EP1707759B1 - Housing of a turbomachine - Google Patents
Housing of a turbomachine Download PDFInfo
- Publication number
- EP1707759B1 EP1707759B1 EP06111846.9A EP06111846A EP1707759B1 EP 1707759 B1 EP1707759 B1 EP 1707759B1 EP 06111846 A EP06111846 A EP 06111846A EP 1707759 B1 EP1707759 B1 EP 1707759B1
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- EP
- European Patent Office
- Prior art keywords
- housing
- bridge
- separating plane
- contact face
- shells
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- 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.)
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- 238000009826 distribution Methods 0.000 claims description 6
- 230000013011 mating Effects 0.000 description 17
- 238000005452 bending Methods 0.000 description 8
- 230000008878 coupling Effects 0.000 description 6
- 238000010168 coupling process Methods 0.000 description 6
- 238000005859 coupling reaction Methods 0.000 description 6
- 230000005540 biological transmission Effects 0.000 description 4
- 230000007246 mechanism Effects 0.000 description 4
- 238000007789 sealing Methods 0.000 description 4
- 230000000295 complement effect Effects 0.000 description 3
- 238000009434 installation Methods 0.000 description 3
- 230000008901 benefit Effects 0.000 description 2
- 230000001419 dependent effect Effects 0.000 description 2
- 238000000034 method Methods 0.000 description 2
- 230000008569 process Effects 0.000 description 2
- 241000251131 Sphyrna Species 0.000 description 1
- 230000004323 axial length Effects 0.000 description 1
- 230000015572 biosynthetic process Effects 0.000 description 1
- 230000008859 change Effects 0.000 description 1
- 150000001875 compounds Chemical class 0.000 description 1
- 230000001627 detrimental effect Effects 0.000 description 1
- 238000005755 formation reaction Methods 0.000 description 1
- 210000004907 gland Anatomy 0.000 description 1
- 230000010354 integration Effects 0.000 description 1
- 238000003754 machining Methods 0.000 description 1
- 238000005457 optimization Methods 0.000 description 1
- 230000000149 penetrating effect Effects 0.000 description 1
- 230000009467 reduction Effects 0.000 description 1
- 230000001052 transient effect Effects 0.000 description 1
Images
Classifications
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- 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
- F01D25/24—Casings; Casing parts, e.g. diaphragms, casing fastenings
- F01D25/243—Flange connections; Bolting arrangements
Definitions
- the invention relates to a housing for a turbomachine, with a first housing shell, which is connected to a second housing shell along a parting plane, which usually passes through the machine axis (s).
- At least one flange is formed in the region of the parting plane, with which the two housing shells are fastened to one another.
- this flange extends in the parting plane and forms there a broadening of the housing, which extends radially with respect to a longitudinal direction of the housing and usually extends over the entire axial length or circumference of the housing.
- the two housing shells are screwed directly to each other in the region of the flange, wherein the respective screw penetrates the parting plane preferably vertically.
- the housing shells thus have contact surfaces which extend in the parting plane, which lie along the parting plane and which are pressed against each other within the respective flange by the respective screwing.
- such a housing at least in a turbomachine, such as in a turbine or a compressor, have a rotationally symmetric or nearly rotationally symmetrical shape.
- the radially projecting flanges are a hindrance to such a housing in two respects: on the one hand, the stiffness of the flange area relative to a bending moment in the circumferential direction, for example a thermal moment due to a radial temperature gradient across the wall, locally significantly different from the rest of the circumference, second, the additional masses and the radial extent of the flanges lead to a change in the temperature behavior of the housing in the region of the flange. Both disturbances have a detrimental effect on the deformation behavior of the housing by locally different curvatures and bends occur even when circumferentially constant pressure and / or temperature load. This gives a rotationally symmetrical housing in operation a no longer circular cross-section.
- the flanges In order to keep the circumferential stiffness constant, the flanges must have a width of about 2 - 3 times the wall thickness. This is contradicted by the fact that they should ideally not protrude over the (rotational) contour of the rest of the housing for reasons of uniform thermal behavior as possible as well as reduction of the size. For these conflicting requirements, on the one hand sufficient bending stiffness in the circumferential direction and on the other hand small radial extent, can be difficult to find a satisfactory compromise with previously known design principles.
- US 2'276'603 also proposes brackets with a wedge mechanism for increasing the closing forces, similar to the aforementioned DE 853'451 , Due to the small remaining vertical contact surfaces between the clamp and the housing half, however, the circumferential stiffening is only slight. The goal is obviously only the larger closing forces, which generate the brackets in cooperation with wedge-shaped widening contact surfaces on the housing flanges.
- asymmetric deformation of the housing is problematic, especially in turbomachinery, since the housing is typically used to support vanes and sealing zones for blades.
- the flow through the turbomachine is disturbed.
- radial gaps between the blades and the housing-side sealing zones and between the guide vanes and rotor-side sealing zones can form or increase, which leads to a flow around the blades at the tip.
- the efficiency of a turbomachine however significantly reduced when the high-energy flow flows around the blades at the tip and thus does not transfer work to the respective blade.
- the invention deals with the problem of providing an improved embodiment for a housing of the aforementioned type which significantly improves in particular the dimensional stability of the housing by the circumferential stiffness in the region of the parting plane almost constant equal to Rest of the housing periphery is, and wherein at the same time the radial extent in the region of the parting plane can be largely adapted to the rest of the rotational contour of the housing.
- the invention is based on the general idea, instead of the respective particular horizontal flanges or connecting brackets to attach at least one bridge, which extends perpendicular to the parting plane and the both sides of the parting plane fixed respectively in a corresponding bridge portion with both a housing shell and with the other housing shell and bending moment rigid is connected in the circumferential direction, which is achieved by such a bridge is designed as a plate whose measured in the parting plane and in the longitudinal direction of the housing longitudinal dimension is greater than their transversely measured to the parting transverse dimension, that on both housing shells a recess is formed into which the bridge is inserted with their bridge sections, and at least one of the bridge sections is bolted to the associated housing shell.
