EP2581553A1 - Method and device for dynamically measuring the imbalance of the rotor of a turbocharger core assembly - Google Patents

Method and device for dynamically measuring the imbalance of the rotor of a turbocharger core assembly Download PDF

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Publication number
EP2581553A1
EP2581553A1 EP11184723.2A EP11184723A EP2581553A1 EP 2581553 A1 EP2581553 A1 EP 2581553A1 EP 11184723 A EP11184723 A EP 11184723A EP 2581553 A1 EP2581553 A1 EP 2581553A1
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EP
European Patent Office
Prior art keywords
housing
turbine
compressor
rotor
imbalance
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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.)
Granted
Application number
EP11184723.2A
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German (de)
French (fr)
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EP2581553B1 (en
EP2581553B9 (en
Inventor
Matthias Breitwieser
Jochen Grossehelweg
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Schenck RoTec GmbH
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Schenck RoTec GmbH
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Publication date
Application filed by Schenck RoTec GmbH filed Critical Schenck RoTec GmbH
Priority to PL11184723T priority Critical patent/PL2581553T3/en
Priority to HUE11184723A priority patent/HUE037381T2/en
Priority to EP11184723.2A priority patent/EP2581553B9/en
Publication of EP2581553A1 publication Critical patent/EP2581553A1/en
Publication of EP2581553B1 publication Critical patent/EP2581553B1/en
Application granted granted Critical
Publication of EP2581553B9 publication Critical patent/EP2581553B9/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
    • F01D5/00—Blades; Blade-carrying members; Heating, heat-insulating, cooling or antivibration means on the blades or the members
    • F01D5/02—Blade-carrying members, e.g. rotors
    • F01D5/027—Arrangements for balancing
    • 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
    • F01D21/00—Shutting-down of machines or engines, e.g. in emergency; Regulating, controlling, or safety means not otherwise provided for
    • F01D21/003—Arrangements for testing or measuring
    • 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
    • F05D2260/00—Function
    • F05D2260/30—Retaining components in desired mutual position
    • F05D2260/34—Balancing of radial or axial forces on regenerative rotors

