EP0042469B1 - Turbomachine, particularly hot gas turbine, in which the stator is adjustable in height for continuously influencing the gap of the labyrinth sealing - Google Patents

Turbomachine, particularly hot gas turbine, in which the stator is adjustable in height for continuously influencing the gap of the labyrinth sealing Download PDF

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Publication number
EP0042469B1
EP0042469B1 EP81101816A EP81101816A EP0042469B1 EP 0042469 B1 EP0042469 B1 EP 0042469B1 EP 81101816 A EP81101816 A EP 81101816A EP 81101816 A EP81101816 A EP 81101816A EP 0042469 B1 EP0042469 B1 EP 0042469B1
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EP
European Patent Office
Prior art keywords
pressure
housing
rotor shaft
support
actuated
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
Application number
EP81101816A
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German (de)
French (fr)
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EP0042469A1 (en
Inventor
Edmund Owsianny
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MAN AG
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MAN Maschinenfabrik Augsburg Nuernberg AG
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Priority to AT81101816T priority Critical patent/ATE8168T1/en
Publication of EP0042469A1 publication Critical patent/EP0042469A1/en
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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
    • F01D25/28—Supporting or mounting arrangements, e.g. for turbine casing
    • 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
    • F01D11/00—Preventing or minimising internal leakage of working-fluid, e.g. between stages
    • F01D11/02—Preventing or minimising internal leakage of working-fluid, e.g. between stages by non-contact sealings, e.g. of labyrinth type
    • F01D11/025—Seal clearance control; Floating assembly; Adaptation means to differential thermal dilatations
    • 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
    • F01D25/16—Arrangement of bearings; Supporting or mounting bearings in casings
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S248/00—Supports
    • Y10S248/901—Support having temperature or pressure responsive feature