- Such a bridge forms transversely to the parting plane an anchor which connects the two housing halves in the parting plane adjacent to each other firmly together.
- the local bending stiffness achievable with the aid of the bridge at the parting plane can be made almost ideally equal to the remainder of the circumference.
- the tensile strength of the bridge by a corresponding dimensioning and / or additional structural elements be many times greater than in a conventional screw which penetrates the flange perpendicular to the parting plane.
- the most important feature is the bending moment stiff connection in the circumferential direction while reducing the radial extent in the parting plane.
- the bridge is screwed to one of the bridge sections or to both bridge sections with the respectively associated housing half.
- the housing shells in the region of the parting plane and the respective bridge are designed so that there is an at least approximately constant mass distribution over the entire circumference of the housing.
- At least one of the bridge sections may be connected via a form-locking connection with the associated housing shell.
- Suitable form-fitting connections are, for example, a dovetail coupling, a hammerhead coupling or a clip coupling.
- a housing 1 according to the invention comprises a first housing shell 2 and a second housing shell 3.
- the two housing shells 2, 3 abut each other along a parting plane 4.
- the housing 1 is the housing 1 of a machine, preferably a turbomachine, such as a turbine, a gas turbine, a steam turbine, a compressor or a compressor.
- the housing 1 may be internally or externally loaded with an overpressure.
- the housing 1 may be thermally loaded internally or externally. Accordingly, the housing shells 2, 3 exposed to strong deformation forces.
- At least one bridge 6 is provided in the region of the parting plane 4. This bridge 6 is also exposed to particularly high loads due to the above-mentioned heavy loads of the housing 1.
- the bridge 6 can basically extend in the axial direction over the entire length of the housing 1. It is also possible to arrange several such bridges 6 in the axial direction of the housing 1 one behind the other. Furthermore, it is clear that the housing 1 in the diametrically opposite parting plane 4 can also have at least one such bridge 6.
- the bridge 6 does not lead to an asymmetrical deformation of the housing 1 due to the occurring loads, it should have substantially the same strength and stiffness values and in particular the same thermal properties (mass, wall thickness, radial extent) as the remaining area of the housing shells 2, 3 .
- This bridge 6 extends perpendicular to the parting plane 4 and is arranged so that it penetrates the parting plane 4. Accordingly, the bridge 6 has a first bridge section 7, which is located on the same side of the parting plane 4 as the first housing shell 2. Furthermore, the bridge 6 has a second bridge section 8, which, like the second housing shell 3 on the other side of Parting level 4 is located.
- the first bridge section 7 is firmly connected to the first housing shell 2.
- the second bridge section 8 is firmly connected to the second housing shell 3.
- both bridge sections 7 and 8 are screwed to the associated housing shell 2, 3.
- Corresponding fittings 9 are in Fig. 1 indicated by dash-dotted lines. The number and / or positioning and / or dimensioning of the screw 9 is selected depending on the forces and moments to be transmitted.
- an associated contact surface is provided on the respective bridge section 7, 8, namely a first contact surface 10 on the first bridge section 7 and a second contact surface 11 on the second bridge section 8.
- the first housing shell 2 has a first mating contact surface 12, while the second housing shell 3 has a second mating contact surface 13.
- the contact surfaces 10, 11 lie flat against the respective mating contact surface 12, 13.
- the connection of the bridge 6 to the housing shells 2, 3 is expediently such that the respective contact surface 10, 11 is pressed against the respective mating contact surface 12, 13. This is achieved with the variant according to Fig.
- the contact surfaces 10, 11 and the mating contact surfaces 12, 13 extend in a plane 14, which stands on the parting plane 4. In the embodiment shown here, this plane 14 is perpendicular to the parting plane 4.
- the invention includes embodiments with slightly inclined contact surfaces, in particular with the plane of symmetry of the housing mirror-inverted contact surfaces similar to a Aushebeschräge, in particular simplify the assembly and disassembly process ( Fig. 1a ).
- the bridge 6 can be particularly easily dimensioned so that the transferable tensile forces are significantly greater than tensile forces that can be transmitted by conventional glands. In addition, the moment stiffness is increased. At the same time, such a bridge 6 builds comparatively compact, whereby the outer contour of the housing 1 is not or only slightly disturbed in terms of its symmetry.
- the bridge 6 is designed as a plate.
- a plate-shaped bridge 6 is a longitudinal dimension of the bridge 6, which is measured in the parting plane 4 and in the longitudinal direction of the housing 1, larger than a transverse dimension of the bridge 6, which is measured transversely to the parting plane 4, ie along the plane 14.
- a plate-shaped bridge 6 can be anchored by a corresponding number of screw 9 with sufficient strength to the housing shells 2, 3.
- Fig. 1 the position of the plane 14 is chosen so that the bridge 6 is completely or almost completely within the rotationally symmetrical outer contour 16 of the housing 1.
- a corresponding recess 20 is formed on the two housing shells 2, 3, in which the bridge 6 is inserted with their bridge sections 7, 8.
- the contact or mating contact surfaces 10, 11 and 12, 13 are included Fig. 1 all in one plane, which may be advantageous for machining, but means relatively large bridges 6 for large housing radii.
- the size of the bridge 6 can be reduced to the degree required for the torque and power transmission by, according to Fig. 1a the contact or mating contact surfaces 10, 11 and 12, 13 no longer be left in one plane.
- the contact surfaces may indeed remain flat, but be arranged in the form of a blunt wedge or otherwise describe any mathematically continuous or discontinuous waveform, such as a circular arc.
- the design of the bridge 6 takes place in such a way that a substantially constant mass distribution results in the cross section of the housing 1 in the circumferential direction of the housing 1 over the region of the parting plane 4.
- the housing has a substantially constant bending stiffness and moreover, the same thermal properties over the entire circumference, which in the case of the loads occurring during operation of the machine, a symmetrical deformation of the housing 1 is achieved particularly easily.
