EP1965035B1 - Minimisation of the axial gap for adjustable guide vanes and for a contour ring for hot gas expanders - Google Patents

Minimisation of the axial gap for adjustable guide vanes and for a contour ring for hot gas expanders Download PDF

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Publication number
EP1965035B1
EP1965035B1 EP07004385.6A EP07004385A EP1965035B1 EP 1965035 B1 EP1965035 B1 EP 1965035B1 EP 07004385 A EP07004385 A EP 07004385A EP 1965035 B1 EP1965035 B1 EP 1965035B1
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EP
European Patent Office
Prior art keywords
flow machine
machine according
guide vanes
contour ring
spacer
Prior art date
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Active
Application number
EP07004385.6A
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German (de)
French (fr)
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EP1965035A1 (en
Inventor
Vinko Mikulec
Martin WÜLLER
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Siemens AG
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Siemens AG
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Priority to EP07004385.6A priority Critical patent/EP1965035B1/en
Priority to CN200810082140.2A priority patent/CN101255804B/en
Publication of EP1965035A1 publication Critical patent/EP1965035A1/en
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Publication of EP1965035B1 publication Critical patent/EP1965035B1/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
    • F01D11/00—Preventing or minimising internal leakage of working-fluid, e.g. between stages
    • F01D11/005—Sealing means between non relatively rotating elements
    • 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
    • F01D11/08—Preventing or minimising internal leakage of working-fluid, e.g. between stages for sealing space between rotor blade tips and stator
    • F01D11/14—Adjusting or regulating tip-clearance, i.e. distance between rotor-blade tips and stator casing
    • F01D11/20—Actively adjusting tip-clearance
    • F01D11/22—Actively adjusting tip-clearance by mechanically actuating the stator or rotor components, e.g. moving shroud sections relative to the rotor
    • 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
    • F01D17/00—Regulating or controlling by varying flow
    • F01D17/10—Final actuators
    • F01D17/12—Final actuators arranged in stator parts
    • F01D17/14—Final actuators arranged in stator parts varying effective cross-sectional area of nozzles or guide conduits
    • F01D17/16—Final actuators arranged in stator parts varying effective cross-sectional area of nozzles or guide conduits by means of nozzle vanes
    • F01D17/165—Final actuators arranged in stator parts varying effective cross-sectional area of nozzles or guide conduits by means of nozzle vanes for radial flow, i.e. the vanes turning around axes which are essentially parallel to the rotor centre line
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2220/00—Application
    • F05D2220/40—Application in turbochargers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2230/00—Manufacture
    • F05D2230/60—Assembly methods
    • F05D2230/64—Assembly methods using positioning or alignment devices for aligning or centring, e.g. pins
    • F05D2230/642—Assembly methods using positioning or alignment devices for aligning or centring, e.g. pins using maintaining alignment while permitting differential dilatation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2260/00—Function
    • F05D2260/50—Kinematic linkage, i.e. transmission of position
    • F05D2260/52—Kinematic linkage, i.e. transmission of position involving springs

