DE2114222B1

DE2114222B1 - Device for changing the sagging of a machine housing caused by its own weight

Info

Publication number: DE2114222B1
Application number: DE19712114222D
Authority: DE
Inventors: Ferdinand Dipl-Ing Zerlauth
Original assignee: Brown Boveri Sulzer Turbomaschinen AG
Current assignee: Brown Boveri Sulzer Turbomaschinen AG
Priority date: 1971-03-17
Filing date: 1971-03-24
Publication date: 1972-09-21
Also published as: CH536456A; SE368731B; DE2114222C2; JPS5146202B1; US3740164A; NL7106159A; FR2178274A5; NL148376B; IT950306B; GB1378531A

Description

luft an und fördert diese in verdichtetem Zustand durch den Kanal 23 in nicht gezeichnete, um die Gasturbine herum angeordnete Brennkammern. Das Verbrennungsgas strömt durch den Kanal 24 in die Beschaufelung der Gasturbine und alsdann durch den Kanal 25 in das Abgasgehäuse 26 der Maschine.air on and promotes this in a compressed state through the channel 23 in not shown to the gas turbine combustion chambers arranged around. The combustion gas flows through the channel 24 into the blading the gas turbine and then through the duct 25 into the exhaust housing 26 of the engine.

Der Rotor 27 des Verdichters und der Rotor 28 der Turbine sind als zusammenhängendes Stück ausgebildet und in den Lagern 29 und 30 gestützt. Das Gehäuse der Turbine ist aus einzelnen Abschnitten 31, 32 und 33 zusammengesetzt. Auch das Gehäuse des Verdichters kann aus mehreren Abschnitten zusammengesetzt sein, wovon ein Abschnitt 34 an dem an die Turbine stoßenden Ende des Verdichters erkennbar ist. Durch die Abschnitte 31 bis 34 entsteht ein rohrartiges Gehäuse, welches durch die Träger 35 und 36 auf einer Grundplatte 37 abgestützt ist. Diese Abstützungen sind etwa in den Mittelebenen 38 und 39 der Lager 29 und 30 angeordnet. Zwischen diesen Lagern erfahren sowohl das Gehäuse als auch der Rotor eine der Schwerkraft entsprechende Biegung, deren Achsen praktisch in allen Fällen wesentliche Unterschiede aufweisen. Um die Biegelinien von Rotor und Gehäuse so gut als möglich zur Deckung zu bringen, ist zwischen den Flanschen der Gehäuseabschnitte 33 und 34 ein wie in F i g. 1 und 2 dargestellter Zwischenring 6, der aus zwei Keilringen besteht, eingesetzt. Durch geeignete Verdrehung der beiden Keilringe gegeneinander, kann die Durchbiegung des Gehäuses der Durchbiegung des Rotors so weit angeglichen werden, daß die Biegungsdifferenzen an allen Stellen der Maschinenlänge auf ein Minimalmaß gebracht werden. In den meisten Fällen wird es sogar notwendig sein, durch diesen Ring die Durchbiegung des Gehäuses zu erhöhen, weil die natürliche Durchbiegung des Gehäuses kleiner ist, als diejenige des Rotors. The rotor 27 of the compressor and the rotor 28 of the turbine are designed as a coherent piece and supported in bearings 29 and 30. The turbine housing is made up of individual sections 31, 32 and 33 assembled. The housing of the compressor can also be composed of several sections be, of which a section 34 can be seen at the end of the compressor abutting the turbine is. The sections 31 to 34 create a tubular housing which is supported by the supports 35 and 36 is supported on a base plate 37. These supports are approximately in the central planes 38 and 39 of the bearings 29 and 30 are arranged. Both the housing and the rotor experience between these bearings a bend corresponding to the force of gravity, the axes of which are fundamentally different in practically all cases exhibit. In order to align the bending lines of the rotor and the housing as closely as possible, is between the flanges of the housing sections 33 and 34 as shown in FIG. 1 and 2 shown Intermediate ring 6, which consists of two wedge rings, is used. By appropriately twisting the two Wedge rings against each other, the deflection of the housing can be matched to the deflection of the rotor that the bending differences are brought to a minimum at all points along the length of the machine will. In most cases it will even be necessary to reduce the deflection through this ring of the housing, because the natural deflection of the housing is smaller than that of the rotor.