- Fig. 2 shows one of the Fig. 1 very similar embodiment, but in which the bridge 6 is not completely integrated into the outer contour 16 of the housing 1, but slightly protrudes in the radial direction over the housing contour 16.
- Form-fit connections 17 are provided, by means of which the respective bridge sections 7, 8 are fixedly connected to the associated housing shells 2, 3.
- these form-locking connections 17 are each designed so that they fix the two housing shells 2, 3 along the parting plane 4 adjacent to each other. That is, the form-locking connections 17 prevent a relative movement between the two housing shells 2, 3 transversely to the parting plane. 4
- Such additional form-locking connections 17 are advantageous if, in addition to the circumferential torques, even high forces have to be transmitted. In particular, they allow to dimension the screw only according to the torque transmission - which usually only relatively small bolt requires because of the relatively large height of the contact surfaces and thus large screw distances - without having to consider surcharges because of additional shear stress of the screws.
- Fig. 3 the in Fig. 3 variant shown by a positive connection 17, which represents a clamp coupling.
- This clip coupling has the advantage that it is radially mountable with respect to the longitudinal direction of the housing 1.
- end sections 18 of the bridge 6 engage over end sections 19 of the housing shells 2, 3.
- Fig. 4 is the positive connection 17 designed in the manner of a hammer head coupling.
- the end portions 19 of the housing shells 2, 3 form undercuts which engage behind the end portions 18 of the bridge 6.
- the bridge 6 can be mounted axially.
- the screw 9 could be omitted in this type of form-locking connection 17 in principle or be further reduced, if either the positive connection about in the middle of the respective contact surfaces sets so that the moment can be transmitted by the planar support to both sides, or by taking in their place each arranges a second row of such compounds closer to the parting plane 4, so that the pairs of forces can be transmitted from the circumferential moments by suitable form-locking connections in the radial direction over the contact surfaces ( Fig. 4a ).
- FIG. 5 is the positive connection 17 formed by shear forces form-fitting contours on the contact surfaces 10, 11 and on the mating contact surfaces 12, 13.
- a detail A shows a Variant in which these form-fitting contours form a kind of toothing, wherein the respective contact surface 10 is provided with axial rows of teeth which engage in complementary rows of teeth which are formed on the mating contact surface 12.
- the detail B shows another embodiment in which the form-fitting contours are wavy.
- the respective contact surface 11 has a multiplicity of shafts which extend essentially axially and which engage in shafts which are complementary thereto and which are formed on the associated countercontact surface 13.
- the screw 9 are required to clamp the contact surfaces 10, 11 against the mating contact surfaces 12, 13.
- FIG. 6 shows Fig. 6 an embodiment in which the contact surfaces 10, 11 and the mating contact surfaces 12, 13 have a curved course and accordingly extend along a curvature.
- This curvature is concave toward the interior of the housing 1.
- this curvature extends coaxially to a curvature of the housing shells 2, 3, ie coaxially to a curvature of the housing 1 in the region of the parting plane 4.
- a recess 20 is provided, in which the bridge 6 is inserted.
- bridge 6 and recess 20 are also coordinated so that the bridge 6 is recessed in the recess and in particular within the outer contour 16 of the housing 1 extends.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
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Description
Die Erfindung betrifft ein Gehäuse für eine Turbomaschine, mit einer ersten Gehäuseschale, die entlang einer Trennebene, die meistens durch die Maschinenachse(n) geht, mit einer zweiten Gehäuseschale verbunden ist.The invention relates to a housing for a turbomachine, with a first housing shell, which is connected to a second housing shell along a parting plane, which usually passes through the machine axis (s).
Bei einem derartigen Gehäuse ist im Bereich der Trennebene zumindest ein Flansch ausgebildet, mit dem die beiden Gehäuseschalen aneinander befestigt sind. Üblicherweise erstreckt sich dieser Flansch in der Trennebene und bildet dort eine Verbreiterung des Gehäuses, die sich bezüglich einer Längsrichtung des Gehäuses radial erstreckt und meist über die gesamte axiale Länge bzw. Umfang des Gehäuses reicht. Die beiden Gehäuseschalen sind im Bereich des Flansches direkt miteinander verschraubt, wobei die jeweilige Verschraubung die Trennebene vorzugsweise senkrecht durchdringt.In such a housing at least one flange is formed in the region of the parting plane, with which the two housing shells are fastened to one another. Usually, this flange extends in the parting plane and forms there a broadening of the housing, which extends radially with respect to a longitudinal direction of the housing and usually extends over the entire axial length or circumference of the housing. The two housing shells are screwed directly to each other in the region of the flange, wherein the respective screw penetrates the parting plane preferably vertically.
Üblicherweise besitzen die Gehäuseschalen somit Kontaktflächen, die sich in der Trennebene erstrecken, die entlang der Trennebene aneinander liegen und die innerhalb des jeweiligen Flansches durch die jeweilige Verschraubung gegeneinander gepresst sind.Usually, the housing shells thus have contact surfaces which extend in the parting plane, which lie along the parting plane and which are pressed against each other within the respective flange by the respective screwing.
