EP0266581B1 - Vireur pour turbomachines - Google Patents

Vireur pour turbomachines Download PDF

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Publication number
EP0266581B1
EP0266581B1 EP87114873A EP87114873A EP0266581B1 EP 0266581 B1 EP0266581 B1 EP 0266581B1 EP 87114873 A EP87114873 A EP 87114873A EP 87114873 A EP87114873 A EP 87114873A EP 0266581 B1 EP0266581 B1 EP 0266581B1
Authority
EP
European Patent Office
Prior art keywords
shaft
oil
overrunning clutch
geared motor
hydraulic
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.)
Expired - Lifetime
Application number
EP87114873A
Other languages
German (de)
English (en)
Other versions
EP0266581A1 (fr
Inventor
Heinrich Dr. Oeynhausen
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 AT87114873T priority Critical patent/ATE50825T1/de
Publication of EP0266581A1 publication Critical patent/EP0266581A1/fr
Application granted granted Critical
Publication of EP0266581B1 publication Critical patent/EP0266581B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • F01D25/34—Turning or inching gear

Definitions

  • the present invention relates to a device for rotating the shaft of a turbo set according to the preamble of claim 1, and methods for operating such a shaft rotating device.
  • DE-PS 975 646 describes a simple shaft turning device with blades driven by pressure oil and placed on a clutch, but which has the disadvantage of considerable oil consumption when starting up and during operation.
  • FR-A 1 295 544 describes a shaft rotating device fastened to the end wall of a foremost bearing, in which a laterally arranged electric motor is connected to the overrunning clutch via a worm gear. No statements are made about the possibilities for centering the shaft and overrunning clutch or about the details of the mounting of these components. Eccentric engagement of the overrunning clutch cannot easily be avoided.
  • the object of the present invention is the space-saving arrangement of a shaft rotating device in alignment with the shaft, taking into account the centering problems which occur, and the integration of this device in the oil supply systems which are anyway necessary for starting. Additional bearings should be avoided if possible.
  • the drive system is a hydraulic motor with an integrated connecting gear, a so-called hydraulic gear motor, which has become standard in the meantime.
  • a hydraulic gear motor is attached to the end wall of the front bearing housing with the interposition of a commercially available overrunning clutch, the overrunning clutch overcoming the shaft of the turboset via the shaft of an auxiliary unit, e.g. Via the main oil pump, which is also located in the front bearing housing, couples with the shaft of the hydraulic gear motor or separates these shafts.
  • the overrunning clutch which is the case with the commercially available systems used, only permits a certain amount of play between the two concentric clutch rings to be coupled, for correct functioning.
  • the outer ring of a commercially available overrunning clutch is usually supported by roller bearings
  • the shaft of the auxiliary unit which is to be connected to the inner part of an overrunning clutch, is supported by hydrodynamic bearings, which cannot be centered with the necessary tolerances when starting off and at low speeds are.
  • the invention provides that this foremost hydrodynamic bearing of the auxiliary unit, with the housing of which the shaft rotating device is firmly connected, should have a hydrostatic bearing for centering with respect to the overrunning clutch. This can be achieved by suitable design of the bearing.
  • the hydraulic geared motor is connected to the oil supply of the shaft lifting system, which is necessary anyway.
  • the shaft lifting system allows the shaft to float into the lower area of the shaft bearing by supplying it under high pressure, for example 180 bar, which only makes it possible to rotate the shaft.
  • high pressure for example 180 bar
  • the start-up process is particularly easy, since the hydraulic motor also starts when the shaft is floating.
  • an adjustable throttle can be provided, which initially allows the full pressure of the oil system to reach the hydraulic motor when the shaft breaks loose, but then prevents it from rotating too quickly. Possibly.
  • a so-called flow control valve can also be used instead of the throttle, which has the advantage that the engine speed remains approximately constant in all load conditions. With pure throttle control, the engine speed increases or decreases with changes in load.
  • An additional shut-off valve can be used to separate the shaft rotating device from the shaft lifting system, e.g. to carry out adjustment work.
  • the oil supply line of the hydraulic geared motor should be connected to the lubricating oil system of the turbo set, preferably via a ver adjustable throttle and a check valve.
  • a ver adjustable throttle and a check valve In the event of an overhaul, when the hydraulic gear motor is no longer needed, it may be necessary, as is known per se, to keep the hydraulic motor turning slowly in order to prevent bearing damage. This can be achieved by connecting to the lubricating oil system, which has only a low pressure of, for example, 2 bar.
  • the idle speed can be preselected by suitable setting of a throttle.
  • the additional hydrostatic bearing of the foremost bearing which serves for centering, can generally be fed from the oil supply of the shaft lifting system, without extensive further changes being required.