Definitions

  • the invention relates to a turbomachine, in particular a hot gas turbine, in which the machine housing is mounted such that it can be adjusted in height on variable support devices with respect to the rotor shaft.
  • the problem of alignment is also based on DE-AS 2 325 642, which is concerned with facilitating and improving the relative alignment of the power turbine rotor in the power turbine housing.
  • DE-AS 2 325 642 which is concerned with facilitating and improving the relative alignment of the power turbine rotor in the power turbine housing.
  • a suspension of the turbine on two pivots and a support of the gas generator on a movable support structure are proposed.
  • a similar suspension is also shown in DE-OS 2 617 024.
  • the housing of the turbine stator is suspended in a freely stretchable manner by means of radially directed bolts on flanges of the outer housing of the engine.
  • a multi-housing or multi-part machine set for example a turbo group consisting of a helium high-temperature turbine with a compressor and a generator
  • a turbo group consisting of a helium high-temperature turbine with a compressor and a generator
  • height-adjustable and axially movable supports are arranged between the foundation and the turbo group which act on claws on the side of the turbo group and should be hydraulically or mechanically height-adjustable. At least four such height-adjustable supports are provided for each machine housing.
  • a gas or steam turbine in which the machine housing outside of the area of the inlet and outlet side rotor shaft bearings, which are supported by bearing blocks arranged on the foundation, is to be mounted in height-adjustable manner independently of these on supporting devices with respect to the rotor shaft.
  • the turbine housing is supported in an articulated manner on the frame by supporting devices in that its ends are designed as balls and are mounted in ball sockets of the housing or the frame.
  • the support devices are designed as tubular rods through which a heat or refrigerant is passed.
  • the height adjustment of the support devices is to be carried out by changing the length due to temperature, namely by heating or cooling by means of the heating or holding means passed through the tubular rods.
  • the device according to US-A-3 764 098 is used to determine and check the weight distribution of a turbine for its support. It aims at housing alignment and simultaneous weight distribution check. In this respect, this device represents an assembly aid before commissioning.
  • DE-A-2 557 805 relates to a machine set consisting of e.g. B. from a turbine, an electrical machine and a pump, the rotor of which has a radial bearing relative to the foundation at three or more points apart.
  • Two of the radial bearings are designed as centering bearings, which determine the position of the rotor relative to the foundation men, while the other radial bearings are designed as radially displaceable bearings by means of an actuator.
  • the invention has for its object to provide an embodiment of the storage for turbomachines, in particular hot gas turbines that are subject to high thermal loads, which allows the problems described above to be met in a satisfactory manner.
  • the invention therefore relates to such a turbomachine, in particular a hot gas turbine, in which the machine housing is mounted outside of the region of the rotor shaft bearings on the inlet and outlet side, which are supported by means of bearing blocks arranged on the foundation, and are height-adjustable independently of these on variable support devices with respect to the rotor shaft.
  • the support device is attached in the region of the rotor shaft bearing and is designed as volume-variable pressure-actuated cushions such that the machine housing is connected to the foundation via crossbeams is height-adjustable by means of support sleeves supported on pressure-actuated pads, the pressure-actuated pads being arranged in ring grooves formed between the support sleeves and the support sleeves formed on studs with play, and that for automatic continuous influencing of the labyrinth seal play of the turbomachine, measurement sensors are assigned to each measurement sensor via control signal lines
  • the positioner is connected, which controls the electrohydraulic transducers assigned to the inlet and outlet sides via control lines and thereby the feed hr or the discharge of pressure medium via the lines to or from the annular spaces of the pressure-operated cushion support devices, and that a gas-loaded pressure medium reservoir or a pump unit with a zero
  • At least one hydraulic pressure cushion enclosed in a sealed annular space is arranged between each support sleeve and the sleeve surrounding it, which carries the machine housing via crossbeams, and is provided with separate supply and discharge lines for the pressure medium.
  • This design and arrangement of the volume-variable pressure-actuated upholstery can, in particular, achieve the further advantage that a better fine adjustment of the labyrinth seal play is possible and, as a result, a considerable amount of sealing medium can be saved, which, if the seal play is enlarged, due to the necessary greater radial play of the stuffing boxes would be required.
  • the bearing blocks of the rotor shaft are supported in a height-adjustable manner with respect to the foundation by means of volume-variable pressure-actuated cushions.
  • This arrangement together with the hydraulic mounting of the machine housing makes it considerably easier to adjust these parts mutually and in a horizontal position and to align them with any other machine units of a turbo group.
  • the vibration damping for both the housing and the turbine runner is significantly improved.
  • the turbine runs more smoothly and the foundation is relieved of vibrations. Even in the case of changes in shape and position of the foundation itself, the ideal position of the machine housing and the turbo rotor can always be achieved with the double adjustment option of the pressure-operated cushion bearing.
  • the resulting changes in shape are automatically and continuously compensated by appropriate adjustment of the machine housing relative to the rotor shaft so that the required labyrinth seal play and thus the radial play of the glands can be kept very tight, so that considerable Savings in sealing medium result.
  • a machine housing 1 of a turbo group is shown, which is shown in the upper part as a longitudinal section and in the lower part as a longitudinal view. Furthermore, the entry-side and exit-side bearing points with the designations I and 11 as well as a bearing point 111 of the subsequent machine housing are shown.
  • rotor shaft is designated 3
  • the indicated rotor bears the designation 24.
  • the machine housing 1 is supported on the cross member 15 in a manner not shown. There are also the stuffing boxes 23, the sensors 21 and the base plates 2 indicated. With 7 are the hydraulic pressure pad para-t Neillungssysteme designates which support the beams and with these the machine housing. 1
  • FIGS. 2 and 3 show details at C and D.
  • the machine housing 1 is supported on the cross member 15, which (FIGS. 4, 5) are supported hydraulically adjustable in height relative to the bearing block 5.
  • the rotor shaft 3 is sealed by means of the labyrinth seals 22, the sealing gap s of which is to be kept constant in all operating states of the machine.
  • an automatically effective labyrinth seal play setting is provided according to the invention, in which the measured value x is scanned by a respective sensor 21, which are arranged on the inlet and outlet sides of the thermally elastic labyrinth seal 22. These sensors continuously measure the change in gap x between the rotor and the seal.
  • the measured value x is transferred according to the invention by means of a transmission system (FIG. 6) to the hydraulic support in such a way that to compensate for gap changes, the pressure-actuated cushion 8 (FIG. 5) is fed with additional pressure medium or is removed.
  • FIG. 4 Further details of the arrangement are shown in FIG. 4.
  • the bearing block 5 is supported on the foundation 2 by means of pressure-actuated pads P1 enclosed in cylinders for vibration damping.
  • the bearing block 5 carries the rotor shaft bearing 4.
  • cross members 15 are arranged by means of the hydraulic pressure medium support according to the invention, on which the machine housing 1, not shown, is supported.
  • the pressure-operated cushion supports are indicated in Fig. 4 with the designations 7 and 13, 14. Details of these support systems can be found in FIG. 5.
  • Each of the cross members 15 shown in FIG. 4 is held by white pressure-operated cushion support systems, as shown in FIG. 5.
  • the support sleeve 7 is screwed into the crossmember 15 by means of a thread 20. This is closed by means of the cover 7a and is supported against the support sleeve 12 by the pressure-actuated cushion P enclosed in the annular space 8.
  • the annular space 8 is sealed off from the support sleeve 12 by means of the seals 18, 19.
  • a line 10 opens into the annular space 8, by means of which pressure oil can be supplied or discharged.
  • Up to the stop nut 16 the support sleeve 12 is moved into a maximum permissible end limit.
  • the upper nut 16 counters the lower stop nut 16.
  • the support sleeve 12 is guided on the stud 6, which is screwed into the bearing block 5.
  • the support sleeve 12 is supported on the bearing block 5 in a self-adjusting manner via the spherical shell 13 resting on the bearing block 5 and the ball head 14.
  • an annular space 9 is provided, which is sealed off from the support sleeve 12 by means of the seal 17.
  • leakage oil which passes between the support sleeve 7 and the support sleeve 12 collects from the annular space 8 and is discharged via the line 11.
  • FIG. 6 An electro-hydraulic circuit for carrying out the automatic sealing gap size control is shown in FIG. 6 as an example.
  • the dimension x as a deviation from a set value is continuously measured by the sensors 21 on the inlet and outlet sides by scanning the rotor shaft 3 and is given as a control signal via the lines 25 to positioners 26 processing the control signals.
  • the supply or discharge of pressure oil via the lines 10 to the annular spaces 8, which contain the pressure-actuated pads P is controlled via the lines 33 and the electro-hydraulic converters 27.
  • the pressure medium is generated by a motor-driven pressure medium pump 29, 30 and is sucked out of the storage container 28 and fed to the electrohydraulic converters 27 via the lines 32 and discharged back to the container 28 via the lines 31.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Turbine Rotor Nozzle Sealing (AREA)
  • Sealing Using Fluids, Sealing Without Contact, And Removal Of Oil (AREA)
  • Sealing Of Bearings (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)

Abstract

A flow machine particularly a superheated gas turbine comprises a housing with a rotor disposed in the housing for rotation therein and sealed at each end with the housing by a labyrinth seal. The construction includes rotor shaft bearings which rotatably support the shafts and which are supported by bearing blocks disposed on the foundation. The housing and the shaft are mounted relative to each other by means of fluid pressure operated cushions adjacent each end of the shaft and adjacent the labyrinth seal so as to maintain the shafts and the seals with a predetermined clearance.

Description

Die Erfindung betrifft eine Strömungsmaschine, insbesondere Heißgasturbine, bei der das Maschinengehäuse auf veränderlichen Stützvorrichtungen gegenüber der Läuferwelle höhenverstellbar gelagert ist.The invention relates to a turbomachine, in particular a hot gas turbine, in which the machine housing is mounted such that it can be adjusted in height on variable support devices with respect to the rotor shaft.

Bei derartigen Maschinen treten hinsichtlich der Gehäuse- und Läuferwellenlagerung mehrere und verschiedenartige Probleme auf, und es hat nicht an zahlreichen Versuchen gefehlt, die bekannten Schwierigkeiten zu vermeiden oder ihnen abzuhelfen.Such machines have several and various problems with regard to the housing and rotor shaft bearings, and there has been no lack of numerous attempts to avoid the known difficulties or to remedy them.