Des weiteren kann ein derartiges Gehäuse, zumindest bei einer Turbomaschine, wie zum Beispiel bei einer Turbine oder bei einem Kompressor, eine rotationssymmetrische oder nahezu rotationssymmetrische Form aufweisen. Die radial vorstehenden Flansche stellen für ein solches Gehäuse in zweifacher Hinsicht eine Störung dar: zum einen ist die Steifigkeit des Flanschbereichs gegenüber einem Biegemoment in Umfangsrichtung, zum Beispiel einem thermischen Moment infolge eines radialen Temperaturgradienten über die Wand, lokal deutlich unterschiedlich zum Rest des Umfangs, zum zweiten führen die zusätzlichen Massen und die radiale Erstreckung der Flansche zu einem veränderten Temperaturverhalten des Gehäuses im Bereich des Flansches. Beide Störungen wirken sich nachteilig auf das Verformungsverhalten des Gehäuses aus, indem selbst bei in Umfangsrichtung konstanter Druck- und/oder Temperaturbelastung lokal unterschiedliche Krümmungen und Verbiegungen auftreten. Dadurch bekommt ein rotationssymmetrisches Gehäuse im Betrieb einen nicht mehr kreisförmigen Querschnitt.Furthermore, such a housing, at least in a turbomachine, such as in a turbine or a compressor, have a rotationally symmetric or nearly rotationally symmetrical shape. The radially projecting flanges are a hindrance to such a housing in two respects: on the one hand, the stiffness of the flange area relative to a bending moment in the circumferential direction, for example a thermal moment due to a radial temperature gradient across the wall, locally significantly different from the rest of the circumference, second, the additional masses and the radial extent of the flanges lead to a change in the temperature behavior of the housing in the region of the flange. Both disturbances have a detrimental effect on the deformation behavior of the housing by locally different curvatures and bends occur even when circumferentially constant pressure and / or temperature load. This gives a rotationally symmetrical housing in operation a no longer circular cross-section.
Um die Umfangssteifigkeit konstant zu halten, müssen die Flansche eine Breite von ca. 2 - 3 mal der Wandstärke haben. Dem steht entgegen, dass sie aus Gründen möglichst gleichförmigen thermischen Verhaltens sowie Reduktion der Baugröße idealerweise nicht über die (Rotations-) Kontur des restlichen Gehäuses hervorragen sollten. Für diese gegensätzlichen Anforderungen, einerseits ausreichende Biegesteifigkeit in Umfangsrichtung und andererseits geringe radiale Erstreckung, lässt sich mit bisher bekannten Konstruktionsprinzipien nur schwer ein befriedigender Kompromiss finden.In order to keep the circumferential stiffness constant, the flanges must have a width of about 2 - 3 times the wall thickness. This is contradicted by the fact that they should ideally not protrude over the (rotational) contour of the rest of the housing for reasons of uniform thermal behavior as possible as well as reduction of the size. For these conflicting requirements, on the one hand sufficient bending stiffness in the circumferential direction and on the other hand small radial extent, can be difficult to find a satisfactory compromise with previously known design principles.
In dieser Beziehung stellen auch die verschiedenen bekannten Lösungen des Standes der Technik für alternative Verbindungsprinzipien von Gehäuseflanschen keine in dieser Hinsicht befriedigende Lösung dar, weil diese hauptsächlich das Ziel einer Vergrößerung der Schließkräfte, teilweise um den Preis einer geringeren Umfangssteifigkeit und ohne Rücksicht auf den notwendigen Einbauraum haben.In this regard, the various known solutions of the prior art for alternative connection principles of housing flanges not a satisfactory solution in this respect, because they have mainly the goal of increasing the closing forces, partly at the cost of a lower circumferential rigidity and without regard to the necessary installation space.
So beschreibt
Ein alternativer Vorschlag mit einem ähnlichen Ziel ist Gegenstand der Schweizer Schrift
US 2'276'603 schlägt ebenfalls Klammern mit einem Keilmechanismus zur Erhöhung der Schließkräfte vor, ähnlich vorgenannter
Bei der Lösung gemäss
In the solution according to
Insgesamt ist festzustellen, dass die hier vorgestellten Lösungen in erster Linie auf eine Abdichtung der Gehäuseschalen und die Erzeugung hoher Schliesskräfte gerichtet sind, die Problematik der Umfangssteifigkeit und Massenverteilung und der Gefahr einer asymmetrischen Deformation jedoch ausser Acht lassen.
Dies hat die zwangsläufige Folge, dass eine hohe Biegesteifigkeit in Umfangsrichtung bei möglichst gleichmäßiger Massenverteilung im Flanschbereich zur Gewährleistung höchstmöglicher Rotationssymmetrie bei hoher mechanischer und thermischer Belastbarkeit nach diesen Lösungen nicht erreicht wird.Overall, it should be noted that the solutions presented here are directed primarily to a sealing of the housing shells and the generation of high closing forces, the problems of circumferential rigidity and mass distribution and the risk of asymmetric deformation but ignore.
This has the inevitable consequence that a high flexural rigidity in the circumferential direction with a uniform mass distribution in the flange area to ensure the highest possible rotational symmetry at high mechanical and thermal capacity is not achieved by these solutions.
Aber gerade bei Turbomaschinen ist eine asymmetrische Deformation des Gehäuses problematisch, da das Gehäuse in der Regel dazu dient, Leitschaufeln und Dichtzonen für Laufschaufeln zu tragen. Durch eine asymmetrische Deformation des Gehäuses wird die Durchströmung der Turbomaschine gestört. Insbesondere können sich Radialspalte zwischen den Laufschaufeln und den gehäuseseitigen Dichtzonen sowie zwischen den Leitschaufeln und rotorseitigen Dichtzonen bilden bzw. vergrößern, was zu einer Umströmung der Schaufeln an deren Spitze führt. Der Wirkungsgrad einer Strömungsmaschine wird jedoch signifikant reduziert, wenn die energiereiche Strömung die Schaufeln an deren Spitze umströmt und dadurch keine Arbeit auf die jeweilige Schaufel überträgt.But asymmetric deformation of the housing is problematic, especially in turbomachinery, since the housing is typically used to support vanes and sealing zones for blades. By an asymmetric deformation of the housing, the flow through the turbomachine is disturbed. In particular, radial gaps between the blades and the housing-side sealing zones and between the guide vanes and rotor-side sealing zones can form or increase, which leads to a flow around the blades at the tip. The efficiency of a turbomachine, however significantly reduced when the high-energy flow flows around the blades at the tip and thus does not transfer work to the respective blade.