Definitions

  • the EP 1 620 633 B1 discloses a radial expansion hot gas expander having an adjustable inlet guide vane in which the adjustable vanes are held in a defined position by a resilient member in which the resilient member biases the vanes in the direction of the respective axis of rotation. From the JP 02 22 36 06 It is also known to reduce secondary flows of a centrifugal compressor in the region of exit from the impeller, in which an actuator displaces the wall opposite the impeller in the direction of minimizing the gap.
  • Turbomachines such as gear machines, in particular hot gas expander of the type mentioned are characterized by a multi-shaft arrangement with different rotational speeds to a central drive wheel. This provides a compact unit for multi-stage compaction / expansion for a variety of media, preferably gaseous media.
  • Such gear machines expand the medium having an inlet temperature of up to 300 ° C or, in a preferred embodiment, an inlet temperature of over 300 ° C can have.
  • an inlet temperature of over 300 ° C can have.
  • At a media inlet temperature of more than 300 ° C one speaks of so-called hot gas expanders.
  • H facedgasexpander have at least one inlet housing, in which the spiral insert is arranged.
  • the spiral insert carries an adjustable milieusleitapparat having a collar, vanes and bolts, wherein the bolts serve as a rotation axis for adjusting the vanes.
  • the guide vanes are therefore rotatably struck on the bolt, wherein the guide vanes are simultaneously connected via a driver with the adjusting ring. If now the adjusting ring is rotated in a desired angular amount, the drivers cause a forced adjustment of the guide vanes about the bolt, so that the adjustment of the guide vanes influencing the direction and / or the speed of the medium flow to the blade or the impeller is effected.
  • the spiral insert thus has two functions. On the one hand, the spiral insert carries the adjusting mechanism (adjusting ring, etc.), with the spiral insert on the other also carries the contour ring.
  • the spiral insert with the associated inlet guide and the contour ring is pre-assembled outside of the inlet housing and used as a unit in this.
  • the unit to be used must therefore be performed during assembly with a relatively large radial clearance to the inlet housing or the impeller to clamps by different thermal expansions to avoid and to ensure axial freedom of movement.
  • the contouring gap between the contour ring surface and the corresponding blade edge of the impeller is sized so large that the efficiency of the hot gas expander is significantly reduced by extremely high gap losses. Efficiency losses can also occur if the gaps between the guide vanes or the bolt (as the axis of rotation of the respective vane) and the associated channel inner wall are too large.
  • the invention is therefore based on the object to improve a turbomachine of the type mentioned, in particular a hot gas expander, by simple means to the effect that the gap losses are reduced, so that the efficiency can be significantly increased.
  • the object is achieved in that the specimensleitapparat and the contour ring are clamped together by means of at least one elastic element against the housing, so that the clamping forces from the elastic element in the direction of a reduction of gaps between the blades and the contour ring act.
  • the flow contour or an associated spiral insert is movable to the inlet housing or to the housing, wherein the spiral insert is preferably seen in the axial direction movable.
  • the diffuser side is assigned in each case a plant, wherein the respective receiving bolt is assigned a respective stop element on the spiral insert side, each of which is fixed frictionally to the respective locating bolt, wherein the respective locating bolt an energy storage and an active element is assigned.
  • the active element is preferably arranged on the spiral insert side, the force accumulator being arranged between the active element and the contact base.
  • the energy storage is designed as a plate spring package or cup spring ring, which is arranged around the receiving bolt around.
  • the active element is provided with pot-like holes.
  • a corresponding to the receiving pin through hole is introduced, so that the active element is slidably mounted along a longitudinal axis of the receiving pin.
  • the stop element acts as a kind of movement limiter of the active element in the direction of the spiral insert.
  • the active element is in the tensioned state preferably on the spiral insert.
  • the inlet guide apparatus has a spacer which is accommodated in the spiral insert on the foot side and is oriented on the head side to a channel inner wall, wherein the clamping system presses the spacer with its head side against the channel inner wall, which at least partially has a sliding element.
  • the specimensleitapparat also has a collar and vanes. The vanes are connected via drivers with the adjusting ring, and rotatably associated with the spacer.
  • the spacer can thus also be referred to as a guide blade bolt and serves as a rotation axis of the guide vanes.
  • the vanes over the drivers are forcibly taken with them and turn around the respective blade axis or around the respective spacer.
  • each spacer is associated with a sliding element, so that the respective sliding elements are arranged at the location assigned to the spacer in the channel inner wall. Of course, but also a single, continuous sliding element may be provided.
  • the sliding element is used as a sliding plate in the channel inner wall sufficiently secure.
  • the sliding element can also be designed as a sliding coating.
  • the sliding element in its embodiment as a sliding plate is formed of a suitable material, which is preferably made of a temperature and corrosion-resistant base material, and is coated or treated accordingly.
  • the sliding elements or sliding plates made of steel or Inconel and be coated with a special layer (eg Tribaloy).
  • the coating is preferably chosen such that a sliding friction coefficient is reduced, and at the same time a high wear resistance is present.
  • the coating also prevents seizing and is corrosion resistant.
  • a treatment by Kolsterizing ® corrosion-resistant surface hardening
  • the slider may be applied in the embodiment as a sliding coating according to the coating directly on the associated region of the channel inner wall.
  • the spiral insert is pre-assembled with the inlet guide outside the inlet housing and inserted into this as a unit.
  • the spiral insert is pressed with suitable tools axially over the spacers (Leitschaufelbolzen) against the sliding plates in the inlet housing rear wall (channel inner wall), whereby then the contour ring is installed and adjusted (axial gap).
  • the clamping system is used at the intended location.
  • the diffuser is connected to the inlet housing, or screwed, the diffuser with its abutment flange abuts the plant foot. By connecting or screwing the diffuser with the inlet housing, the clamping system is biased.
  • the clamping system in particular the cup spring assembly is designed prior to assembly with respect to the required spring tension even under operating conditions.
  • the respective components spiral insert, inlet guide, contour ring
  • the clamping system presses the spacers with their head side against the corresponding sliding element or the preferred sliding plate.
  • sliding in the radial direction is advantageously achieved, since the spacers are supported on the sliding elements.
  • thermal expansion advantageous axial compression of the disc springs.
  • the H thoroughlygasexpander also has the impeller, which is spaced with its blade edges to the contour ring, so that a contouring gap is formed.
  • this contouring gap can be advantageously minimized, since the temperature expansion acts directly on the spacer, which is supported on the channel inner wall or the respective sliding element, and pushes the contour ring away from the impeller in a thermally induced expansion, so that the thermal Expansion of the blades and the contour ring quasi picks up.
  • gap losses are reduced, as a result of which the efficiency of the turbomachine or of the geared machine or of the exemplary one Hot gas expander is increased.
  • the gap dimensions can be performed minimally from the outset, whereby it is achieved by means of the clamping system that the thermal expansion is virtually compensated.
  • FIG. 1 shows a turbomachine or a gear machine, which is designed in the illustrated embodiment as a hot gas expander 1 with an inlet temperature of a preferably gaseous medium of up to 510 ° C.
  • the hot gas expander 1 has at least one inlet housing 2, in which a spiral insert 3 is arranged.
  • the spiral insert 3 is assigned an inlet guide 4 and a contour ring 6, so that a flow contour is formed.
  • the inlet housing 2 is further associated with a diffuser 7.
  • the inlet guide 4 has an adjusting ring 8, at least one spacer 9 and vanes 11.
  • the guide vanes 11 are connected via drivers with the adjusting ring 8, so that a rotation of the adjusting ring 8 causes a corresponding adjustment of the guide vanes 11 which are rotatably mounted on the spacers 9.
  • the spacers 9 thus serve as the axis of rotation of the guide vanes 11.
  • the spiral insert 3 is associated with an elastic element or a clamping system 12.
  • the clamping system 12 rests on the one hand on the spiral insert 3 and on the other hand on the diffuser 7 or on its abutment flange 13 to the inlet housing 2.
  • the clamping system 12 has a central receiving bolt 14, to which a plant foot 16 is associated with the diffuser side.
  • the plant foot 16 rests with its contact surface 17 against a corresponding abutment surface 18 of the diffuser 7 or its abutment flange 13.
  • the receiving bolt 14 is assigned a stop element 19, which is fixed in a form-fitting manner to the receiving bolt 14 via a screw connection.
  • the stop member 19 may also be connected to the locating bolts 14 in any other suitable manner of connection.
  • the stop element 19 could be welded to the locating bolt.
  • the active element 21 is preferably arranged on the spiral side, and provided with pot-like holes, of which in FIG. 2 due to the selected display range, only one is recognizable, so that the active element 21 seen in the selected section is U-shaped with a base web 23 (bottom hole) and two U-legs 24 is executed.
  • a through hole 26 corresponding to the receiving bolt 14 is inserted, so that the active element 21 is movable along a longitudinal axis (double arrow 27) of the receiving bolt 14.
  • the U-legs 24 are oriented with their free ends 28 in the direction of the spiral insert 3, so that the active element 21 rests against the spiral insert 3 in the clamped state of the clamping system 8.
  • the energy accumulator 22 is disposed between the active element 21 and the ganfuß 16, and preferably designed as a plate spring package or as a cup spring ring.
  • the spacer 9 is accommodated on the foot side in the spiral insert 3, and is oriented on the head side to a channel inner wall 29 (FIG. FIG. 1 ).
  • the clamping system 12 presses the spacer 9 with its head side 31 against the channel inner wall 29, on which at least on the contact surface of the spacer 9 sliding elements 32 are provided.
  • the sliding elements 32 are executed in the illustrated embodiment as sliding plates, which are formed from a suitable material and preferably coated or processed accordingly.
  • the sliding elements 32 are sufficiently secure in the channel inner wall 29 introduced.
  • the hot gas expander 1 is of course associated with an impeller 33, the blades are spaced with their edges 34 in the direction of the contour ring 6, so that a contouring gap 36 is formed.
  • the spiral insert 3 is preassembled with the inlet guide 4 outside the inlet housing 2 to form a unit us as a unit in the inlet housing 2.
  • the spiral insert 3 is pressed with suitable tools axially over the spacers 9 (Leitschaufelbolzen) against the sliding plates in the inlet housing rear wall (channel inner wall 11), so then the contoured ring 6 is installed and adjusted (axial gap). Subsequently, the clamping system 12 is used.
  • the inlet housing 2 is closed by the abutment flange 13 is screwed to the inlet housing 2.
  • the clamping system 12 is tensioned, whereby the gap between the guide vanes 11 and the channel inner wall 29 as well as the contouring gap 36 can be set to a minimum amount.
  • the spiral insert 3 is free of the inlet housing 2 in the radial and in the axial direction.
  • the individual components can expand due to the thermal effect.
  • the spacers 9 are pressed via the spiral insert 3 against the channel inner wall 29 and against the sliding elements 32, so that here a sliding in the radial direction is effected.
  • a sliding in the radial direction is effected.
  • only the blade height of the guide vanes must advantageously be taken into account.
  • the contoured ring 6 is pressed away from the blades of the impeller 33 by the pressing of the spacer 9 against the sliding elements 32.
  • the spiral insert 3 is also associated with an adjustment system 37 for radial adjustability and a suitable sealing system 38 that seals the contour ring 6 to the diffuser 7.