Bei eingehäusigen, mehr noch bei zwei- oder mehrgehäusigen Strömungsmaschinen, wie Turbinen oder Verdichtern, taucht bereits beim Ausrichten der Gehäuseteile bei der Montage die Aufgabe auf, eine Justierungsmöglichkeit für diese Teile zu schaffen, welche ein exaktes und einfaches Ausrichten ermöglicht.In the case of single-case, more particularly two-case or multi-case flow machines, such as turbines or compressors, the task already arises when aligning the housing parts during assembly to create an adjustment option for these parts, which enables precise and simple alignment.

Ein weiteres Problem bei derartigen Maschinen besteht auch darin, daß sich zuweilen Veränderungen in der Fundamentierung, beispielsweise durch Bodensetzungen ergeben, wodurch die genaue waagerechte Ausrichtung der Maschine bzw. der Maschinensätze beeinträchtigt werden kann. In diesen Fällen muß eine Nachrichtung erfolgen, welche häufig mit erheblichem technischen Aufwand verbunden ist.Another problem with such machines is that changes in the foundations sometimes occur, for example due to subsidence, which can impair the precise horizontal alignment of the machine or machine sets. In these cases, notification must take place, which is often associated with considerable technical outlay.

Ein sehr schwerwiegendes Problem stellt die Sicherung einer genauen Zentrierung und Aufrechterhaltung der Spiele bei Wärmedehnungen der Maschine dar. Um ein Nachstellen von Gehäuseteilen zu ermöglichen, wird beispielsweise nach der DE-AS 1 289 535 vorgeschlagen, diese Teile gegeneinander mit Hilfe von Einstellschrauben und austauschbaren Beilagen veränderlicher Stärke abzustützen. Auch ein weiterer ähnlicher Vorschlag nach dem DE-GM 7 124 691 bezieht sich auf dieses Problem und zeigt eine Anordnung von kugeligen Einstellkörpern in Verbindung mithöhenverstellbaren Tauchmuttern.A very serious problem is ensuring a precise centering and maintenance of the games in the case of thermal expansion of the machine. In order to enable housing parts to be readjusted, it is proposed, for example according to DE-AS 1 289 535, that these parts be replaced by adjusting screws and interchangeable inserts support variable strength. Another similar proposal according to DE-GM 7 124 691 relates to this problem and shows an arrangement of spherical adjusting bodies in connection with height-adjustable immersion nuts.

Das Problem des Ausrichtens, insbesondere mehrgehäusigen Maschinensätzen dieser Art, liegt auch der DE-AS 2 325 642 zugrunde, bei der es darum geht, die relative Ausrichtung von Nutzleistungs-Turbinenrotor im Nutzleistungs-Turbinengehäuse zu erleichtern und zu verbessern. Es wird zu diesem Zweck eine Aufhängung der Turbine an zwei Drehzapfen und eine Abstützung des Gasgenerators an einer beweglichen Tragkonstruktion vorgeschlagen. Eine ähnliche Aufhängung zeigt auch die DE-OS 2 617 024. Dort ist das Gehäuse des Turbinenstators mittels radialgerichteter Bolzen an Flanschen des Außengehäuses des Triebwerks frei dehnbar aufgehängt.The problem of alignment, in particular multi-housing machine sets of this type, is also based on DE-AS 2 325 642, which is concerned with facilitating and improving the relative alignment of the power turbine rotor in the power turbine housing. For this purpose, a suspension of the turbine on two pivots and a support of the gas generator on a movable support structure are proposed. A similar suspension is also shown in DE-OS 2 617 024. There, the housing of the turbine stator is suspended in a freely stretchable manner by means of radially directed bolts on flanges of the outer housing of the engine.

Besondere Schwierigkeiten bringt die axiale Ausrichtung eines mehrgehäusigen bzw. mehrteiligen Maschinensatzes mit sich, beispielsweise einer Turbogruppe bestehend aus einer Helium-Hochtemperatur-Turbine mit einem Verdichter und einem Generator. Gemäß der DE-OS 2 717 617 wird vorgeschlagen, daß zwischen dem Fundament und der Turbogruppe höhenverstellbare und axialbewegliche Abstützungen angeordnet sind, welche an Pratzen seitlich der Turbogruppe angreifen und hydraulisch oder mechanisch höhenverstellbar sein sollten. Dabei sind für jedes Maschinengehäuse mindestens vier derartige höhenverstellbare Abstützungen vorgesehen. Mittels einer derartigen Anordnung ist es möglich, die Gehäuse von mehreren zu einer Turbogruppe gehörenden Maschinen axial auszurichten und auch diese Ausrichtung im Bedarfsfall nachzustellen.The axial alignment of a multi-housing or multi-part machine set, for example a turbo group consisting of a helium high-temperature turbine with a compressor and a generator, presents particular difficulties. According to DE-OS 2 717 617 it is proposed that height-adjustable and axially movable supports are arranged between the foundation and the turbo group which act on claws on the side of the turbo group and should be hydraulically or mechanically height-adjustable. At least four such height-adjustable supports are provided for each machine housing. By means of such an arrangement it is possible to axially align the housings of several machines belonging to a turbo group and also to adjust this alignment if necessary.

Abgesehen von den in den genannten Veröffentlichungen behandelten Schwierigkeiten der Ausrichtung solcher Strömungsmaschinen bei der Montage oder aber bei sich im Laufe der Betriebszeit einstellenden Fluchtungsfehlern sowie dem weiteren Problem, vor allem bei thermisch hoch belasteten Strömungsmaschinen, daß sich bei ungleichförmiger Wärmebelastung der Gehäuse- und Baugruppenteile Spannungen und unzulässige Änderungen der erforderlichen Spiele ergeben können, besteht auch noch weiterhin die Schwierigkeit, daß eine ausreichende Schwingungsdämpfung bei derartigen Maschinen, unter Berücksichtigung unterschiedlicher Betriebszustände, bei Anwendung der bekannten Lageranordnungen, oft nicht erreichbar ist.Apart from the difficulties of aligning such turbomachines during assembly or in the event of misalignments which arise in the course of the operating time, as well as the further problem, especially with thermally highly stressed turbomachines, that uneven thermal loading of the housing and assembly parts causes stresses and may result in inadmissible changes in the required games, there is still the difficulty that adequate vibration damping in such machines, taking into account different operating states, when using the known bearing arrangements, is often not achievable.