Hier setzt die Erfindung an. Die Erfindung, wie sie in den Ansprüchen gekennzeichnet ist, beschäftigt sich mit dem Problem, für ein Gehäuse der eingangs genannten Art eine verbesserte Ausführungsform anzugeben, die insbesondere die Formstabilität des Gehäuses signifikant verbessert, indem die Umfangssteifigkeit auch im Bereich der Trennebene nahezu konstant gleich dem Rest des Gehäuseumfangs ist, und wobei gleichzeitig die radiale Erstreckung im Bereich der Trennebene weitgehend der übrigen Rotationskontur des Gehäuses angepasst werden kann.This is where the invention starts. The invention, as characterized in the claims, deals with the problem of providing an improved embodiment for a housing of the aforementioned type which significantly improves in particular the dimensional stability of the housing by the circumferential stiffness in the region of the parting plane almost constant equal to Rest of the housing periphery is, and wherein at the same time the radial extent in the region of the parting plane can be largely adapted to the rest of the rotational contour of the housing.
Erfindungsgemäß wird dieses Problem durch den Gegenstand des unabhängigen Anspruchs gelöst. Vorteilhafte Ausführungsformen sind Gegenstand der abhängigen Ansprüche.According to the invention, this problem is solved by the subject matter of the independent claim. Advantageous embodiments are the subject of the dependent claims.
Die Erfindung beruht auf dem allgemeinen Gedanken, anstelle der jeweiligen insbesondere horizontalen Flansche oder verbindender Klammern wenigstens eine Brücke anzubringen, die sich senkrecht zur Trennebene erstreckt und die beiderseits der Trennebene jeweils in einem entsprechenden Brückenabschnitt sowohl mit der einen Gehäuseschale als auch mit der anderen Gehäuseschale fest und biegemomentsteif in Umfangsrichtung verbunden ist, welches erreicht wird, indem eine solche Brücke als Platte ausgestaltet ist, deren in der Trennebene und in der Längsrichtung des Gehäuses gemessene Längsabmessung größer ist als deren quer zur Trennebene gemessene Querabmessung, dass an beiden Gehäuseschalen eine Aussparung ausgebildet ist, in welche die Brücke mit ihren Brückenabschnitten eingesetzt ist, und zumindest einer der Brückenabschnitte mit der zugehörigen Gehäuseschale verschraubt ist.
Eine derartige Brücke bildet quer zur Trennebene einen Anker, der die beiden Gehäusehälften in der Trennebene aneinander anliegend fest miteinander verbindet. Dabei kann die mit Hilfe der Brücke erzielbare lokale Biegesteifigkeit an der Trennebene nahezu ideal gleich dem Rest des Umfangs gemacht werden. Zusätzlich kann erforderlichenfalls die Zugfestigkeit der Brücke durch eine entsprechende Dimensionierung und/oder zusätzliche Konstruktionselemente um ein Vielfaches größer sein als bei einer herkömmlichen Verschraubung, welche den Flansch senkrecht zur Trennebene durchdringt.
Das wichtigste Merkmal ist jedoch die biegemomentsteife Verbindung in Umfangsrichtung bei gleichzeitiger Reduktion der radialen Erstreckung in der Trennebene.
Die Brücke ist an einem der Brückenabschnitte oder an beiden Brückenabschnitten mit der jeweils zugehörigen Gehäusehälfte verschraubt. Mit Hilfe einer derartigen Verschraubung kann durch eine geeignete Auswahl der Schraubstellen hinsichtlich Positionierung und/oder Anzahl und/oder Dimensionierung eine besonders hohe Biegesteifigkeit und nötigenfalls auch Festigkeit für die jeweilige Verbindung zwischen der jeweiligen Gehäuseschale und dem jeweiligen Brückenabschnitt hergestellt werden.The invention is based on the general idea, instead of the respective particular horizontal flanges or connecting brackets to attach at least one bridge, which extends perpendicular to the parting plane and the both sides of the parting plane fixed respectively in a corresponding bridge portion with both a housing shell and with the other housing shell and bending moment rigid is connected in the circumferential direction, which is achieved by such a bridge is designed as a plate whose measured in the parting plane and in the longitudinal direction of the housing longitudinal dimension is greater than their transversely measured to the parting transverse dimension, that on both housing shells a recess is formed into which the bridge is inserted with their bridge sections, and at least one of the bridge sections is bolted to the associated housing shell.
Such a bridge forms transversely to the parting plane an anchor which connects the two housing halves in the parting plane adjacent to each other firmly together. In this case, the local bending stiffness achievable with the aid of the bridge at the parting plane can be made almost ideally equal to the remainder of the circumference. In addition, if necessary, the tensile strength of the bridge by a corresponding dimensioning and / or additional structural elements be many times greater than in a conventional screw which penetrates the flange perpendicular to the parting plane.
However, the most important feature is the bending moment stiff connection in the circumferential direction while reducing the radial extent in the parting plane.
The bridge is screwed to one of the bridge sections or to both bridge sections with the respectively associated housing half. With the help of such a screw connection can be made by a suitable selection of the screw locations with respect to positioning and / or number and / or dimensioning a particularly high bending stiffness and, if necessary, strength for the respective connection between the respective housing shell and the respective bridge section.
Nach einer bevorzugten Ausführungsart sind die Gehäuseschalen im Bereich der Trennebene und die jeweilige Brücke so ausgelegt sind, dass sich über den gesamten Gehäuseumfang hinweg eine wenigstens annähernd konstante Massenverteilung ergibt.According to a preferred embodiment, the housing shells in the region of the parting plane and the respective bridge are designed so that there is an at least approximately constant mass distribution over the entire circumference of the housing.
Zusätzlich kann zumindest einer der Brückenabschnitte über eine Formschlussverbindung mit der zugehörigen Gehäuseschale verbunden sein. Geeignete Formschlussverbindungen sind beispielsweise eine Schwalbenschwanz-Kupplung, eine Hammerkopf-Kupplung oder eine Klammer-Kupplung. Durch Formschluss lassen sich besonders hohe Momente und Kräfte direkt zwischen der Brücke und der jeweiligen Gehäuseschale übertragen.In addition, at least one of the bridge sections may be connected via a form-locking connection with the associated housing shell. Suitable form-fitting connections are, for example, a dovetail coupling, a hammerhead coupling or a clip coupling. By Form fit can be particularly high moments and forces transmitted directly between the bridge and the respective housing shell.