  • the foremost bearing is then hydrostatically centered, which ensures that the overrunning clutch functions properly.
  • Claims 8 and 9 relate to methods for operating the previously described device with its various configurations.
  • the simplicity of the processes to be triggered enables the start-up process to be automated without any problems, since the function of the hydraulic geared motor depends entirely on the other systems that are already required and does not require any special control measures.
  • Fig. 1 the connection of a shaft rotating device to the foremost end of a shaft 1 of a turbo set is shown in a longitudinal axial section.
  • the foremost unit on the shaft assembly of the turbo set is the main oil pump 2, the outlines of which are indicated.
  • the foremost bearing 3 of the shaft 1 is a bearing of the main oil pump 2, but this is not of critical importance for the principle of the invention.
  • This foremost bearing 3 of the shaft 1 like the other bearings, is provided with an oil inlet 5, so that hydrodynamic lubrication of the shaft is possible by feeding oil into the bearing part 3a.
  • this bearing is provided with an additional bearing part 3b and an oil feed 4, which serve for hydrostatic centering.
  • the inner ring 6 of the overrunning clutch is fastened, preferably screwed tight with a nut 9.
  • the outer ring 7 of the overrunning clutch can be connected to the inner ring via clamping bodies 8, the clamping bodies rotating with the inner ring 6 and swiveling in at high speeds of the inner ring 6 so that there is no wear on the outer ring 7 with the shaft 14, preferably a profile shaft , connected via a corresponding profile shaft flange 13 and a retaining ring 10, screwed in the case shown.
  • Retaining ring 10 and profile shaft flange 13 are supported by ball bearings 11 in a housing 12.
  • the housing 12 itself is connected to the housing of the foremost bearing on the shaft 1 via the bearing housing and is so attached or screwed on that relative movements between the two are not possible.
  • the hydraulic motor 16 with its integrated gear 15 is also firmly screwed to the housing 12 of the overrunning clutch, so that both are carried by the housing 12 of the overrunning clutch without additional mounting.
  • the oil supply to the hydraulic motor 16 takes place via an oil supply line 17, and the disposal via an oil drain line 18.
  • the leakage oil of the hydraulic transmission motor initially supplies the integrated transmission 15 internally and from there reaches the overrunning clutch via a leak oil outlet 19 and an oil line 20, which has an oil supply 21 inside to the profile shaft flange.
  • the profile shaft flange 13 in turn has an oil collecting collar 22, in which the incoming oil is collected under the influence of gravity and is fed through oil drain holes 23 to the clamping bodies 8 and the ball bearings 11 until it reaches an outlet, not shown.
  • Overrunning clutches which can be used in the present case, are relatively sensitive to eccentricities of inner ring 6 and outer ring 7.
  • a clutch used in tests switched perfectly up to eccentricities between outer and inner ring of 0.25 mm (concentricity deviation 0.5 mm) . Since manufacturing tolerances of parts 3, 2, 12, 11 and 10 must be taken into account, the actual eccentricity must always be less than about half of the bearing clearance between 1 and 3. On the other hand, this also prevents bearing damage caused by eccentric clutch engagement.
  • the max. Bearing clearance is limited to 0.4 mm due to the increasing oil consumption.
  • a hydrostatic, self-centering bearing 3b additionally integrated in the foremost bearing 3 can center the shaft end with the inner ring 6 of the overrunning clutch so well that no eccentricities above the tolerance limit occur with normal bearing wear. Since the entire shaft rotating device otherwise fully follows all movements of the front bearing housing, further factors need not be taken into account.
  • Fig. 2 shows the integration of the shaft turning device according to the invention in the existing oil systems.
  • the oil supply 30 of the shaft lifting system which has, for example, a pressure of about 180 bar, feeds on the one hand the feed lines 31, 32 to the individual bearings of the shaft 1 and on the other hand the oil feed line 33, 17 to the hydraulic motor 16 Adjust the distribution of the oil quantities between the pump bearing and the hydraulic motor, with the full pressure reaching the hydraulic motor when starting.
  • a pressure measuring device 35 and a shut-off valve 36 for shutting off the hydraulic motor can be provided.
  • the oil supply line 17 of the hydraulic motor can also be connected to the lubricating oil circuit 38 of the turboset via a check valve 40 and an adjustable throttle 39, which, for example, has a pressure of approximately 2 bar.
  • the check valve 40 After switching off the oil supply 30 of the shaft lifting system, the check valve 40 then opens and supplies the hydraulic motor 16 with 01 under low pressure, which causes slow rotation to avoid damage to the bearings.
  • Hydraulic geared motor and overrunning clutch can be commercially available components, whereby for different torques differently strong, but otherwise identical hydraulic motors with corresponding overrunning clutches can be used. It is relatively easy to replace the hydraulic motor while the shaft is running, and retrofitting to the system with existing turbo sets is only possible with little effort.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Control Of Positive-Displacement Air Blowers (AREA)

