.
  • an embodiment of the transmission analogous to the exemplary embodiments according to FIGS. 1 and 3 is possible.
  • FIGS. 5 to 7 each show a gear shaft 1 for a gear 8 (see FIG. 4) for coupling a gas turbine 12 to a generator 13.
  • the gear shaft 1 is directed along a main axis 2 and has one consisting of two middle parts 3a, 3b Middle part 3.
  • Each middle part 3a, 3b has gear teeth 5 (represented by a dash-dotted line in FIGS. 5 to 7 below the main axis 2), which run along a respective axis which is oriented obliquely with respect to the main axis 2.
  • the gear shaft 1 thus represents a double helically toothed gear shaft.
  • the central parts 3a, 3b are secured against rotation via radial serration 19, can be moved radially and are concentrated. arranged trically to each other.
  • a second end part 6b adjoins the middle part 3b, which is connected to the middle part 3b in a rotationally secure manner.
  • the second end part 6b is in each case connected to a generator shaft 16b of a generator 13 via a flange 18.
  • the second end part 6b is also connected to the central part 3b in a manner secured against rotation by means of serration 19.
  • the middle part 3b and the second end part 6b form a unit, in particular the second end part 6b is firmly welded to the middle part 3b.
  • a first end part 6a adjoins the middle part 3a, which is also connected to the middle part 3a in a manner preventing rotation.
  • This twist-proof connection takes place, according to FIG. 5, again by means of serration 19 and in FIGS. 6 to 7, in particular by welding the middle part 3a to the first end part 6a.
  • the gear shaft 1 thus has four parts releasably connected to one another according to FIG. 5, three releasable parts according to FIG. 6 and two releasable parts according to FIG.
  • the invention is characterized by a gear shaft, which has a hollow cylindrical, central part supporting the gear teeth.
  • the central part is preferably clamped between two end parts which are toothed with the central part via a spur-tooth coupling that allows rotation and radial expansion.
  • the end parts each have a significantly smaller diameter than the diameter of the for the purpose of storage at a distance from the central part

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Gears, Cams (AREA)

Abstract

L'invention concerne un arbre (1) de transmission pour vitesses de rotation élevées, comportant une partie centrale (3) cylindrique creuse dirigée le long d'un axe principal (2). Cette partie centrale (3) porte des dentures (5) sur sa périphérie extérieure (4) et est bloquée de manière fixe avec une première partie terminale (6a) par l'intermédiaire d'une tige de tension (7, 17). L'invention concerne en outre une transmission (8) permettant de transmettre la rotation d'une turbine (12) à un générateur (13).
PCT/DE1997/002445 1996-10-30 1997-10-22 Arbre de transmission et transmission pour vitesses de rotation elevees WO1998019081A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19643883.7 1996-10-30
DE19643883 1996-10-30

Publications (1)

Publication Number Publication Date
WO1998019081A1 true WO1998019081A1 (fr) 1998-05-07

Family

ID=7809657

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/DE1997/002445 WO1998019081A1 (fr) 1996-10-30 1997-10-22 Arbre de transmission et transmission pour vitesses de rotation elevees

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WO (1) WO1998019081A1 (fr)

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2567482A (en) * 1944-02-18 1951-09-11 Avco Mfg Corp Lay shaft construction
DE1428054A1 (de) * 1963-04-08 1969-02-06 Borg Warner Einstufiger Kreiselradverdichter
DE2734747A1 (de) * 1977-08-02 1979-02-15 Daimler Benz Ag Verbindung eines keramischen turbinenrades mit einer metallischen welle
EP0028217A1 (fr) * 1979-10-25 1981-05-06 ELIN-UNION Aktiengesellschaft für elektrische Industrie Rotor pour turbomachine thermique
US4340317A (en) * 1981-05-07 1982-07-20 Northern Research & Engineering Corp. Splineless coupling means

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2567482A (en) * 1944-02-18 1951-09-11 Avco Mfg Corp Lay shaft construction
DE1428054A1 (de) * 1963-04-08 1969-02-06 Borg Warner Einstufiger Kreiselradverdichter
DE2734747A1 (de) * 1977-08-02 1979-02-15 Daimler Benz Ag Verbindung eines keramischen turbinenrades mit einer metallischen welle
EP0028217A1 (fr) * 1979-10-25 1981-05-06 ELIN-UNION Aktiengesellschaft für elektrische Industrie Rotor pour turbomachine thermique
US4340317A (en) * 1981-05-07 1982-07-20 Northern Research & Engineering Corp. Splineless coupling means

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