Bei der Abgasturbinen-Aufladegruppe nach F i g. 4 ist der Rotor 40 innerhalb eines aus den Abschnitten 41, 42, 43 und 44 zusammengesetzten Gehäuse angeordnet. Dieses Gehäuse wird im mittleren Bereich mit Hilfe der Pratzen 45 durch eine Konsole 46 der nicht dargestellten Brennkraftmaschine getragen. Der Gehäuseabschnitt 41 dient zur Abstützung des Lagers 47 und der Gehäuseabschnitt 44 zur Abstützung des Lagers 48. Damit wird durch das Eigengewicht des Gehäuses und insbesondere durch die Lagerbelastung das Gehäuse an den Enden nach unten gebogen, so daß seine Achse in der Längsmitte des Gehäuses aufwärts gebogen erscheint, während der an beiden Enden gelagerte Rotor in seiner Längsmitte nach unten gebogen ist. Dadurch entstehen besonders bei der Wellendichtung in der Mitte des Rotors und auch an den Lauf rädern der Turbine und des Verdichters erhebliche Verschiebungen gegenüber dem diese Teile umgebenden Gehäuse. Zur Verhinderung dieses Nachteils ist mindestens zwischen den Flanschen der Gehäuseabschnitte 42 und 43 ein Zwischenring 6, wie in den F i g. 1 und 2 dargestellt, eingebaut. Durch Einstellung des günstigsten Keilwinkels für diesen Ring 6 kann der Spalt zwischen dem Verdichterrotor 49 und der feststehenden Deckscheibe 50 auf einen Minimalwert eingestellt werden, wodurch infolge Verminderung des Spaltes der Wirkungsgrad entsprechend gehoben werden kann. Für den Fall, daß auch das Turbinenrad 51 gegenüber dem Gehäuse zu große Verschiebungen erfahren sollte, könnte ein entsprechender Doppelring auch zwischen den Flanschen der Gehäuseabschnitte 43 und 44 eingesetzt werden. Mindestens an den Schaufelenden könnte dann durch Spaltverminderungen eine Verbesserung des Betriebswirkungsgrades erreicht werden.In the exhaust gas turbine supercharging group according to FIG. 4, the rotor 40 is within one of the sections 41, 42, 43 and 44 assembled housing arranged. This case is in the middle Area carried by a bracket 46 of the internal combustion engine, not shown, with the aid of the claws 45. The housing section 41 serves to support the bearing 47 and the housing section 44 for support of the bearing 48. This is due to the weight of the housing and in particular by the Bearing load the housing bent down at the ends so that its axis in the longitudinal center of the Housing appears bent upwards, while the rotor, which is supported at both ends, is in its longitudinal center is bent downwards. This is particularly the case with the shaft seal in the middle of the rotor and there are also considerable shifts on the impellers of the turbine and the compressor compared to this Parts surrounding the housing. To prevent this disadvantage is at least between the flanges of the Housing sections 42 and 43 an intermediate ring 6, as shown in FIGS. 1 and 2 shown, installed. By attitude the most favorable wedge angle for this ring 6 can be the gap between the compressor rotor 49 and the fixed cover plate 50 can be set to a minimum value, as a result of reduction of the gap, the efficiency can be increased accordingly. In the event that the turbine wheel 51 should experience excessive shifts in relation to the housing, a corresponding one could be used Double ring can also be used between the flanges of the housing sections 43 and 44. At least at the blade ends an improvement in the operating efficiency could then be achieved by reducing the gap can be achieved.

Man sieht, daß im Fall der Maschine nach F i g. 4 durch das Einsetzen der Ringe sogar eine umgekehrte Biegung des Gehäuses erreicht werden muß. Das Gehäuse, das unter Schwerkrafteinfluß an den Enden nach unten gebogen ist, muß mittels des Zwischenrings 6 so gebogen werden, daß die Enden umgekehrt über die geometrische Achslinie hochgehoben werden. It can be seen that in the case of the machine according to FIG. 4 by inserting the rings it is even reversed Bending of the housing must be achieved. The housing that is gravity at the ends is bent downwards, must be bent by means of the intermediate ring 6 so that the ends are reversed be lifted above the geometric axis line.