Definitions

  • the invention relates to a method and apparatus for dynamically measuring the imbalance of the rotor of a turbocharger body group, the rotor comprising a turbine wheel, a compressor wheel and a shaft mounted in a center housing of the turbocharger body group.
  • Exhaust-driven turbochargers have a rotor that rotates in operation at a very high speed of often over 100,000 revolutions per minute and therefore must be balanced very precisely to avoid noise and excessive bearing loads.
  • the rotor consists of a shaft mounted in a bearing housing which carries a turbine wheel at one end and a compressor wheel at the other end. The measurement of the imbalance of the rotor is made for accuracy reasons usually at a substantially normal operating speed corresponding angular velocity.
  • Out EP 0 426 676 B1 is a method of the type specified for dynamically balancing the imbalance of the high-speed rotor of an exhaust-driven turbocharger known in which the turbocharger center housing in which the rotor is mounted, with a turbine housing enclosing the housing and the compressor enclosing housing is firmly connected and the so formed unit by means of flexible bellows hoses, which engage the two housings, is movably stored soft in a frame in all three spatial directions. Accelerometers are arranged on the housings whose acceleration signals are processed in conjunction with an optically measured phase angle to determine the size and position of the imbalance.
  • attached to the turbocharger center housing housing parts affect the vibration behavior and thus the measurement of imbalance considerably.
  • the invention has for its object to provide a method of the type mentioned above, which allows automatic implementation of the imbalance measurement with high accuracy and operating conditions. It is Another object of the invention to provide a particularly suitable for carrying out the method, simple and inexpensive device.
  • the method according to the invention enables a fully automatic measurement of the imbalance of a turbocharger rotor under operating-like conditions, i. under pressure. Nevertheless, the oscillatory mass is advantageously small, so that large vibration amplitudes can be achieved. Oscillations and resonances caused by coupled housings, which affect measurement accuracy, are avoided.
  • the compressor housing requires in contrast to the turbine housing no connections, because the air can be sucked from the atmosphere and flow freely back into this, but can be connected to hoses without any disadvantage.
  • the apparatus for carrying out the method is inexpensive, because no complicated clamping device for clamping the center housing during the measurement is needed. Accordingly, the handling when inserting or removing the turbocharger fuselage group is simple and automatic, for example, by means of a positionally precisely controllable handling gripper feasible.
  • the vibrations of the center housing can be measured without contact, for example by using a laser vibrometer to measure the vibrations.
  • the bearing elements can be very easily and very easily performed because they do not need any means to attach vibration sensors.
  • an advantageous apparatus for dynamically measuring the imbalance of the rotor of a turbocharger body group wherein the rotor comprises a turbine wheel, a compressor wheel and a shaft which is mounted in a center housing of the turbocharger body group, comprises a turbine wheel adapted to receive the turbine wheel , Turbine housing mounted on a machine bed, which is connected for accelerating the rotor by driving the turbine wheel by means of compressed air to a compressed air source and having a means of springs in at least two spatial directions movably mounted first bearing element on which the turbine side of the center housing in a movement of the center housing and of the turbine wheel in the at least two spatial directions permitting distance from the turbine housing can be supported, and a trained for receiving the compressor wheel, mounted on the machine bed compressor housing, which moves by means of springs in at least two spatial directions having mounted second bearing element, on which the compressor side of the center housing in a movement of the center housing and the compressor in the at least two spatial directions permitting distance from the compressor housing is supported, and by acting on the center housing,
  • the device according to the invention is easy to handle and allows a fully automatic implementation of the imbalance measurement.
  • the means for receiving the turbocharger hull group are simple and allow a cost effective Production of the device.
  • the first and / or second bearing element may be a simple to manufacture bearing ring which engages around a centering surface of the center housing.
  • On the turbine housing can advantageously be attached a flexible seal which is sealingly connectable to the middle housing.
  • a non-contact measuring vibration sensor for vibration measurement can be assigned to the center housing a non-contact measuring vibration sensor according to the invention, in particular a laser vibrometer.
  • a holding device for holding the turbocharger body group during the tensioning operation can be used according to the invention arranged on the turbine housing or the compressor housing clamping device or a positionally controllable handling gripper. Furthermore, the turbine housing and / or the compressor housing can be adjusted by an actuator in the axial direction for automatic clamping.
  • the drawing shows schematically the design of an unbalance measuring device with arranged therein turbocharger body group.
  • the unbalance measuring apparatus shown comprises a turbine housing 1, a compressor housing 2 and a machine bed 3.
  • the unbalance measuring device is intended and arranged to receive a turbocharger body group 4 comprising a center housing 5 with a rotor 6 mounted therein, a turbine wheel 7 at one end thereof and at its other end a compressor 8 has.
  • the middle housing 5 has on the compressor wheel 8 side facing a plate-shaped flange 9, on which the turbocharger body group 4 can be stretched.
  • a cylindrical annular collar 10, 11 is formed on the two end faces of the center housing. Between the turbine wheel 7 and the annular collar 10, a heat shield 12 is arranged.
  • the turbine housing 1 of the unbalance measuring device has a turbine chamber 13, a surrounding spiral channel 14 with not shown inlet and a central outlet channel 15.
  • an annular first bearing element 16 is arranged on the side facing the compressor housing 2 concentric with the turbine axis, which is held and supported axially and radially movably by means of springs 17 on the turbine housing 1.
  • the bearing element 16 has a bearing surface 18 orthogonal to the turbine axis for the middle housing 5 and the heat shield 12 and may additionally be provided with a centering surface if required.
  • the compressor housing 2 has, on the side facing the turbine housing 1, a compression chamber 20 with a central inlet channel 21 and a spiral channel 22, which adjoins the radially outer edge of the compression chamber 20. The outlet of the spiral channel 22 is not shown.
  • the compressor housing 2 is further provided with a clamping device 23 with rotatable clamping levers 24.
  • an annular second bearing element 25 which is arranged concentrically to the compressor axis and supported and held in the radial and axial directions by means of springs 26 on the compressor housing 2.
  • the bearing element 25 has a contact surface orthogonal to the compressor axis 27 and a cylindrical centering bore 28.
  • the turbine housing 1 is connected to the machine bed 3 by rigid attachment means 30.
  • the fasteners 30 are releasable and allow after loosening a movement of the turbine housing 1 in the axial direction to change the distance between the turbine housing 1 and the compressor housing 2 to the measure required for the imbalance measurement or for insertion and removal.
  • the storage of the compressor housing 2 may be formed with a mobility required for changing the distance.
  • a blockable actuator such as a pneumatic or hydraulic lifting cylinder or a linear motor can be used as a pneumatic or hydraulic lifting cylinder or a linear motor.
  • a non-contact measuring vibration sensor 31 is attached to the machine bed 3, which detects vibrations of the center housing 5 of the turbocharger body group 4.
  • the turbine housing 1 is previously solved on the machine bed 3 and axially removed from the compressor housing 2 until the necessary for the insertion distance between the turbine and compressor housing. Thereafter, the turbocharger body group 4 is inserted into the unbalance measuring device and first attached to the compressor housing 2 by the turbocharger body group 4 is inserted with the compressor 8 in the compressor housing 2 and the middle housing 5 is clamped by means of the clamping device 23 to the flange 9. The middle housing 5 is thereby kept in front of the compressor housing 2. The annular collar 11 of the middle housing 5 abuts axially against the contact surface 27 of the bearing element 25 and engages in the centering bore 28.
  • the turbine housing 1 After tightening the turbocharger body group 4 to the compressor housing 2, the turbine housing 1 is brought into the position shown in the drawing and attached to the machine bed 3.
  • an adjustable stop 32 By an adjustable stop 32, the appropriate position of the turbine housing 1 can be set on the machine bed. In this position, the voltage applied to the annular collar 10 heat shield 12 of the middle housing 5 passes to the storage on the bearing element 16 and the springs 17 and 26 are tensioned in the axial direction so far that the middle housing 5 is securely and limited movable from the bearing elements 16, 25 is held , In this position, the rotor 6 and the middle housing 5 have opposite the turbine housing 1 and the compressor housing 2 each such a distance that it does not come to a contact between them due to the vibrations occurring during a measurement run.
  • the insertion and holding of the turbocharger fuselage group 4 can take place during clamping by means of a positionally controllable handling gripper, which grips, inserts and holds the middle housing in position. After completion of the clamping operation of the handling gripper is opened and removed from the center housing.
  • the turbine wheel 7 is driven by compressed air and the rotor 6 is accelerated to a speed substantially corresponding to its normal operating speed.
  • a flexible seal may be attached to the turbine housing 1, which bears sealingly against the heat shield.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Testing Of Balance (AREA)
  • Supercharger (AREA)