Aus der CH-A-212270 ist eine Gas- oder Dampfturbine bekannt, bei der das Maschinengehäuse außerhalb des Bereichs der ein- und austrittsseitigen, mittels auf dem Fundament angeordneten Lagerböcke abgestützten Läuferwellenlager unabhängig von diesen auf Stützvorrichtungen gegenüber der Läuferwelle höhenverstellbar gelagert werden soll. Das Turbinengehäuse ist dabei auf dem Rahmen durch Stützvorrichtungen dadurch gelenkig abgestützt, daß ihre Enden als Kugeln ausgebildet und in Kugelpfannen des Gehäuses bzw. des Rahmens gelagert sind. Die Stützvorrichtungen sind als rohrförmige Stangen ausgebildet, durch die ein Wärme- bzw. Kältemittel hindurchgeleitet wird. Die Höhenverstellung der Stützvorrichtungen soll hierbei durch temperaturbedingte Längenveränderung, und zwar durch Erwärmen oder Abkühlen mittels der durch die rohrförmigen Stangen hindurchgeführten Wärme- oder Hältemittel, erfolgen.From CH-A-212270 a gas or steam turbine is known, in which the machine housing outside of the area of the inlet and outlet side rotor shaft bearings, which are supported by bearing blocks arranged on the foundation, is to be mounted in height-adjustable manner independently of these on supporting devices with respect to the rotor shaft. The turbine housing is supported in an articulated manner on the frame by supporting devices in that its ends are designed as balls and are mounted in ball sockets of the housing or the frame. The support devices are designed as tubular rods through which a heat or refrigerant is passed. The height adjustment of the support devices is to be carried out by changing the length due to temperature, namely by heating or cooling by means of the heating or holding means passed through the tubular rods.

Die Einrichtung nach der US-A-3 764 098 dient der Bestimmung und Überprüfung der Gewichtsverteilung einer Turbine auf ihre Abstützung. Sie bezweckt die Gehäuseausrichtung und gleichzeitige Gewichtsverteilungsüberprüfung. Diese Einrichtung stellt insofern eine Montagehilfe vor der Inbetriebnahme dar.The device according to US-A-3 764 098 is used to determine and check the weight distribution of a turbine for its support. It aims at housing alignment and simultaneous weight distribution check. In this respect, this device represents an assembly aid before commissioning.

Die DE-A-2 557 805 betrifft einen Maschinensatz, bestehend z. B. aus einer Turbine, einer elektrischen Maschine und einer Pumpe, dessen Rotor an drei oder mehr voneinander entfernten Stellen eine Radiallagerung gegenüber dem Fundament aufweist. Zwei der Radiallagerungen sind als Zentrierlager ausgebildet, die die Lage des Rotors gegenüber dem Fundament bestimmen, während die übrigen Radiallagerungen als mittels Stellmotor radial verschiebliche Lager ausgebildet sind.DE-A-2 557 805 relates to a machine set consisting of e.g. B. from a turbine, an electrical machine and a pump, the rotor of which has a radial bearing relative to the foundation at three or more points apart. Two of the radial bearings are designed as centering bearings, which determine the position of the rotor relative to the foundation men, while the other radial bearings are designed as radially displaceable bearings by means of an actuator.

Der Erfindung liegt die Aufgabe zugrunde, eine Ausbildungsweise der Lagerung für Strömungsmaschinen, insbesondere Heißgasturbinen, die thermisch hoch belastet sind, zu schaffen, die es gestattet, den oben geschilderten Problemen in befriedigender Weise zu begegnen. Die Erfindung bezieht sich daher auf eine solche Strömungsmaschine, insbesondere Heißgasturbine, bei der das Maschinengehäuse außerhalb des Bereiches der ein- und austrittsseitigen, mittels auf dem Fundament angeordneter Lagerböcke abgestützten Läuferwellenlager unabhängig von diesen auf veränderlichen Stützvorrichtungen gegenüber der Läuferwelle höhenverstellbar gelagert ist.The invention has for its object to provide an embodiment of the storage for turbomachines, in particular hot gas turbines that are subject to high thermal loads, which allows the problems described above to be met in a satisfactory manner. The invention therefore relates to such a turbomachine, in particular a hot gas turbine, in which the machine housing is mounted outside of the region of the rotor shaft bearings on the inlet and outlet side, which are supported by means of bearing blocks arranged on the foundation, and are height-adjustable independently of these on variable support devices with respect to the rotor shaft.

Die Aufgabe wird in der Weise gelöst, daß bei einem Maschinengehäuse das beidseitig mit einer mittels eines Sperrmediums beaufschlagten Labyrinthdichtung gegenüber der Läuferwelle vorgesehen ist, die Stützvorrichtung im Bereich des Läuferwellenlagers angebracht und als volumenveränderlich druckbetätigte Polster ausgebildet sind, daß das Maschinengehäuse gegenüber dem Fundament über Traversen mittels sich auf druckbetätigten Polstern abstützender Traghülsen höhenverstellbar gelagert ist, wobei die druckbetätigten Polster in zwischen den Traghülsen und den an Stehbolzen mit Spiel geführten Stützhülsen gebildeten Ringnuten angeordnet sind, und daß zur selbsttätigen kontinuierlichen Beeinflussung des Labyrinthdichtungsspiels der Strömungsmaschine Meßfühler über Steuersignalleitungen mit einem jedem Meßfühler zugeordneten Stellungsregler in Verbindung stehen, der über Steuerleitungen jeweils der Ein-und der Austrittsseite zugeordneter elektrohydraulische Wandler steuert und dadurch die Zufuhr bzw. die Ableitung von Druckmittel über die Leitungen zu bzw. aus den Ringräumen der druckbetätigten Polster-Stützvorrichtungen regelt, und daß als Druckmittelquelle zur Bereitstellung von Druckmittel mit stets gleichmäßiger und ausreichender Druckhöhe ein gasbelasteter Druckmittelspeicher oder ein Pumpenaggregat mit einer Nullhubregelung bzw. Druckbegrenzungsregelung dient. Dabei sind die Stützhülsen auf dem Lager nur mittels selbsteinstellender, aus Kugelschale und Kugelkopf gebildeten sphärischen Lagern abgestützt.The object is achieved in such a way that in the case of a machine housing which is provided on both sides with a labyrinth seal against the rotor shaft by means of a locking medium, the support device is attached in the region of the rotor shaft bearing and is designed as volume-variable pressure-actuated cushions such that the machine housing is connected to the foundation via crossbeams is height-adjustable by means of support sleeves supported on pressure-actuated pads, the pressure-actuated pads being arranged in ring grooves formed between the support sleeves and the support sleeves formed on studs with play, and that for automatic continuous influencing of the labyrinth seal play of the turbomachine, measurement sensors are assigned to each measurement sensor via control signal lines The positioner is connected, which controls the electrohydraulic transducers assigned to the inlet and outlet sides via control lines and thereby the feed hr or the discharge of pressure medium via the lines to or from the annular spaces of the pressure-operated cushion support devices, and that a gas-loaded pressure medium reservoir or a pump unit with a zero stroke control or pressure limitation control serves as the pressure medium source for the provision of pressure medium with a constant and sufficient pressure level . The support sleeves are supported on the bearing only by means of self-adjusting spherical bearings formed from a spherical shell and ball head.