Claims (9)

1. Dispositif-vireur pour l'arbre (1) d'une turbomachine au moyen d'un motoréducteur hydrostatique (15, 16) avec interposition d'une roue libre (6, 7, 8, 9, 10, 11, 12), l'arbre étant monté dans plusieurs paliers hydrodynamiques qui présentent de préférence également des admissions d'huile d'un système de soulèvement d'arbre, caractérisé en ce que le motoréducteur hydrostatique (15, 16) et la roue d'arbre (6, 7, 8, 9, 10, 11, 12) sont fixés, en alignement avec l'arbre (1), sur la face frontale du palier (3) situé le plus en avant de l'arbre (1), que la roue libre (6, 7, 8, 9, 10, 11, 12) est montée, en outre, sur des roulements (11) et le palier (3) le plus en avant de l'arbre (1) présente un dispositif de palier hydrostatique supplémentaire (3b, 4) pour le centrage par rapport à la roue libre (6, 7, 8, 9, 10, 11, 12).
2. Dispositif selon la revendication 1, caractérisé en ce que la conduite d'arrivée d'huile (17) du motoréducteur hydrostatique (15, 16) est en liaison (33) avec l'alimentation en huile (30) du système de soulèvement d'arbre, de préférence par l'intermédiaire d'un étranglement réglable (37) et d'un robine d'arrêt (36).
3. Dispositif selon la revendication 1 ou 2, caractérisé en ce que la conduite d'arrivée d'huile (17) du motoréducteur hydrostatique (15, 16) est en liaison avec le système d'huile de graissage (38), de préférence par l'intermédiaire d'un étrangleur réglable (39) et d'une soupape antiretour (40).
4. Dispositif selon la revendication 1, 2 ou 3, caractérisé en ce que le dispositif de palier hydrostatique supplémentaire (3b, 4) est en liaison directe avec l'alimentation en huile (30) du système de soulèvement d'arbre.
5. Dispositif selon une des revendications précédentes, caractérisé en ce que la sortie d'huile de fuite (19) du motoréducteur hydrostatique (15, 16) est en liaison avec une arrivée d'huile (21) de la roue libre (6, 7, 8, 9, 10, 11, 12).
6. Dispositif selon une des revendications précédentes, caractérisé en ce que la roue libre (6, 7, 8, 9, 10, 11, 12) présente une bague intérieure (6) fixée sur l'arbre (1) de la turbomachine et une bague extérieure (7) montée extérieurement sur des billes (11) dans un carter (12) et qui est reliée par une bride d'arbre cannelée (13) à l'arbre cannelé (14) du motoréducteur hydrostatique (15, 16), des pièces de serrage (8) reliant la bague extérieure (7) de façon détachable à la bague intérieure (6) jusqu'au dépassement de la vitesse de la roue libre.
7. Dispositif selon la revendication 6, caractérisé en ce que la bride d'arbre profilée (13) présente un collet collecteur d'huile (22) pour recueillir de l'huile provenant de l'arrivée d'huile (21), des perçages (23) étant prévus pour l'écoulement de l'huile en direction des pièces de serrage (8) et du roulement à billes (11).
8. Procédé de virage d'un arbre (1) d'une turbomachine monté dans plusieurs paliers hydrodynamiques, au moyen d'un motoréducteur hydrostatique (15, 16), avec interposition d'une roue libre (6, 7, 8, 9, 10, 11, 12), lesquels sont fixés, en alignement avec l'arbre (1), sur la face frontale du palier (3) situé le plus à l'avant de l'arbre (1), la roue libre (6, 7, 8, 9, 10, 11, 12) étant montée sur des roulements (11) et le palier (3) au bout de l'arbre (1) présentant un dispositif de palier hydrostatique supplémentaire (3b, 4) pour le centrage par centrage par rapport à la roue libre (6, 7, 8, 9, 10, 11, 12), avec prévision, en plus, d'un système de soulèvement d'arbre avec une alimentation en huile (30) qui est en liaison (33) avec la conduite d'arrivée d'huile (17) du motoréducteur hydrostatique (15, 16), caractérisé en ce que le motoréducteur hydrostatique (15, 16) est alimenté en même temps que le système de soulèvement d'arbre à partir de l'alimentation en huile (30) de ce système, de préférence à travers un étranglement réglable (37), et que le palier (3) d'arbre (1) voisin de la roue libre (6, 7, 8, 9, 10, 11, 12) est centré, par rapport à la roue libre, par une injection d'huile supplémentaire pour le montage rotatif par voie hydrostatique, de préférence à partir de l'alimentation en huile (30) du système de soulèvement d'arbre.
9. Procédé selon la revendication 8, caractérisé en ce que, pour éviter l'endommagement des paliers, le motoréducteur hydrostatique (15, 16) n'est pas arrêté complètement en cas de dépassement de la vitesse de la roue libre, mais continue à être tourné lentement, sous basse pression, par le raccordement au système d'huile de graissage (38).
EP87114873A 1986-10-23 1987-10-12 Vireur pour turbomachines Expired - Lifetime EP0266581B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT87114873T ATE50825T1 (de) 1986-10-23 1987-10-12 Wellendrehvorrichtung fuer turbosaetze und verfahren zu ihrem betrieb.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3636115 1986-10-23
DE19863636115 DE3636115A1 (de) 1986-10-23 1986-10-23 Wellendrehvorrichtung fuer turbosaetze und verfahren zu ihrem betrieb