Weitere wichtige Merkmale und Vorteile des erfindungsgemäßen Gehäuses ergeben sich aus den abhängigen Ansprüchen, aus den Zeichnungen und aus der zugehörigen Figurenbeschreibung anhand der Zeichnungen.Further important features and advantages of the housing according to the invention will become apparent from the dependent claims, from the drawings and from the associated figure description with reference to the drawings.
Bevorzugte Ausführungsbeispiele der Erfindung sind in den Zeichnungen dargestellt und werden in der nachfolgenden Beschreibung näher erläutert, wobei sich gleiche Bezugszeichen auf gleiche oder ähnliche oder funktional gleiche Komponenten beziehen. Es zeigen, jeweils schematisch,
- Fig. 1 bis 6
- jeweils einen Querschnitt durch ein erfindungsgemäßes Gehäuse im Bereich der Trennebene der Gehäuseschalen bei unterschiedlichen Ausführungsformen.
- Fig. 1 to 6
- in each case a cross section through an inventive housing in the region of the parting plane of the housing shells in different embodiments.
Entsprechend den
Um die beiden Gehäuseschalen 2, 3 aneinander zu befestigen, ist im Bereich der Trennebene 4 zumindest eine Brücke 6 vorgesehen. Diese Brücke 6 ist aufgrund der oben genannten starken Belastungen des Gehäuses 1 ebenfalls besonders hohen Belastungen ausgesetzt. Die Brücke 6 kann sich grundsätzlich in axialer Richtung über die gesamte Länge des Gehäuses 1 erstrecken. Ebenso ist es möglich, mehrere solcher Brücken 6 in der Achsrichtung des Gehäuses 1 hintereinander anzuordnen. Des Weiteren ist klar, dass das Gehäuse 1 in der diametral gegenüberliegenden Trennebene 4 ebenfalls zumindest eine solche Brücke 6 aufweisen kann.
Damit die Brücke 6 aufgrund der auftretenden Belastungen nicht zu einer unsymmetrischen Deformation des Gehäuses 1 führt, sollte sie im wesentlichen dieselben Festigkeits- und Steifigkeitswerte und insbesondere dieselben thermischen Eigenschaften (Masse, Wandstärke, radiale Erstreckung) wie der übrige Bereich der Gehäuseschalen 2, 3 aufweisen.
Diese Brücke 6 erstreckt sich senkrecht zur Trennebene 4 und ist so angeordnet, dass sie die Trennebene 4 durchdringt. Dementsprechend weist die Brücke 6 einen ersten Brückenabschnitt 7 auf, der sich auf derselben Seite der Trennebene 4 befindet wie die erste Gehäuseschale 2. Des Weiteren weist die Brücke 6 einen zweiten Brückenabschnitt 8 auf, der sich wie die zweite Gehäuseschale 3 auf der anderen Seite der Trennebene 4 befindet. Der erste Brückenabschnitt 7 ist mit der ersten Gehäuseschale 2 fest verbunden. Der zweite Brückenabschnitt 8 ist mit der zweiten Gehäuseschale 3 fest verbunden.In order to fasten the two
So that the
This
Bei der Ausführungsform gemäß
Um besonders hohe Momente und auch Kräfte zwischen der Brücke 6 und den Gehäuseschalen 2, 3 übertragen zu können, ist am jeweiligen Brückenabschnitt 7, 8 eine zugehörige Kontaktfläche vorgesehen, nämlich eine erste Kontaktfläche 10 am ersten Brückenabschnitt 7 und eine zweite Kontaktfläche 11 am zweiten Brückenabschnitt 8. Komplementär dazu weist die erste Gehäuseschale 2 eine erste Gegenkontaktfläche 12 auf, während die zweite Gehäuseschale 3 eine zweite Gegenkontaktfläche 13 besitzt. Im montierten Zustand liegen die Kontaktflächen 10, 11 an der jeweiligen Gegenkontaktfläche 12, 13 flächig an. Die Anbindung der Brücke 6 an die Gehäuseschalen 2, 3 erfolgt zweckmäßig so, dass die jeweilige Kontaktfläche 10, 11 gegen die jeweilige Gegenkontaktfläche 12, 13 angepresst ist. Erreicht wird dies bei der Variante gemäß
Bei der hier gezeigten Ausführungsform erstrecken sich die Kontaktflächen 10, 11 und die Gegenkontaktflächen 12, 13 in einer Ebene 14, die auf der Trennebene 4 steht. Bei der hier gezeigten Ausführungsform steht diese Ebene 14 senkrecht auf der Trennebene 4. Erfindungsgemäß mit eingeschlossen sind Ausführungsformen mit leicht schrägstehenden Kontaktflächen, insbesondere mit zur Symmetrieebene des Gehäuses spiegelbildlich schrägstehenden Kontaktflächen ähnlich einer Aushebeschräge, die insbesondere den Montage- und Demontagevorgang vereinfachen (
Die Brücke 6 kann besonders einfach so dimensioniert werden, dass die damit übertragbaren Zugkräfte erheblich größer sind als Zugkräfte, die mittels konventioneller Verschraubungen übertragen werden können. Zusätzlich wird die Momentsteifigkeit erhöht. Gleichzeitig baut eine derartige Brücke 6 vergleichsweise kompakt, wodurch die Außenkontur des Gehäuses 1 hinsichtlich seiner Symmetrie nicht oder nur geringfügig gestört wird.The
Die Brücke 6 ist als Platte ausgestaltet. Bei einer plattenförmigen Brücke 6 ist eine Längsabmessung der Brücke 6, die in der Trennebene 4 und in der Längsrichtung des Gehäuses 1 gemessen ist, größer als eine Querabmessung der Brücke 6, die quer zur Trennebene 4, also entlang der Ebene 14 gemessen ist. Eine plattenförmige Brücke 6 lässt sich durch eine entsprechende Anzahl von Verschraubungen 9 mit hinreichender Festigkeit an den Gehäuseschalen 2, 3 verankern.The
Entsprechend
Vorzugsweise erfolgt die Auslegung der Brücke 6 so, dass sich im Querschnitt des Gehäuses 1 in der Umfangsrichtung des Gehäuses 1 über den Bereich der Trennebene 4 hinweg eine im Wesentlichen konstante Massenverteilung ergibt. Auf diese Weise besitzt das Gehäuse eine weitgehend konstante Biegesteifigkeit und darüber hinaus im W esentlichen dieselben thermischen Eigenschaften über den gesamten Umfang, wodurch bei den im Betrieb der Maschine auftretenden Belastungen eine symmetrische Verformung des Gehäuses 1 besonders einfach erreicht wird.Preferably, the design of the