Erfindungsgemäß ist zwischen jeder Stützhülse und der sie umgebenden, das Maschinengehäuse über Traversen tragenden Hülse jeweils mindestens ein in einen abgedichteten Ringraum eingeschlossenes hydraulisches Druckpolster angeordnet, das mit getrennten Zuführungs- und Ablaßleitungen für das Druckmittel versehen ist.According to the invention, at least one hydraulic pressure cushion enclosed in a sealed annular space is arranged between each support sleeve and the sleeve surrounding it, which carries the machine housing via crossbeams, and is provided with separate supply and discharge lines for the pressure medium.

Durch diese Ausbildungs- und Anordnungsweise der volumenveränderlich druckbetätigten Polster kann insbesondere der weitere Vorteil erzielt werden, daß eine bessere Feineinstellung des Labyrinthdichtungsspieles möglich ist und dadurch eine erhebliche Menge an Sperrmedium eingespart werden kann, welches bei einer Vergrößerung des Dichtungsspiels wegen der notwendigen größeren Radialspiele der Stopfbüchsen erforderlich wäre.This design and arrangement of the volume-variable pressure-actuated upholstery can, in particular, achieve the further advantage that a better fine adjustment of the labyrinth seal play is possible and, as a result, a considerable amount of sealing medium can be saved, which, if the seal play is enlarged, due to the necessary greater radial play of the stuffing boxes would be required.

Erfindungsgemäß wird weiterhin vorgeschlagen, daß auch die Lagerböcke der Läuferwelle gegenüber dem Fundament mittels volumenveränderlicher druckbetätigter Polster höheneinstellbar abgestützt sind. Durch diese Anordnung zusammen mit der hydraulischen Lagerung des Maschinengehäuses wird es ganz wesentlich erleichtert, diese Teile gegenseitig und in horizontaler Lage zu justieren und zusammen mit etwa vorhandenen weiteren Maschineneinheiten einer Turbogruppe auszurichten. Ferner wird die Schwingungsdämpfung sowohl für das Gehäuse als auch für den Turbinenläufer ganz erheblich verbessert. Die Turbine läuft ruhiger und das Fundament wird schwingungstechnisch entlastet. Auch bei Form- und Lageveränderungen des Fundamentes selbst kann durch die zweifache Einstellungsmöglichkeit der druckbetätigten Polsterlagerung ohne Schwierigkeiten stets die ideale Lage des Maschinengehäuses und des Turboläufers hergestellt werden.According to the invention it is further proposed that the bearing blocks of the rotor shaft are supported in a height-adjustable manner with respect to the foundation by means of volume-variable pressure-actuated cushions. This arrangement together with the hydraulic mounting of the machine housing makes it considerably easier to adjust these parts mutually and in a horizontal position and to align them with any other machine units of a turbo group. Furthermore, the vibration damping for both the housing and the turbine runner is significantly improved. The turbine runs more smoothly and the foundation is relieved of vibrations. Even in the case of changes in shape and position of the foundation itself, the ideal position of the machine housing and the turbo rotor can always be achieved with the double adjustment option of the pressure-operated cushion bearing.

Je nach Betriebszustand und dadurch bedingter thermischer Belastung der Strömungsmaschine werden die sich ergebenden Formänderungen selbsttätig und kontinuierlich durch entsprechende Verstellung des Maschinengehäuses gegenüber der Läuferwelle so ausgeglichen, daß das erforderliche Labyrinthdichtungsspiel und damit die radialen Spiele der Stopfbüchsen sehr eng gehalten werden können, so daß sich erhebliche Einsparungen an Sperrmedium ergeben.Depending on the operating state and the resulting thermal load on the turbomachine, the resulting changes in shape are automatically and continuously compensated by appropriate adjustment of the machine housing relative to the rotor shaft so that the required labyrinth seal play and thus the radial play of the glands can be kept very tight, so that considerable Savings in sealing medium result.

Ein Ausführungsbeispiel der erfindungsgemäßen Ausbildungs- und Anordnungsweise der Lagerung des Maschinengehäuses und auch der Lagerböcke für die Läuferwelle und ein Schaltschema sind in der Zeichnung dargestellt und im folgenden näher erläutert. Es zeigt

  • Fig. 1 eine Strömungsmaschine teils in Seitenansicht, teils im Längsschnitt;
  • Fig. 2 eine Einzelheit bei C im Längsschnitt;
  • Fig. 3 eine Einzelheit D im Längsschnitt;
  • Fig. 4 einen Schnitt A-A' gem. Fig. 1;
  • Fig. 5 einen Schnitt B-B' gem. Fig. 4;
  • Fig. 6 eine Schaltungsanordnung gemäß der Erfindung.
An embodiment of the inventive training and arrangement of the storage of the machine housing and also the bearing blocks for the rotor shaft and a circuit diagram are shown in the drawing and explained in more detail below. It shows
  • 1 shows a turbomachine, partly in side view, partly in longitudinal section;
  • Figure 2 shows a detail at C in longitudinal section.
  • 3 shows a detail D in longitudinal section;
  • Fig. 4 shows a section AA 'acc. Fig. 1;
  • Fig. 5 shows a section BB 'acc. Fig. 4;
  • Fig. 6 shows a circuit arrangement according to the invention.