Publications (2)

Publication Number Publication Date
EP0266581A1 EP0266581A1 (fr) 1988-05-11
EP0266581B1 true EP0266581B1 (fr) 1990-03-07

Family

ID=6312338

Family Applications (1)

Application Number Title Priority Date Filing Date
EP87114873A Expired - Lifetime EP0266581B1 (fr) 1986-10-23 1987-10-12 Vireur pour turbomachines

Country Status (4)

Country Link
EP (1) EP0266581B1 (fr)
AT (1) ATE50825T1 (fr)
DE (2) DE3636115A1 (fr)
IN (1) IN167380B (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
RU2397344C1 (ru) * 2009-01-11 2010-08-20 Государственное образовательное учреждение высшего профессионального образования "Тюменский государственный нефтегазовый университет" Валоповоротное и пусковое устройство газотурбинной установки

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3723385A1 (de) * 1987-07-15 1989-01-26 Siemens Ag Wellendrehvorrichtung mit hydromechanischer ueberholkupplung
RU2135783C1 (ru) * 1997-04-30 1999-08-27 Акционерное общество открытого типа "Ленинградский Металлический завод" Валоповоротное устройство
EP2757230A1 (fr) 2013-01-16 2014-07-23 Alstom Technology Ltd Procédé pour la rotation d'un rotor de turbomachine et appareil de rotation pour appliquer ce procédé
CN107725126A (zh) * 2017-08-23 2018-02-23 佛山市轩宸机电设备有限公司 一种汽轮机电磁式液压盘车

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1295544A (fr) * 1961-04-28 1962-06-08 Alsacienne Constr Meca Dispositif de virage pour le lancement de gros rotors de machines
FR1341662A (fr) * 1962-09-20 1963-11-02 Rateau Soc Dispositif de virage pour turbines à vapeur et machines similaires
DE2627032A1 (de) * 1976-06-16 1977-12-29 Kraftwerk Union Ag Anordnung zur druckoelversorgung von wellendrehvorrichtungen
CH622061A5 (fr) * 1977-06-24 1981-03-13 Bbc Brown Boveri & Cie

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
RU2397344C1 (ru) * 2009-01-11 2010-08-20 Государственное образовательное учреждение высшего профессионального образования "Тюменский государственный нефтегазовый университет" Валоповоротное и пусковое устройство газотурбинной установки

Also Published As

Publication number Publication date
EP0266581A1 (fr) 1988-05-11
IN167380B (fr) 1990-10-20
ATE50825T1 (de) 1990-03-15
DE3761835D1 (de) 1990-04-12
DE3636115A1 (de) 1988-04-28

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