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

Abstract

The flow machine (1) has a rotating blade with rotor, a housing and a fixed flow contour e.g. inlet guiding apparatus (4), contour ring (6). The flow contour is twisted by a flexible element against a housing, so that the clamping forces are acted between the rotating blade and the flow contour from the flexible element in decreasing direction of cleave.

Description

Die Erfindung betrifft eine Strömungsmaschine, insbesondere Heißgasexpander, welche strömungsmaschine,

  • einen Laufschaufeln umfassenden Rotor aufweist,
  • einen Eintrittsleitapparat aufweist, mit einen Stellring, mit zumindest einen Abstandhalter und mit Leitschaufeln, wobei ein Verdrehen des Stellrings ein Verdrehen der Leitschaufeln bewirkt,
  • ein Gehäuse und einen Konturring aufweist, welcher Strömungskanäle im Bereich der Laufschaufeln einseitig begrenzt.
The invention relates to a turbomachine, in particular Heißgasexpander, which flow machine,
  • Having a rotor blades,
  • an inlet guide, with a collar, with at least one spacer and vanes, wherein a rotation of the collar causes a twisting of the vanes,
  • a housing and a contoured ring which limits flow channels in the region of the blades on one side.

Aus der EP 1 249 577 A1 , der EP 1 643 172 A1 , der WO 01/09488 A1 , der US 5,203,673 A sind jeweils Mechanismen zur aktiven Spaltkontrolle einer Turbomaschine bekannt, bei denen ein Antrieb ein mindestens eine Dichtung tragendes Gehäuseteil derart verschiebt, dass sich radiale Spalte zu Laufschaufeln eines sich konisch aufweitenden Strömungskanal einer Turbomaschine verringern oder vergrößern lassen, so dass im Interesse einer Wirkungsgradverbesserung ein Spaltminimum erzielbar ist. Analog zu der aktiven Spaltkontrolle offenbart die DE 2 165 528 eine manuelle Einstellbarkeit des Spaltes, wobei statt eines Linearantriebes zum Verschieben des Gehäuseteiles eine verstellbare Schraubverbindung vorgesehen ist.From the EP 1 249 577 A1 , of the EP 1 643 172 A1 , of the WO 01/09488 A1 , of the US 5,203,673 A In each case, mechanisms for active gap control of a turbomachine are known in which a drive displaces a housing part bearing at least one seal in such a way that radial gaps can be reduced or increased to form blades of a conically widening flow channel of a turbomachine, so that a gap minimum can be achieved in the interest of improving the efficiency is. Similar to the active gap control discloses the DE 2 165 528 a manual adjustability of the gap, wherein instead of a linear drive for moving the housing part, an adjustable screw connection is provided.

Die EP 1 620 633 B1 offenbart einen Heißgasexpander in radialer Bauweise mit einem verstellbaren Eintrittsleitapparat, bei dem die verstellbaren Leitschaufeln von einem elastischen Element in einer definierten Lage gehalten werden, in dem das elastische Element die Leitschaufeln in Richtung der jeweiligen Drehachse vorspannt. Aus der JP 02 22 36 06 ist es darüber hinaus bekannt, Sekundäretrömungen eines Zentrifugalverdichters im Bereich des Austritts aus dem Laufrad zu reduzieren, in dem ein Aktuator die dem Laufrad gegenüberliegende Wand in Richtung der Minimierung des Spaltes verlagert.The EP 1 620 633 B1 discloses a radial expansion hot gas expander having an adjustable inlet guide vane in which the adjustable vanes are held in a defined position by a resilient member in which the resilient member biases the vanes in the direction of the respective axis of rotation. From the JP 02 22 36 06 It is also known to reduce secondary flows of a centrifugal compressor in the region of exit from the impeller, in which an actuator displaces the wall opposite the impeller in the direction of minimizing the gap.

Strömungsmaschinen, beispielsweise Getriebemaschinen, insbesondere Heißgasexpander der eingangs genannten Art zeichnen sich durch eine Mehrwellenanordnung mit unterschiedlichen Rotationsgeschwindigkeiten um ein zentrales Antriebsrad aus. Hierdurch wird eine kompakte Einheit für eine mehrstufige Verdichtung/Expansion für eine Vielzahl von Medien, vorzugsweise von gasförmigen Medien zur Verfügung gestellt.Turbomachines, such as gear machines, in particular hot gas expander of the type mentioned are characterized by a multi-shaft arrangement with different rotational speeds to a central drive wheel. This provides a compact unit for multi-stage compaction / expansion for a variety of media, preferably gaseous media.

Derartige Getriebemaschinen expandieren das Medium, welches eine Eintrittstemperatur von bis zu 300°C oder in einer bevorzugten Ausführung eine Eintrittstemperatur über 300°C aufweisen kann. Bei einer Medieneintrittstemperatur von mehr als 300°C spricht man auch von so genannten Heißgasexpandern.Such gear machines expand the medium having an inlet temperature of up to 300 ° C or, in a preferred embodiment, an inlet temperature of over 300 ° C can have. At a media inlet temperature of more than 300 ° C one speaks of so-called hot gas expanders.

Diese Heißgasexpander weisen mindestens ein Einlaufgehäuse auf, in dem der Spiraleinsatz angeordnet ist. Der Spiraleinsatz trägt einen verstellbaren Eintrittsleitapparat, der einen Stellring, Leitschaufeln und Bolzen aufweist, wobei die Bolzen als Drehachse zum Einstellen der Leitschaufeln dienen.These Heißgasexpander have at least one inlet housing, in which the spiral insert is arranged. The spiral insert carries an adjustable Eintrittsleitapparat having a collar, vanes and bolts, wherein the bolts serve as a rotation axis for adjusting the vanes.

Die Leitschaufeln sind also drehbar an dem Bolzen angeschlagen, wobei die Leitschaufeln gleichzeitig über einen Mitnehmer mit dem Stellring verbunden sind. Wird nun der Stellring in einem gewünschten Winkelbetrag verdreht, bewirken die Mitnehmer eine Zwangsverstellung der Leitschaufeln um den Bolzen, so dass durch die Verstellung der Leitschaufeln eine Beeinflussung der Richtung und/oder der Geschwindigkeit des Mediumstroms zu der Laufschaufel bzw. zum Laufrad bewirkt wird.The guide vanes are therefore rotatably struck on the bolt, wherein the guide vanes are simultaneously connected via a driver with the adjusting ring. If now the adjusting ring is rotated in a desired angular amount, the drivers cause a forced adjustment of the guide vanes about the bolt, so that the adjustment of the guide vanes influencing the direction and / or the speed of the medium flow to the blade or the impeller is effected.