Bei den Ausführungsformen der
Solche zusätzlichen Formschlussverbindungen 17 sind von Vorteil, wenn neben den Umfangsmomenten auch noch hohe Kräfte zu übertragen sind. Insbesondere erlauben sie, die Verschraubung nur entsprechend der Momentübertragung zu dimensionieren - was wegen der relativ großen Höhe der Kontaktflächen und damit großen Schraubenabstände meist nur relativ kleine Bolzen erfordert - ohne Zuschläge wegen zusätzlicher Scherbelastung der Schrauben berücksichtigen zu müssen.Such additional form-locking
Im Einzelnen handelt es sich bei der in
Bei der Ausführungsform gemäß
Die Verschraubungen 9 könnten bei dieser Art Formschlussverbindung 17 grundsätzlich entfallen oder weiter reduziert werden, wenn man entweder die Formschlussverbindung etwa in die Mitte der jeweiligen Kontaktflächen legt, damit das Moment durch die flächige Abstützung zu beiden Seiten übertragen werden kann, oder indem man an ihrer Stelle jeweils eine zweite Reihe solcher Verbindungen näher an der Trennebene 4 anordnet, damit auch die Kräftepaare aus den Umfangsmomenten durch geeignete Formschlussverbindungen in radialer Richtung über die Kontaktflächen übertragen werden können (
The
Bei der Ausführungsform gemäß
Dabei ist klar, dass die in
Während bei den Ausführungsformen der
- 11
- Gehäusecasing
- 22
- erste Gehäuseschalefirst housing shell
- 33
- zweite Gehäuseschalesecond housing shell
- 44
- Trennebeneparting plane
- 55
- Flanschflange
- 66
- Brückebridge
- 77
- erster Brückenabschnittfirst bridge section
- 88th
- zweiter Brückenabschnittsecond bridge section
- 99
- Verschraubungscrew
- 1010
- erste Kontaktflächefirst contact surface
- 1111
- zweite Kontaktflächesecond contact surface
- 1212
- erste Gegenkontaktflächefirst mating contact surface
- 1313
- zweite Gegenkontaktflächesecond mating contact surface
- 1414
- Ebenelevel
- 1515
- Verschraubungscrew
- 1616
- Außenkonturouter contour
- 1717
- FormschlussverbindungPositive connection
- 1818
- Endabschnitt von 6End section of 6
- 1919
- Endabschnitt von 2 bzw. 3End section of 2 or 3
- 2020
- Aussparungrecess
Claims (7)
- Housing of a turbomachine,
with a first housing shell (2) which bears on a second housing shell (3) along a separating plane (4), and the two housing shells (2, 3) are attached to each other in the region of the separating plane (4),
wherein at least one bridge (6) is arranged in the region of the separating plane (4) and extends transversely to the separating plane (4) and, on the one side of the separating plane (4), is fixedly connected in a first bridge portion (7) to the first housing shell (2) and, on the other side of the separating plane (4), in a second bridge portion (8) to the second housing shell (3), and
a contact face (10, 11) is formed on at least one of the bridge portions (7, 8), via which the bridge portion (7, 8) bears broadly on a counter contact face (12, 13) formed on the associated housing shell (2, 3),
wherein the bridge (6) is configured as a plate, the length dimension of which measured in the separating plane (4) and in the longitudinal direction of the housing (1) is greater then its transverse dimension measured transversely to the separating plane (4),
wherein a recess (20) is formed on both housing shells (7, 8), in which recess the bridge (6) is inserted with its bridge portions (7, 8), and
wherein at least one of the bridge portions (7, 8) is screwed to the associated housing shell (2, 3),
characterised in that
the recess (20) is formed such that the bridge (6) is situated at least partially inside the rotationally symmetrical outer contour of the housing (1). - Housing according to claim 1, characterised in that in the region of the separating plane (4) and the respective bridge (6), the housing shells (2, 3) are configured such that an at least approximately constant mass distribution results over the entire housing periphery.
- Housing according to claim 1, characterised in that at least one of the bridge portions (7, 8) is connected to the associated housing shell (2, 3) via a form-fit connection (17).
- Housing according to claim 1, characterised in that at least one of the bridge portions (7, 8) runs inside a cylindrical outer contour (16) of the housing (1).
- Housing according to claim 1, characterised in that the bridge (6) is connected to the housing shells (2, 3) such that the respective contact face (10, 11) is pressed against the associated counter contact face (12, 13), and the respective contact face (10, 11) and/or the associated counter contact face (12, 13) has/have a surface with increased coefficient of friction.
- Housing according to claim 1, characterised in that the respective contact face (10, 11) and the associated counter contact face (12, 13) extend along a curvature which is concave towards the interior of the housing (1) and extends coaxially to a curvature of the housing shells (2, 3) in the region of the separating plane (4).
- Housing according to any of claims 1 to 6, characterised in that the two housing shells (2, 3) are attached to each other in the region of the separating plane (4) exclusively via the respective bridge (6).