In Fig. 1 ist ein Maschinengehäuse 1 einer Turbogruppe gezeigt, welches im oberen Teil als Längsschnitt und im unteren Teil als Längsansicht dargestellt ist. Ferner sind auch die eintrittsseitigen und austrittsseitigen Lagerstellen mit den Bezeichnungen I und 11 sowie eine Lagerstelle 111 des nachfolgenden Maschinengehäuses dargestellt.In Fig. 1, a machine housing 1 of a turbo group is shown, which is shown in the upper part as a longitudinal section and in the lower part as a longitudinal view. Furthermore, the entry-side and exit-side bearing points with the designations I and 11 as well as a bearing point 111 of the subsequent machine housing are shown.

In Fig. 1 ist die Läuferwelle mit 3 bezeichnet, während der angedeutete Läufer die Bezeichnung 24 trägt. Auf die Traverse 15 stützt sich - in nicht näher dargestellter Weise - das Maschinengehäuse 1 ab. Es sind ferner die Stopfbüchsen 23, die Meßfühler 21 und die Grundplatten 2 angedeutet. Mit 7 sind die hydraulischen Druckpolster-Abstützungssysteme bezeichnet, welche die Traversen und mit diesen das Maschinengehäuse 1 abstützen.In Fig. 1, the rotor shaft is designated 3, while the indicated rotor bears the designation 24. The machine housing 1 is supported on the cross member 15 in a manner not shown. There are also the stuffing boxes 23, the sensors 21 and the base plates 2 indicated. With 7 are the hydraulic pressure pad para-t ützungssysteme designates which support the beams and with these the machine housing. 1

Die Besonderheiten der Lagerung des Maschinengehäuses 1 ergeben sich aus den Fig. 2 und 3, welche Einzelheiten bei C und D zeigen. Das Maschinengehäuse 1 stützt sich auf die Traverse 15 ab, welche (Fig. 4, 5) hydraulisch höhenverstellbar gegenüber dem Lagerbock 5 abgestützt sind. Die Läuferwelle 3 ist mittels den Labyrinthdichtungen 22 abgedichtet, deren Dichtspalt s bei allen Betriebszuständen der Maschine konstant gehalten werden soll. Um dies zu erreichen, ist erfindungsgemäß eine selbsttätig wirksame Labyrinthdichtungsspiel-Einstellung vorgesehen, bei welcher der Meßwert x durch jeweils einen Meßfühler 21 abgetastet wird, die an den Ein-und Austrittsseiten an der wärmeelastischen Labyrinthdichtung 22 angeordnet sind. Durch diese Meßfühler wird kontinuierlich die Spaltveränderung x zwischen dem Läufer und der Dichtung gemessen. Der abgenommene Meßwert x wird erfindungsgemäß mittels eines Übertragungssystems (Fig. 6) auf die hydraulische Abstützung in der Weise übertragen, daß zum Ausgleich von Spaltveränderungen den volumenveränderlich druckbetätigten Polstern 8 (Fig. 5) weiteres Druckmittel zugeführt oder aber abgeführt wird.The special features of the mounting of the machine housing 1 result from FIGS. 2 and 3, which show details at C and D. The machine housing 1 is supported on the cross member 15, which (FIGS. 4, 5) are supported hydraulically adjustable in height relative to the bearing block 5. The rotor shaft 3 is sealed by means of the labyrinth seals 22, the sealing gap s of which is to be kept constant in all operating states of the machine. In order to achieve this, an automatically effective labyrinth seal play setting is provided according to the invention, in which the measured value x is scanned by a respective sensor 21, which are arranged on the inlet and outlet sides of the thermally elastic labyrinth seal 22. These sensors continuously measure the change in gap x between the rotor and the seal. The measured value x is transferred according to the invention by means of a transmission system (FIG. 6) to the hydraulic support in such a way that to compensate for gap changes, the pressure-actuated cushion 8 (FIG. 5) is fed with additional pressure medium or is removed.

Weitere Einzelheiten der Anordnung sind in Fig. 4 dargestellt. Auf dem Fundament 2 ist der Lagerbock 5 über in Zylindern eingeschlossene druckbetätigte Polster P1 zur Schwingungsdämpfung abgestützt. Der Lagerbock 5 trägt das Läuferwellenlager 4. Ferner sind auf dem Lagerbock 5 beidseitig des Läuferwellenlagers 2 Traversen 15 mittels der erfindungsgemäßen hydraulischen Druckmittelabstützung angeordnet, auf welche sich das nicht dargestellte Maschinengehäuse 1 abstützt. Die druckbetätigten Polster-Abstützungen sind in Fig. 4 mit den Bezeichnungen 7 und 13, 14 angedeutet. Einzelheiten dieser Abstützungssysteme ergeben sich aus Fig. 5.Further details of the arrangement are shown in FIG. 4. The bearing block 5 is supported on the foundation 2 by means of pressure-actuated pads P1 enclosed in cylinders for vibration damping. The bearing block 5 carries the rotor shaft bearing 4. Furthermore, on the bearing block 5 on both sides of the rotor shaft bearing 2 cross members 15 are arranged by means of the hydraulic pressure medium support according to the invention, on which the machine housing 1, not shown, is supported. The pressure-operated cushion supports are indicated in Fig. 4 with the designations 7 and 13, 14. Details of these support systems can be found in FIG. 5.

Jede der aus Fig. 4 ersichtlichen Traversen 15 wird durch wei druckbetätigte Polster-Abstützungssysteme, wie in Fig. 5 dargestellt, gehalten. In die Traverse 15 ist mittels Gewinde 20 die Traghülse 7 eingeschraubt. Diese ist mittels des Deckels 7a verschlossen und stützt sich über das im Ringraum 8 eingeschlossene druckbetätigte Polster P gegenüber der Stützhülse 12 ab. Der Ringraum 8 ist mittels der Dichtungen 18,19 gegenüber der Stützhülse 12 abgedichtet. In den Ringraum 8 mündet eine Leitung 10, mittels welcher Drucköl zugeführt oder abgelassen werden kann. Bis zur Anschlagmutter 16 wird die Stützhülse 12 in eine maximal zulässige Endbegrenzung gefahren. Die obere Mutter 16 kontert die untere Anschlagmutter 16.Each of the cross members 15 shown in FIG. 4 is held by white pressure-operated cushion support systems, as shown in FIG. 5. The support sleeve 7 is screwed into the crossmember 15 by means of a thread 20. This is closed by means of the cover 7a and is supported against the support sleeve 12 by the pressure-actuated cushion P enclosed in the annular space 8. The annular space 8 is sealed off from the support sleeve 12 by means of the seals 18, 19. A line 10 opens into the annular space 8, by means of which pressure oil can be supplied or discharged. Up to the stop nut 16, the support sleeve 12 is moved into a maximum permissible end limit. The upper nut 16 counters the lower stop nut 16.