Der Spiraleinsatz hat somit zwei Funktionen. Zum einen trägt der Spiraleinsatz den Verstellmechanismus (Stellring usw.), wobei der Spiraleinsatz zum anderen auch den Konturring trägt.The spiral insert thus has two functions. On the one hand, the spiral insert carries the adjusting mechanism (adjusting ring, etc.), with the spiral insert on the other also carries the contour ring.

Der Spiraleinsatz mit dem zugeordneten Eintrittsleitapparat und dem Konturring wird außerhalb des Einlaufgehäuses vormontiert und als Einheit in dieses eingesetzt.The spiral insert with the associated inlet guide and the contour ring is pre-assembled outside of the inlet housing and used as a unit in this.

Aufgrund der hohen thermischen Belastung, insbesondere bei Heißgasexpandern, wird jedoch beobachtet, dass sich die unterschiedlichen Bauteilkomponenten aufgrund der thermischen Einwirkung ausdehnen bzw. unterschiedlich ausdehnen. Durch die üblicherweise starre Verbindung des Spiraleinsatzes mit den zugeordneten Bauteilen an dem Einlaufgehäuse muss die einzusetzende Einheit daher bei der Montage mit relativ großem radialen Spiel zum Einlaufgehäuse bzw. zum Laufrad ausgeführt werden, um ein Klemmen durch unterschiedliche Temperaturdehnungen zu vermeiden und um eine axiale Bewegungsfreiheit sicherstellen zu können.Due to the high thermal load, in particular with hot gas expanders, however, it is observed that the different component components expand or expand differently due to the thermal effect. Due to the usually rigid connection of the spiral insert with the associated components to the inlet housing, the unit to be used must therefore be performed during assembly with a relatively large radial clearance to the inlet housing or the impeller to clamps by different thermal expansions to avoid and to ensure axial freedom of movement.

Hierdurch ist aber der Konturringspalt zwischen der Konturringfläche und den dazu korrespondierenden Laufschaufelkanten des Laufrades derart groß bemessen, dass der Wirkungsgrad des Heißgasexpanders durch extrem hohe Spaltverluste erheblich herabgesetzt ist. Wirkungsgradverluste können aber auch auftreten, wenn die Spalte zwischen den Leitschaufeln bzw. dem Bolzen (als Drehachse der jeweiligen Leitschaufel) und der zugeordneten Kanalinnenwand zu groß sind.As a result, but the contouring gap between the contour ring surface and the corresponding blade edge of the impeller is sized so large that the efficiency of the hot gas expander is significantly reduced by extremely high gap losses. Efficiency losses can also occur if the gaps between the guide vanes or the bolt (as the axis of rotation of the respective vane) and the associated channel inner wall are too large.

Der Erfindung liegt daher die Aufgabe zugrunde, eine Strömungsmaschine der Eingangs genannten Art, insbesondere einen Heißgasexpander, mit einfachen Mitteln dahingehend zu verbessern, dass die Spaltverluste reduziert sind, so dass der Wirkungsgrad erheblich erhöht werden kann.The invention is therefore based on the object to improve a turbomachine of the type mentioned, in particular a hot gas expander, by simple means to the effect that the gap losses are reduced, so that the efficiency can be significantly increased.

Erfindungsgemäß wird die Aufgabe dadurch gelöst, dass der Eintrittsleitapparat und der Konturring gemeinsam mittels mindestens eines elastischen Elements gegen das Gehäuse verspannt werden, so dass die Verspannkräfte aus dem elastischen Element in Richtung einer Verringerung von Spalten zwischen den Laufschaufeln und dem Konturring wirken.According to the invention the object is achieved in that the Eintrittsleitapparat and the contour ring are clamped together by means of at least one elastic element against the housing, so that the clamping forces from the elastic element in the direction of a reduction of gaps between the blades and the contour ring act.

Aufgrund des erfindungsgemäßen elastischen Elementes, das im Folgenden als Spannsystem bezeichnet wird, ist die Strömungskontur bzw. ein zugeordneter Spiraleinsatz beweglich zum Einlaufgehäuse bzw. zum Gehäuse, wobei der Spiraleinsatz bevorzugt in axialer Richtung gesehen beweglich ist.Due to the elastic element according to the invention, which is referred to below as the clamping system, the flow contour or an associated spiral insert is movable to the inlet housing or to the housing, wherein the spiral insert is preferably seen in the axial direction movable.

Günstig im Sinne der Erfindung ist, wenn das Spannsystem zentrale Aufnahmenbolzen aufweist, denen diffusorseitig jeweils ein Anlagefuß zugeordnet ist, wobei dem jeweiligen Aufnahmebolzen spiraleinsatzseitig jeweils ein Stoppelement zugeordnet ist, das jeweils kraftformschlüssig an dem jeweiligen Aufnahmebolzen festgelegt ist, wobei dem jeweiligen Aufnahmebolzen ein Kraftspeicher und ein Wirkelement zugeordnet ist. Das Wirkelement ist vorzugsweise spiraleinsatzseitig angeordnet, wobei der Kraftspeicher zwischen dem Wirkelement und dem Anlagefuß angeordnet ist.Favorable in the context of the invention, when the clamping system has central receiving bolts, the diffuser side is assigned in each case a plant, wherein the respective receiving bolt is assigned a respective stop element on the spiral insert side, each of which is fixed frictionally to the respective locating bolt, wherein the respective locating bolt an energy storage and an active element is assigned. The active element is preferably arranged on the spiral insert side, the force accumulator being arranged between the active element and the contact base.

In bevorzugter Ausgestaltung ist der Kraftspeicher als Tellerfederpaket bzw. Tellerfederkranz ausgeführt, der um den Aufnahmebolzen herum angeordnet ist.In a preferred embodiment of the energy storage is designed as a plate spring package or cup spring ring, which is arranged around the receiving bolt around.

Zweckmäßiger Weise ist das Wirkelement mit topfartigen Bohrungen versehen. In dem Bohrungsgrund der topfartigen Bohrungen ist jeweils eine zum Aufnahmebolzen korrespondierende Durchgangsbohrung eingebracht, so dass das Wirkelement entlang einer Längsachse des Aufnahmebolzens verschiebbar gelagert ist. Das Stoppelement wirkt dabei quasi als Bewegungsbegrenzer des Wirkelements in Richtung zum Spiraleinsatz. Das Wirkelement liegt im verspannten Zustand bevorzugt an dem Spiraleinsatz an.Appropriately, the active element is provided with pot-like holes. In the hole bottom of the pot-like bores in each case a corresponding to the receiving pin through hole is introduced, so that the active element is slidably mounted along a longitudinal axis of the receiving pin. The stop element acts as a kind of movement limiter of the active element in the direction of the spiral insert. The active element is in the tensioned state preferably on the spiral insert.