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102005015150A DE102005015150A1 (en) | 2005-03-31 | 2005-03-31 | machine housing |
Publications (3)
Publication Number | Publication Date |
---|---|
EP1707759A2 EP1707759A2 (en) | 2006-10-04 |
EP1707759A3 EP1707759A3 (en) | 2011-10-26 |
EP1707759B1 true EP1707759B1 (en) | 2018-09-26 |
Family
ID=36121305
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP06111846.9A Not-in-force EP1707759B1 (en) | 2005-03-31 | 2006-03-28 | Housing of a turbomachine |
Country Status (4)
Country | Link |
---|---|
US (1) | US20060269393A1 (en) |
EP (1) | EP1707759B1 (en) |
CN (1) | CN1840956B (en) |
DE (1) | DE102005015150A1 (en) |
Families Citing this family (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP2096272A1 (en) | 2008-02-27 | 2009-09-02 | Siemens Aktiengesellschaft | Partitioned turbo engine casing with optimised partial joint flange |
EP2096273A1 (en) * | 2008-02-28 | 2009-09-02 | Siemens Aktiengesellschaft | Tubular casing for a section of turbomachine housing |
CH705190A1 (en) * | 2011-06-21 | 2012-12-31 | Alstom Technology Ltd | Pressure housing for carrying e.g. guide vanes of turbo-machine, has housing shells sealingly pressed against each other in separation plane by clamp, which is screwed with housing such that clamp transfers bending torques between shells |
JP5984618B2 (en) * | 2012-10-18 | 2016-09-06 | 三菱日立パワーシステムズ株式会社 | Turbine casing, turbine and casing assembling method |
JP6099474B2 (en) * | 2013-01-23 | 2017-03-22 | 三菱重工業株式会社 | Cabin, rotating machine, car assembly method |
DE102015213257A1 (en) * | 2015-07-15 | 2017-01-19 | Siemens Aktiengesellschaft | Abdampfgehäuse for a turbine, turbine frame, turbine housing and mounting system |
DE102016107119A1 (en) * | 2016-04-18 | 2017-10-19 | Man Diesel & Turbo Se | Turbomachinery housing |
DE102019214917A1 (en) * | 2019-09-27 | 2021-04-01 | Continental Teves Ag & Co. Ohg | Manufactured-optimized housing for a hydraulic unit to generate brake pressure for a hydraulic brake system |
Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US6506018B1 (en) * | 1999-01-25 | 2003-01-14 | Elliott Turbomachinery Co., Inc. | Casing design for rotating machinery and method for manufacture thereof |
Family Cites Families (17)
Publication number | Priority date | Publication date | Assignee | Title |
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US1957699A (en) * | 1930-04-25 | 1934-05-08 | Allis Chalmers Mfg Co | Flange connection |
US2169092A (en) * | 1937-09-11 | 1939-08-08 | Gen Electric | Turbine-casing joint |
US2276603A (en) * | 1938-11-04 | 1942-03-17 | Parsons C A & Co Ltd | Butt-jointing device |
US2311434A (en) * | 1941-11-01 | 1943-02-16 | Century Motors Corp | Connection |
US2457073A (en) * | 1946-11-07 | 1948-12-21 | Westinghouse Electric Corp | Turbine cylinder joint |
DE853451C (en) * | 1950-05-28 | 1952-10-23 | Brown | Flange connection on pressure vessels, especially on the housings of steam and gas turbines |
CH319355A (en) * | 1952-05-08 | 1957-02-15 | Parsons & Marine Eng Turbine | Flange connection for turbine housing |
US3014741A (en) * | 1957-12-06 | 1961-12-26 | Gen Motors Corp | Multi-member joint |
DE1056624B (en) * | 1958-07-11 | 1959-05-06 | Licentia Gmbh | Axial turbine housing divided in one or more axial planes |
US3914741A (en) | 1973-11-01 | 1975-10-21 | Bell Telephone Labor Inc | Fault detection arrangement for digital transmission system |
DE2715639C2 (en) * | 1977-04-07 | 1979-06-07 | Gelenkwellenbau Gmbh, 4300 Essen | PTO shaft |
US4208774A (en) * | 1978-11-27 | 1980-06-24 | United Technologies Corporation | Process for welding flanges to a cylindrical engine casing having a plurality of spaced rails and ribs |
US4411134A (en) * | 1981-10-26 | 1983-10-25 | Moir David L | Apparatus for the repair and replacement of transition ducts on jet engines and bracket therefor |
CN1143946C (en) * | 1997-09-26 | 2004-03-31 | 西门子公司 | Housing for blade mechanism |
EP1022439B1 (en) * | 1999-01-20 | 2004-05-06 | ALSTOM Technology Ltd | Steam or gas turbine casing |
JP2001107922A (en) * | 1999-10-08 | 2001-04-17 | Mitsubishi Heavy Ind Ltd | Fastening structure of flangeless casing |
GB0117550D0 (en) * | 2001-07-19 | 2001-09-12 | Rolls Royce Plc | Joint arrangement |
-
2005
- 2005-03-31 DE DE102005015150A patent/DE102005015150A1/en not_active Withdrawn
-
2006
- 2006-03-28 EP EP06111846.9A patent/EP1707759B1/en not_active Not-in-force
- 2006-03-29 US US11/277,781 patent/US20060269393A1/en not_active Abandoned
- 2006-03-31 CN CN200610079443XA patent/CN1840956B/en not_active Expired - Fee Related
Patent Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US6506018B1 (en) * | 1999-01-25 | 2003-01-14 | Elliott Turbomachinery Co., Inc. | Casing design for rotating machinery and method for manufacture thereof |
Also Published As
Publication number | Publication date |
---|---|
US20060269393A1 (en) | 2006-11-30 |
DE102005015150A1 (en) | 2006-10-05 |
EP1707759A3 (en) | 2011-10-26 |
CN1840956B (en) | 2012-11-14 |
EP1707759A2 (en) | 2006-10-04 |
CN1840956A (en) | 2006-10-04 |
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