Die Stützhülse 12 ist an dem Stehbolzen 6 geführt, welcher im Lagerbock 5 verschraubt ist. Über die auf dem Lagerbock 5 aufliegende Kugelschale 13 und den Kugelkopf 14 ist die Stützhülse 12 auf dem Lagerbock 5 selbsteinstellend abgestützt. Ferner ist ein Ringraum 9 vorgesehen, der mittels der Dichtung 17 gegenüber der Stützhülse 12 abgedichtet ist. Im Ringraum 9 sammelt sich gegebenenfalls aus dem Ringraum 8 zwischen der Traghülse 7 und der Stützhülse 12 durchtretendes Lecköl, welches über die Leitung 11 abgeführt wird.The support sleeve 12 is guided on the stud 6, which is screwed into the bearing block 5. The support sleeve 12 is supported on the bearing block 5 in a self-adjusting manner via the spherical shell 13 resting on the bearing block 5 and the ball head 14. Furthermore, an annular space 9 is provided, which is sealed off from the support sleeve 12 by means of the seal 17. In the annular space 9, leakage oil which passes between the support sleeve 7 and the support sleeve 12 collects from the annular space 8 and is discharged via the line 11.

In Fig. 6 ist als Beispiel eine elektro-hydraulische Schaltung zur Durchführung der selbsttätigen Dichtspaltgröße-Steuerung dargestellt. Das Maß x als Abweichung von einem eingestellten Sollwert wird durch die Meßfühler 21 eintritts-und austrittsseitig durch Abtasten der Läuferwelle 3 kontinuierlich gemessen und als Steuersignal über die Leitungen 25 an die Steuersignale verarbeitende Stellungsregler 26 gegeben. Von dort erfolgt über die Leitungen 33 und die elektrohydraulischen Wandler 27 die Steuerung der Zuführung oder Abführung von Drucköl über die Leitungen 10 zu den Ringräumen 8, welche die druckbetätigten Polster P enthalten. Das Druckmittel wird im Ausführungsbeispiel von einer motorgetriebenen Druckmittelpumpe 29, 30 erzeugt und aus dem Vorratsbehälter 28 angesaugt und über die Leitungen 32 den elektrohydraulischen Wandlern 27 zugeführt und über die Leitungen 31 wieder an den Behälter 28 abgeführt.An electro-hydraulic circuit for carrying out the automatic sealing gap size control is shown in FIG. 6 as an example. The dimension x as a deviation from a set value is continuously measured by the sensors 21 on the inlet and outlet sides by scanning the rotor shaft 3 and is given as a control signal via the lines 25 to positioners 26 processing the control signals. From there, the supply or discharge of pressure oil via the lines 10 to the annular spaces 8, which contain the pressure-actuated pads P, is controlled via the lines 33 and the electro-hydraulic converters 27. In the exemplary embodiment, the pressure medium is generated by a motor-driven pressure medium pump 29, 30 and is sucked out of the storage container 28 and fed to the electrohydraulic converters 27 via the lines 32 and discharged back to the container 28 via the lines 31.

Claims (4)

1. A flow machine, more particularly a hot gas turbine, the machine housing being mounted on variable support means so as to be vertically adjustable with respect to the rotor shaft, characterized in that in the case of a machine housing (1) both sides of which are provided with a labyrinth seal with respect to the rotor shaft, the said seals being subjected to the action of a barrier medium, the support means is disposed in the region of the rotor shaft bearing (4) and is in the form of a variable-volume pressure-actuated cushion (P), the machine housing (1) is mounted for vertical adjustment with respect to the foundation (2) by way of cross-members (15) through the agency of carrier sleeves (7) being on pressure-actuated cushions (P), the latter being disposed in annular grooves (8) formed between the carrier sleeves (7) and the support sleeves (12) guided with clearance on stay bolts (6), and in that for the purpose of automatic continuous control of the labyrinth seal clearance of the flow machine measuring sensors (21) are connected via control signal lines (25) to a position controller (26) which is associated which each measuring sensor (21) and which by way of control lines (33) controls electrohydraulic transducers (27) each associated with the inlet and with the outlet side and thus controls the supply and discharge of pressure medium via the lines (10) to and from the annular spaces (8) of the pressure-actuated cushion support means, and a gas-loaded pressure medium accumulator or a pump unit (29, 30) is used as pressure medium source for preparing pressure medium having always a uniform and adequate pressure head.
2. A flow machine according to claim 1, characterized in that the support sleeves (12) are borne on the bearing bracket (5) by means of selfadjusting spherical bearings formed from a ball socket (13) and ball head (14).
3. A flow machine according to claims 1 and 2, characterized in that at least one hydraulic pressure cushion (P) enclosed in a sealed annular chamber (8) is provided between each support sleeve (12) and its surrounding sleeve (7) bearing the machine housing (1) by way of the crossmember (15), the said pressure cushion or cushions being provided with separate supply and discharge lines (10,11) for the pressure medium.
4. A flow machine according to claim 1, characterized in that the bearing brackets (5) of the rotor shaft (3) are supported so as to be vertically adjustable with respect to the foundation (1) by means of variable-volume pressure-actuated cushions (P1).
EP81101816A 1980-06-19 1981-03-12 Turbomachine, particularly hot gas turbine, in which the stator is adjustable in height for continuously influencing the gap of the labyrinth sealing Expired EP0042469B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT81101816T ATE8168T1 (en) 1980-06-19 1981-03-12 FLOW MACHINE, ESPECIALLY HOT GAS TURBINE, IN WHICH THE HOUSING IS MOUNTED ADJUSTABLE IN HEIGHT FOR THE AUTOMATIC CONTINUOUS INFLUENCE OF THE LABYRINTH SEAL PLAY.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3022861A DE3022861C2 (en) 1980-06-19 1980-06-19 Turbo machine, in particular hot gas turbine, and method for automatic continuous influencing of the labyrinth seal clearance of the turbo machine
DE3022861 1980-06-19