Der Eintrittsleitapparat weist einen Abstandhalter auf, der fußseitig in dem Spiraleinsatz aufgenommen ist und kopfseitig zu einer Kanalinnenwand orientiert ist, wobei das Spannsystem den Abstandhalter mit seiner Kopfseite gegen die Kanalinnenwand drückt, die zumindest bereichsweise ein Gleitelement aufweist. Der Eintrittsleitapparat weist zudem einen Stellring und Leitschaufeln auf. Die Leitschaufeln sind über Mitnehmer mit dem Stellring verbunden, und drehbar dem Abstandhalter zugeordnet. Der Abstandhalter kann somit auch als Leitschaufelbolzen bezeichnet werden und dient als Drehachse der Leitschaufeln. Bei einem Verstellen des Stellrings in einem gewünschten Winkelbetrag werden die Leitschaufeln über die Mitnehmer zwangsgeführt mitgenommen und drehen sich um die jeweilige Schaufelachse bzw. um den jeweiligen Abstandhalter. Zweckmäßiger Weise ist jedem Abstandhalter ein Gleitelement zugeordnet, so dass die jeweiligen Gleitelemente an dem zum Abstandhalter zugeordneten Ort in der Kanalinnenwand angeordnet sind. Natürlich kann aber auch ein einziges, durchgehendes Gleitelement vorgesehen sein.The inlet guide apparatus has a spacer which is accommodated in the spiral insert on the foot side and is oriented on the head side to a channel inner wall, wherein the clamping system presses the spacer with its head side against the channel inner wall, which at least partially has a sliding element. The Eintrittsleitapparat also has a collar and vanes. The vanes are connected via drivers with the adjusting ring, and rotatably associated with the spacer. The spacer can thus also be referred to as a guide blade bolt and serves as a rotation axis of the guide vanes. When adjusting the adjusting ring in a desired angle amount, the vanes over the drivers are forcibly taken with them and turn around the respective blade axis or around the respective spacer. Appropriately, each spacer is associated with a sliding element, so that the respective sliding elements are arranged at the location assigned to the spacer in the channel inner wall. Of course, but also a single, continuous sliding element may be provided.

In bevorzugter Ausführung ist das Gleitelement als Gleitplatte in der Kanalinnenwand hinreichend lagesicher eingesetzt. Das Gleitelement kann aber auch als Gleitbeschichtung ausgeführt sein. Das Gleitelement in seiner Ausgestaltung als Gleitplatte ist aus einem geeigneten Material gebildet, welches bevorzugt aus einem temperatur- und korrosionsfesten Grundmaterial gefertigt ist, und entsprechend beschichtet oder behandelt ist. Beispielsweise können die Gleitelemente bzw. Gleitplatten aus Stahl oder Inconel bestehen und mit einer Spezialschicht (z.B. Tribaloy) beschichtet sein. Die Beschichtung wird bevorzugt derart gewählt, dass ein Gleitreibungsbeiwert reduziert wird, und gleichzeitig eine hohe Verschleißfestigkeit vorhanden ist. Die Beschichtung verhindert zudem ein Fressen und ist korrosionsfest. Alternativ ist auch eine Behandlung durch Kolsterisieren® (korrosionsfestes Oberflächenhärten) möglich. Natürlich kann das Gleitelement in der Ausgestaltung als Gleitbeschichtung entsprechend mit der Beschichtung direkt auf dem zugeordneten Bereich der Kanalinnenwand aufgebracht sein.In a preferred embodiment, the sliding element is used as a sliding plate in the channel inner wall sufficiently secure. The sliding element can also be designed as a sliding coating. The sliding element in its embodiment as a sliding plate is formed of a suitable material, which is preferably made of a temperature and corrosion-resistant base material, and is coated or treated accordingly. For example, the sliding elements or sliding plates made of steel or Inconel and be coated with a special layer (eg Tribaloy). The coating is preferably chosen such that a sliding friction coefficient is reduced, and at the same time a high wear resistance is present. The coating also prevents seizing and is corrosion resistant. Alternatively, a treatment by Kolsterizing ® (corrosion-resistant surface hardening) is possible. Of course, the slider may be applied in the embodiment as a sliding coating according to the coating directly on the associated region of the channel inner wall.

Der Spiraleinsatz wird mit dem Eintrittsleitapparat außerhalb des Einlaufgehäuses vormontiert und in dieses als Einheit eingesetzt. Der Spiraleinsatz wird mit geeigneten Hilfsmitteln axial über die Abstandhalter (Leitschaufelbolzen) gegen die Gleitplatten in der Einlaufgehäuserückwand (Kanalinnenwand) gedrückt, wobei so dann der Konturring eingebaut und eingestellt wird (axialer Spalt). Anschließend wird das Spannsystem an der vorgesehenen Stelle eingesetzt. Anschließend wird der Diffusor mit dem Einlaufgehäuse verbunden, bzw. verschraubt, wobei der Diffusor mit seinem Anlageflansch an dem Anlagefuß anliegt. Durch das verbinden bzw. verschrauben des Diffusors mit dem Einlaufgehäuse wird das Spannsystem vorgespannt. Selbstverständlich wird das Spannsystem, insbesondere das Tellerfederpaket vor der Montage bezüglich der erforderlichen Federspannung auch unter Betriebbedingungen ausgelegt. Natürlich werden auch die jeweiligen Komponenten (Spiraleinsatz, Eintrittsleitapparat, Konturring) entsprechend ausgelegt.The spiral insert is pre-assembled with the inlet guide outside the inlet housing and inserted into this as a unit. The spiral insert is pressed with suitable tools axially over the spacers (Leitschaufelbolzen) against the sliding plates in the inlet housing rear wall (channel inner wall), whereby then the contour ring is installed and adjusted (axial gap). Subsequently, the clamping system is used at the intended location. Subsequently, the diffuser is connected to the inlet housing, or screwed, the diffuser with its abutment flange abuts the plant foot. By connecting or screwing the diffuser with the inlet housing, the clamping system is biased. Of course, the clamping system, in particular the cup spring assembly is designed prior to assembly with respect to the required spring tension even under operating conditions. Of course, the respective components (spiral insert, inlet guide, contour ring) are designed accordingly.