Hierzu 1 Blatt Zeichnungen OOPY 1 sheet of OOPY drawings

Claims

1 2 other lying wedge rings existing intermediate ring claims: is used in such a way that by rotating the wedge rings against each other their on the housing sections

1. Device for changing the contact surfaces through the th in a selectable angle Deflection 5 caused by its own weight are adjustable against each other.

of a machine housing, which is perpendicular to By suitable rotation of the ring parts against a longitudinal axis in at least two with each other, the differences in the housing and rotor-like joint resulting from the sections to be connected with a circular ring-shaped dead weight can now be subdivided, thereby reducing deflection to a minimum value factory indicates that at the joint between. This makes it possible to maintain a minimum clearance between the housing sections (1, 2; 33, 34; 42, see rotor and housing. 43), one consisting of two tapered rings lying on top of one another by means of these tapered rings at the same time (7, 8) Intermediate ring (6) is inserted, standing manufacturing errors are corrected,
Advantageously, each of the wedge rings is subdivided several times around one another, their alignment on the housing sections, with the ring-end bearing surfaces being held together at a selectable angle by releasable tabs, adjustable relative to one another. A first embodiment of the invention

2. Device according to claim 1, characterized in that it is a gas turbine group in FIG. 1 indicates that each wedge ring (7,8) shown in um- to 3, wherein

f angsrichtung is divided several times and the 20 F i g. 1 is a longitudinal section of part of the machine ring part by detachable tabs (11, 12) together housing,

are held. F i g. 2 shows a section of the used

Intermediate ring on a larger scale and
F i g. 3 a partial longitudinal section of the gas turbine

25 illustrate group;

Fig. 4 shows a second embodiment as an exhaust gas turbine charging group for internal combustion

The invention relates to a device.

to change the weight resulting from the two housing sections 1 and 2 (Fig. 1)

called deflection of a machine housing, 30 are mutually soft by means of the flanges 3 and 4 perpendicular to its longitudinal axis in at least bound. Both flanges are perpendicular to the Mazwei Sections to be connected with a machine axis 5. Between these flanges is a circular joint is divided. Intermediate ring 6 is inserted, which consists of two superimposed

The deflection of the machine housing and lowing wedge rings 7 and 8 exists. The rotors lying flat due to their own weight can, in particular, reach 35 between these partial rings 7 and 8 in comparison with machines for high performance levels above the flat areas of the ring 6 at the flange values. But now, especially with turbines 3 and 4 of the machine housing, it must be inclined,
nen and compressors for gaseous working media The flanges 3 and 4 (Fig. 1) and the wedge rings 7

the clearance of the rotor in relation to the housing is possible and 8 have bores9 (Fig. 2) with uniformly small, in order to keep the gap losses small, to 40 divisions t on the circumference of a circle of screws. The same considerations apply to hy- seslo. The inclination of the flanges 3 and 4 (Fig. 1) hydraulic machines. In very few cases the housing sections 1 and 2 are against each other, but the sizes of the deflection on the housing on the one hand by turning the wedge rings 7 and 8 against each other and on the rotor on the other hand can be the same, so that it is necessary to be set on the pitch circle so that the It becomes unnecessary to increase the running play by increasing the difference between the inside diameter of the housing produced under its own weight by the difference between the deflection of the housing axis 5 and the deflection. This causes deflection of the axis of the increased gap losses caused by the housing. nen rotor 27 approaches a minimum value. These

Proposals have already become known about who-deviations can be made to setting during assembly of the circular shape of the parts of axially 50 den and needs in the later course of operation and radially divided housings can no longer be changed by inserting, as experience has shown an undivided circular ring hardly changes the housing in the radial one, e.g. as a result of To prevent separation. It is also known to cause creep of the building material. But should im the expansion of the housing of rotary piston machines, the later operation but still significant changes as a result of great differences in temperature arises, that could arise after the support of the housing to make harmless that the rotor shaft and removal of the bolts the rings against each other be moved on the bearing bodies of the rotors by means of pairs so that the minimum dimension of the wise arranged, in mutually perpendicular Rieh deflection differences between the housing and flexible intermediate links. Rotor 6 is reached again. To facilitate sol-hereby If it was possible, at least in the longitudinal 60 rather corrections it is recommended to use the wedge rings 7 by means of the machine, the rotor is designed in two parts opposite the gear and 8 and the ring halves keep the housing reasonably centered. with detachable tabs 11 and 12 (Fig. 1)

However, since the invention is contrary to that of the connect. The connection of the straps with known proposals makes it the task that the halves of the wedge rings take place, for example, by means of screw-bending form of housing and rotor 65 bolts 13 with retractable heads,
to match as possible, it also needs other solutions. 3 consists of

solvent, which consists in that at the joint of a gas turbine 20 and a compressor 21 from between the housing sections one of two on top of the supply channel 22, the compressor 21 sucks fuel