Publications (2)

Publication Number Publication Date
EP0042469A1 EP0042469A1 (en) 1981-12-30
EP0042469B1 true EP0042469B1 (en) 1984-06-27

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EP81101816A Expired EP0042469B1 (en) 1980-06-19 1981-03-12 Turbomachine, particularly hot gas turbine, in which the stator is adjustable in height for continuously influencing the gap of the labyrinth sealing

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Country Link
US (1) US4405283A (en)
EP (1) EP0042469B1 (en)
JP (2) JPS5728808A (en)
AT (1) ATE8168T1 (en)
DE (2) DE3022861C2 (en)
ES (2) ES8204053A1 (en)

Families Citing this family (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4759262A (en) * 1987-05-11 1988-07-26 The Dow Chemical Company Apparatus for restraining rotary motion of a motor component
JP2888655B2 (en) * 1991-02-28 1999-05-10 株式会社東芝 Shaft sealing device for axial flow turbine
WO2002077417A2 (en) * 2001-03-26 2002-10-03 Pebble Bed Modular Reactor (Proprietary) Limited A method of operating a turbine and a gas turbine
EP1249579A1 (en) * 2001-04-11 2002-10-16 Siemens Aktiengesellschaft Steam turbine
US7368827B2 (en) * 2006-09-06 2008-05-06 Siemens Power Generation, Inc. Electrical assembly for monitoring conditions in a combustion turbine operating environment
US7656135B2 (en) * 2007-01-05 2010-02-02 General Electric Company Method and apparatus for controlling rotary machines
US20130073172A1 (en) * 2011-09-15 2013-03-21 Bret Dwayne Worden Detection system and method
DE102016108463A1 (en) * 2016-05-09 2017-11-09 Man Diesel & Turbo Se labyrinth seal
CN107448611B (en) * 2017-09-27 2024-05-24 孟金来 Labyrinth sealing device with adjustable sealing gap
US11970279B2 (en) 2020-02-21 2024-04-30 General Electric Company Control system and methods of controlling an engine-mounting link system
US11939070B2 (en) 2020-02-21 2024-03-26 General Electric Company Engine-mounting links that have an adjustable inclination angle

Family Cites Families (23)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE7124691U (en) * 1900-01-01 Siemens Ag Height-adjustable support of the lower part of an inner housing shell of a turbomachine, in particular steam turbine, housing on the lower outer housing part
US1168273A (en) * 1914-05-11 1916-01-18 Ingersoll Rand Co Means for maintaining clearances in rotary machines.
CH212270A (en) * 1939-08-05 1940-11-15 Sulzer Ag Gas or steam turbine.
DE733968C (en) * 1941-08-06 1943-04-06 Turbinenfabrik Brueckner Kanis Cantilever overpressure steam or gas turbine with vibration protection
DE937234C (en) * 1954-02-21 1955-12-29 Aeg Storage of a turbine runner or turbine and generator runner
US3052123A (en) * 1959-05-21 1962-09-04 Robert E Gustafson Temperature sensing element and method of installation
DE1184973B (en) * 1960-03-04 1965-01-07 Reutlinger & Soehne Dr Arrangement for non-contact measurement of movements of a rotating shaft running perpendicular to the axis of rotation
US3161389A (en) * 1962-06-19 1964-12-15 Allis Chalmers Mfg Co Rotary machine support
US3250503A (en) * 1964-05-25 1966-05-10 Edward S Karstens Hydraulic leveling jack
GB1149203A (en) * 1966-10-20 1969-04-16 Taylor Weeks & Partner Ltd Registering printing plates
US3464654A (en) * 1967-03-24 1969-09-02 Babcock & Wilcox Co Leveling construction for heavy machinery and instruments
CH467941A (en) * 1967-07-03 1969-01-31 Escher Wyss Ag Labyrinth seal on a hydraulic centrifugal machine, the rotor of which revolves at times in water and at times in air.
US3632117A (en) * 1969-05-15 1972-01-04 Westinghouse Electric Corp Seal lift-off mechanism
US3642295A (en) * 1970-01-15 1972-02-15 Westinghouse Electric Corp Self-adjusting seal ring
US3764098A (en) * 1971-02-16 1973-10-09 Westinghouse Electric Corp Turbine with load force determining device
GB1409902A (en) * 1972-05-24 1975-10-15 Rolls Royce Stationary gas turbine power plant mounting apparatus
US3799482A (en) * 1972-05-26 1974-03-26 Bbc Brown Boveri & Cie Stabilized support structure for a turbo-machine
US3999766A (en) * 1975-11-28 1976-12-28 General Electric Company Dynamoelectric machine shaft seal
DE2557805A1 (en) * 1975-12-22 1977-06-23 Escher Wyss Gmbh Machine assembly rotor with radial bearings - has two part central bearing for positioning of pair of radially displaceable bearings
DE2617024C2 (en) * 1976-04-17 1985-09-26 MTU Motoren- und Turbinen-Union München GmbH, 8000 München Gas turbine engine
DE2635918C2 (en) * 1976-08-10 1978-01-19 Kraftwerk Union AG, 4330 Mülheim Shaft seal for a steam turbine
CH619507A5 (en) * 1977-03-21 1980-09-30 Bbc Brown Boveri & Cie
JPS54121402A (en) * 1978-03-13 1979-09-20 Kubota Ltd Gap adjusting process and its device in vacuum pump

Also Published As

Publication number Publication date
DE3022861A1 (en) 1981-12-24
EP0042469A1 (en) 1981-12-30
ATE8168T1 (en) 1984-07-15
JPS5728808A (en) 1982-02-16
ES503177A0 (en) 1982-05-01
ES8204052A1 (en) 1982-05-01
JPS6325283Y2 (en) 1988-07-11
ES8204053A1 (en) 1982-05-01
US4405283A (en) 1983-09-20
ES503176A0 (en) 1982-05-01
JPS6018203U (en) 1985-02-07
DE3022861C2 (en) 1983-12-08
DE3164373D1 (en) 1984-08-02

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