Das Spannsystem drückt die Abstandhalter mit ihrer Kopfseite gegen das entsprechende Gleitelement, bzw. die bevorzugte Gleitplatte. Bei Differenzen in der Temperaturdehnung der einzelnen Komponenten wird vorteilhaft ein Gleiten in radialer Richtung erreicht, da sich die Abstandhalter an den Gleitelementen abstützen. Weiter wird durch die Wärmedehnungen vorteilhaft ein axiales Einfedern der Tellerfedern erreicht. Durch das Pressen bzw. Verspannen der Abstandhalter gegen die Kanalinnenwand entfallen zusätzlich Spaltmasse, die durch eine Verformung des Einlaufgehäuses entstehen können. Als axiale Wärmedehnung kann somit vorteilhaft lediglich die Schaufelhöhe der Leitschaufeln Berücksichtigung zur Spaltauslegung finden. Durch die geringen Spalte am Eintrittsleitgitter (Leitschaufeln) wird der Wirkungsgrad gesteigert.The clamping system presses the spacers with their head side against the corresponding sliding element or the preferred sliding plate. With differences in the thermal expansion of the individual components, sliding in the radial direction is advantageously achieved, since the spacers are supported on the sliding elements. Next is achieved by the thermal expansion advantageous axial compression of the disc springs. By pressing or clamping the spacer against the channel inner wall also eliminates gap material, which can be caused by deformation of the inlet housing. As axial thermal expansion can thus advantageously only the blade height of the vanes find consideration for gap design. Due to the small gap at Eintrittsleitgitter (vanes), the efficiency is increased.

Der Heißgasexpander weist zudem das Laufrad auf, welches mit seinen Laufschaufelkanten zu dem Konturring beabstandet ist, so dass ein Konturringspalt gebildet ist. Mittels des vorteilhaften Spannsystems kann dieser Konturringspalt vorteilhaft minimiert werden, da die Temperaturdehnung direkt auf den Abstandhalter wirkt, der sich an der Kanalinnenwand bzw. dem jeweiligen Gleitelement abstützt, und bei einer thermisch bedingten Ausdehnung den Konturring von dem Laufrad wegdrückt, so dass sich die thermische Ausdehnung der Laufschaufeln und des Konturrings quasi aufhebt.The Heißgasexpander also has the impeller, which is spaced with its blade edges to the contour ring, so that a contouring gap is formed. By means of the advantageous clamping system, this contouring gap can be advantageously minimized, since the temperature expansion acts directly on the spacer, which is supported on the channel inner wall or the respective sliding element, and pushes the contour ring away from the impeller in a thermally induced expansion, so that the thermal Expansion of the blades and the contour ring quasi picks up.

Insgesamt wird somit vorteilhaft erreicht, dass Spaltverluste reduziert sind, wodurch der Wirkungsgrad der Strömungsmaschine bzw. der Getriebemaschine bzw. des beispielhaften Heißgasexpanders erhöht ist. Die Spaltmaße können von vornherein minimaler ausgeführt werden, wobei mittels des Spannsystems erreicht wird, dass die thermische Ausdehnung quasi kompensiert wird.Overall, it is thus advantageously achieved that gap losses are reduced, as a result of which the efficiency of the turbomachine or of the geared machine or of the exemplary one Hot gas expander is increased. The gap dimensions can be performed minimally from the outset, whereby it is achieved by means of the clamping system that the thermal expansion is virtually compensated.

Vorteilhaft wird weiter mittels des Spannsystems erreicht, dass übermäßige Bauteilbeanspruchungen durch Wärmedehnungen verhindert werden, da der Spiraleinsatz in radialer und axialer Richtung frei vom Einlaufgehäuse ist.Advantageously, it is further achieved by means of the clamping system that excessive component stresses are prevented by thermal expansion, since the spiral insert in the radial and axial direction is free from the inlet housing.

Weiter vorteilhafte Ausgestaltungen der Erfindung sind in den Unteransprüchen und der folgenden Figurenbeschreibung offenbart. Es zeigen:

Fig. 1
einen Querschnitt durch einen beispielhaft dargestellten Heißgasexpander, und
Fig. 2
ein elastisches Element (Spannsystem) als Einzelheit.
Further advantageous embodiments of the invention are disclosed in the subclaims and the following description of the figures. Show it:
Fig. 1
a cross section through a exemplified hot gas expander, and
Fig. 2
an elastic element (clamping system) as a detail.

In den unterschiedlichen Figuren sind gleiche stets mit denselben Bezugszeichen versehen, weswegen diese in der Regel auch nur einmal beschrieben werden.In the different figures, the same are always provided with the same reference numerals, which is why these are usually described only once.

Figur 1 zeigt eine Strömungsmaschine bzw. eine Getriebemaschine, die in dem dargestellten Ausführungsbeispiel als Heißgasexpander 1 mit einer Eintrittstemperatur eines vorzugsweise gasförmigen Mediums von bis zu 510°C ausgeführt ist. Der Heißgasexpander 1 weist mindestens ein Einlaufgehäuse 2 auf, in dem ein Spiraleinsatz 3 angeordnet ist. Dem Spiraleinsatz 3 ist ein Eintrittsleitapparat 4 und ein Konturring 6 zugeordnet, so dass eine Strömungskontur gebildet ist. Dem Einlaufgehäuse 2 ist weiterhin ein Diffusor 7 zugeordnet. FIG. 1 shows a turbomachine or a gear machine, which is designed in the illustrated embodiment as a hot gas expander 1 with an inlet temperature of a preferably gaseous medium of up to 510 ° C. The hot gas expander 1 has at least one inlet housing 2, in which a spiral insert 3 is arranged. The spiral insert 3 is assigned an inlet guide 4 and a contour ring 6, so that a flow contour is formed. The inlet housing 2 is further associated with a diffuser 7.

Der Eintrittsleitapparat 4 weist einen Stellring 8, zumindest einen Abstandhalter 9 und Leitschaufeln 11 auf.The inlet guide 4 has an adjusting ring 8, at least one spacer 9 and vanes 11.

Die Leitschaufeln 11 sind über Mitnehmer mit dem Stellring 8 verbunden, so dass ein Verdrehen des Stellrings 8 eine entsprechende Verstellung der Leitschaufeln 11 bewirkt, die drehbar an den Abstandhaltern 9 befestigt sind. Die Abstandhalter 9 dienen somit als Drehachse der Leitschaufeln 11.The guide vanes 11 are connected via drivers with the adjusting ring 8, so that a rotation of the adjusting ring 8 causes a corresponding adjustment of the guide vanes 11 which are rotatably mounted on the spacers 9. The spacers 9 thus serve as the axis of rotation of the guide vanes 11.

Dem Spiraleinsatz 3 ist ein elastisches Element bzw. ein Spannsystem 12 zugeordnet. Das Spannsystem 12 liegt einerseits an dem Spiraleinsatz 3 und andererseits an dem Diffusor 7 bzw. an seinem Anlageflansch 13 zum Einlaufgehäuse 2 an.The spiral insert 3 is associated with an elastic element or a clamping system 12. The clamping system 12 rests on the one hand on the spiral insert 3 and on the other hand on the diffuser 7 or on its abutment flange 13 to the inlet housing 2.

In der in Figur 2 dargestellten Ausführung weist das Spannsystem 12 einen zentralen Aufnahmebolzen 14 auf, dem diffusorseitig ein Anlagefuß 16 zugeordnet ist. Der Anlagefuß 16 liegt mit seiner Anlagefläche 17 an einer dazu korrespondierenden Gegenanlagefläche 18 des Diffusors 7 bzw. seines Anlageflansches 13 an. Spiralseitig ist dem Aufnahmebolzen 14 ein Stoppelement 19 zugeordnet, welches über eine Schraubverbindung kraftformschlüssig an dem Aufnahmebolzen 14 festgelegt ist. Natürlich kann das Stoppelement 19 auch in einer anderen, geeigneten Verbindungsart mit den Aufnahmebolzen 14 verbunden sein. Beispielsweise könnte das Stoppelement 19 mit dem Aufnahmebolzen verschweißt sein.In the in FIG. 2 In the illustrated embodiment, the clamping system 12 has a central receiving bolt 14, to which a plant foot 16 is associated with the diffuser side. The plant foot 16 rests with its contact surface 17 against a corresponding abutment surface 18 of the diffuser 7 or its abutment flange 13. On the spiral side, the receiving bolt 14 is assigned a stop element 19, which is fixed in a form-fitting manner to the receiving bolt 14 via a screw connection. Of course, the stop member 19 may also be connected to the locating bolts 14 in any other suitable manner of connection. For example, the stop element 19 could be welded to the locating bolt.

Weiter sind dem Aufnahmebolzen 14 ein Wirkelement 21 und ein Kraftspeicher 22 zugeordnet.
Das Wirkelement 21 ist bevorzugt spiralseitig angeordnet, und mit topfartigen Bohrungen versehen, von denen in Figur 2 aufgrund des gewählten Darstellungsbereiches lediglich eine erkennbar ist, so dass das Wirkelement 21 in dem gewählten Schnitt gesehen U-förmig mit einem Basissteg 23 (Bohrungsgrund) und zwei U-Schenkeln 24 ausgeführt ist. In dem Basissteg 23 (Bohrungsgrund) ist eine zum Aufnahmebolzen 14 korrespondierende Durchgangsöffnung 26 eingebracht, so dass das Wirkelement 21 entlang einer Längsachse (Doppelpfeil 27) des Aufnahmebolzens 14 beweglich ist. Die U-Schenkel 24 sind mit ihren freien Enden 28 in Richtung zum Spiraleinsatz 3 orientiert, so dass das Wirkelement 21 im verspannten Zustand des Spannsystems 8 an dem Spiraleinsatz 3 anliegt.
Der Kraftspeicher 22 ist zwischen dem Wirkelement 21 und dem Anlagefuß 16 angeordnet, und bevorzugt als Tellerfederpaket bzw. als Tellerfederkranz ausgeführt.Next, the receiving bolt 14, an active element 21 and a force accumulator 22 are assigned.
The active element 21 is preferably arranged on the spiral side, and provided with pot-like holes, of which in FIG. 2 due to the selected display range, only one is recognizable, so that the active element 21 seen in the selected section is U-shaped with a base web 23 (bottom hole) and two U-legs 24 is executed. In the base web 23 (bottom of the hole), a through hole 26 corresponding to the receiving bolt 14 is inserted, so that the active element 21 is movable along a longitudinal axis (double arrow 27) of the receiving bolt 14. The U-legs 24 are oriented with their free ends 28 in the direction of the spiral insert 3, so that the active element 21 rests against the spiral insert 3 in the clamped state of the clamping system 8.
The energy accumulator 22 is disposed between the active element 21 and the Anlagefuß 16, and preferably designed as a plate spring package or as a cup spring ring.

Der Abstandhalter 9 ist fußseitig in dem Spiraleinsatz 3 aufgenommen, und orientiert sich kopfseitig zu einer Kanalinnenwand 29 (Figur 1). Das Spannsystem 12 drückt den Abstandhalter 9 mit seiner Kopfseite 31 gegen die Kanalinnenwand 29, an der zumindest an der Anlagefläche des Abstandhalters 9 Gleitelemente 32 vorgesehen sind.The spacer 9 is accommodated on the foot side in the spiral insert 3, and is oriented on the head side to a channel inner wall 29 (FIG. FIG. 1 ). The clamping system 12 presses the spacer 9 with its head side 31 against the channel inner wall 29, on which at least on the contact surface of the spacer 9 sliding elements 32 are provided.

Die Gleitelemente 32 sind in dem dargestellten Ausführungsbeispiel als Gleitplatten ausgeführt, die aus einem geeigneten Material gebildet und vorzugsweise beschichtet oder entsprechend bearbeitet sind. Die Gleitelemente 32 sind hinreichend lagesicher in der Kanalinnenwand 29 eingebracht.The sliding elements 32 are executed in the illustrated embodiment as sliding plates, which are formed from a suitable material and preferably coated or processed accordingly. The sliding elements 32 are sufficiently secure in the channel inner wall 29 introduced.

Dem Heißgasexpander 1 ist natürlich ein Laufrad 33 zugeordnet, dessen Laufschaufeln mit ihren Kanten 34 in Richtung zum Konturring 6 beabstandet sind, so dass ein Konturringspalt 36 gebildet ist.The hot gas expander 1 is of course associated with an impeller 33, the blades are spaced with their edges 34 in the direction of the contour ring 6, so that a contouring gap 36 is formed.

Der Spiraleinsatz 3 wird mit dem Eintrittsleitapparat 4 außerhalb des Einlaufgehäuses 2 zu einer Einheit vormontiert uns als Einheit in das Einlaufgehäuse 2 eingesetzt. Der Spiraleinsatz 3 wird mit geeigneten Hilfsmitteln axial über die Abstandhalter 9 (Leitschaufelbolzen) gegen die Gleitplatten in der Einlaufgehäuserückwand (Kanalinnenwand 11) gedrückt, wobei so dann der Konturring 6 eingebaut und eingestellt wird (axialer Spalt). Anschließend wird das Spannsystem 12 eingesetzt. Mittels des Diffusors 7 wird das Einlaufgehäuse 2 verschlossen, indem der Anlageflansch 13 mit dem Einlaufgehäuse 2 verschraubt wird. Hierdurch wird das Spannsystem 12 gespannt, wodurch auch die Spalte zwischen den Leitschaufeln 11 und der Kanalinnenwand 29 ebenso wie der Konturringspalt 36 auf einen minimalen Betrag eingestellt werden kann. Der Spiraleinsatz 3 ist in radialer und in axialer Richtung frei von dem Einlaufgehäuse 2.The spiral insert 3 is preassembled with the inlet guide 4 outside the inlet housing 2 to form a unit us as a unit in the inlet housing 2. The spiral insert 3 is pressed with suitable tools axially over the spacers 9 (Leitschaufelbolzen) against the sliding plates in the inlet housing rear wall (channel inner wall 11), so then the contoured ring 6 is installed and adjusted (axial gap). Subsequently, the clamping system 12 is used. By means of the diffuser 7, the inlet housing 2 is closed by the abutment flange 13 is screwed to the inlet housing 2. As a result, the clamping system 12 is tensioned, whereby the gap between the guide vanes 11 and the channel inner wall 29 as well as the contouring gap 36 can be set to a minimum amount. The spiral insert 3 is free of the inlet housing 2 in the radial and in the axial direction.

Unter Betriebsbedingungen, insbesondere bei einer Eintrittstemperatur eines Mediums, vorzugsweise eines gasförmigen Mediums über 300°C, beispielsweise von 510°C können sich die einzelnen Komponenten aufgrund der thermischen Einwirkung Ausdehnen. Die thermische Ausdehnung bewirkt ein Einfedern des Spannsystems 12 bzw. des Kraftspeichers 22. Durch das Spannsystem 12 werden die Abstandhalter 9 über den Spiraleinsatz 3 gegen die Kanalinnenwand 29 bzw. gegen die Gleitelemente 32 gedrückt, so dass hier ein Gleiten in radialer Richtung bewirkt wird. Als axiale Wärmedehnung muss vorteilhaft lediglich die Schaufelhöhe der Leitschaufeln berücksichtigt werden. Durch das Anpressen der Abstandhalter 9 an die Kanalinnenwand 29 entfallen zusätzliche Spaltmaße, die durch eine (thermische) Verformung des Einlaufgehäuses 2 entstehen könnten. Gleichzeitig wird der Konturring 6 durch das Anpressen des Abstandhalters 9 an die Gleitelemente 32 von den Laufschaufeln des Laufrades 33 weggedrückt.Under operating conditions, in particular at an inlet temperature of a medium, preferably a gaseous medium above 300 ° C, for example of 510 ° C, the individual components can expand due to the thermal effect. By the clamping system 12, the spacers 9 are pressed via the spiral insert 3 against the channel inner wall 29 and against the sliding elements 32, so that here a sliding in the radial direction is effected. As axial thermal expansion, only the blade height of the guide vanes must advantageously be taken into account. By pressing the spacer 9 to the channel inner wall 29 accounts for additional gap dimensions, which could be caused by a (thermal) deformation of the inlet housing 2. At the same time, the contoured ring 6 is pressed away from the blades of the impeller 33 by the pressing of the spacer 9 against the sliding elements 32.

Insgesamt wird mittels des vorteilhaften Spannsystems 12 erreicht, dass übermäßige Bauteilbeanspruchungen durch Wärmedehnungen verhindert werden können, da der Spiraleinsatz 3, welcher gleichzeitig Träger des Eintrittsleitapparates 4 ist, zumindest in axialer Richtung frei vom Einlaufgehäuse 2 ist. Damit können Spalte zwischen den Leitschaufeln 11 und der Kanalinnenwand 29 aber auch der Konturringsspalt 36 minimal ausgeführt werden, da nur die Schaufelachse also der Abstandhalter 9 für die Wärmedehnung berücksichtigt werden muss. Durch die Wärmedehnungen kommt es zu einem radialen Gleiten über die Gleitelemente 32 und zu einem axialen Einfedern des Kraftspeichers 22 bzw. des Tellerfederpakets.Overall, it is achieved by means of the advantageous clamping system 12 that excessive component stresses can be prevented by thermal expansions, since the spiral insert 3, which is also carrier of the inlet guide 4, at least in the axial direction is free from the inlet housing 2. Thus, gaps between the guide vanes 11 and the channel inner wall 29 but also the contour ring gap 36 can be made minimal, since only the blade axis so the spacer 9 must be taken into account for the thermal expansion. Due to the thermal expansions, there is a radial sliding over the sliding elements 32 and an axial compression of the force accumulator 22 or of the cup spring package.

In dem in Figur 1 dargestellten Ausführungsbeispiel ist dem Spiraleinsatz 3 zudem ein Einstellsystem 37 zur radialen Einstellbarkeit und ein geeignetes Dichtsystem 38 zugeordnet, dass den Konturring 6 zum Diffusor 7 abdichtet.In the in FIG. 1 illustrated embodiment, the spiral insert 3 is also associated with an adjustment system 37 for radial adjustability and a suitable sealing system 38 that seals the contour ring 6 to the diffuser 7.

Claims (8)

  1. Flow machine (1),
    in particular a hot gas expander,
    which flow machine has
    - a rotor (33) comprising rotor blades,
    - an intake guiding device (4) having a set collar (8), at least one spacer (9) and guide vanes (11), wherein rotating the set collar rotates the guide vanes,
    - a housing (2);
    characterized in that the flow machine has a contour ring (6), which delimits on one side flow channels in the region of the rotor blades,
    wherein the intake guiding device (4) and the contour ring are together braced against the housing (2) by means of at least one elastic element (12),
    such that the bracing forces from the elastic element (12) act so as to reduce gaps between the rotor blades and the contour ring.
  2. Flow machine according to Claim 1,
    characterized in that
    the spacer (9) is arranged between the contour ring and the housing (2).
  3. Flow machine according to Claim 2,
    characterized in that
    the spacer (9) forms the rotation spindle of guide vanes.
  4. Flow machine according to one of the preceding claims,
    characterized in that
    the elastic element (12) is in abutment against a spiral insert (3) on one side and against a diffuser (7) on the other side.
  5. Flow machine according to one of the preceding claims,
    characterized in that
    the elastic element (12) has central locating pins (14) to which in each case a contact foot (16) is assigned on the diffuser side,
    wherein in each case a stop element (19) is assigned to the respective locating pin (14) on the spiral insert side, and wherein an operating element (21) and an energy storing device (22) are assigned to the respective locating pin (14).
  6. Flow machine according to Claim 5,
    characterized in that
    a through bore (26) corresponding to the locating pin (14) is incorporated in the operating element (21).
  7. Flow machine according to one of the preceding claims,
    characterized in that
    the heads of the spacers (9) are pressed against a channel internal wall (29) by means of the elastic element (12), wherein at least one sliding element (32) is assigned at least to a region of this wall.
  8. Flow machine according to Claim 7,
    characterized in that
    the sliding element (32) is formed as a slide plate, which preferably has a slide coating.
EP07004385.6A 2007-03-02 2007-03-02 Minimisation of the axial gap for adjustable guide vanes and for a contour ring for hot gas expanders Active EP1965035B1 (en)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP07004385.6A EP1965035B1 (en) 2007-03-02 2007-03-02 Minimisation of the axial gap for adjustable guide vanes and for a contour ring for hot gas expanders
CN200810082140.2A CN101255804B (en) 2007-03-02 2008-03-03 Fluid machine, especially hot gas expansion machine

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP07004385.6A EP1965035B1 (en) 2007-03-02 2007-03-02 Minimisation of the axial gap for adjustable guide vanes and for a contour ring for hot gas expanders

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EP1965035A1 EP1965035A1 (en) 2008-09-03
EP1965035B1 true EP1965035B1 (en) 2013-12-18

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DE102017223791A1 (en) 2017-12-27 2019-06-27 Siemens Aktiengesellschaft Shaft seal arrangement of a turbomachine, turbomachine

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