Abstract

The method involves arranging a turbine housing (1) and a compressor housing (2) at a distance from each other at a machine bed (3). The turbine housing is connected with compressed air sources, and a rotor (6) is accelerated by driving a turbine wheel (7) with pressurized air at normal operating speed. Oscillations induced by imbalance, at a unit housing (5) are measured during rotation of the rotor with the normal speed. Phase position of the oscillations is determined. The measured oscillations and the phase position are utilized to determine imbalance of the rotor to be adjusted. An independent claim is also included for a device for dynamic measurement of imbalance of a rotor of a turbo supercharger core assembly.

Description

Die Erfindung betrifft ein Verfahren und eine Vorrichtung zum dynamischen Messen der Unwucht des Rotors einer Turbolader-Rumpfgruppe, wobei der Rotor ein Turbinenrad, ein Verdichterrad und eine Welle umfasst, die in einem Mittelgehäuse der Turbolader-Rumpfgruppe gelagert ist.The invention relates to a method and apparatus for dynamically measuring the imbalance of the rotor of a turbocharger body group, the rotor comprising a turbine wheel, a compressor wheel and a shaft mounted in a center housing of the turbocharger body group.

Abgasgetriebene Turbolader haben einen Rotor, der im Betrieb mit einer sehr hohen Drehzahl von oft über 100.000 Umdrehungen pro Minute dreht und daher zur Vermeidung von Geräuschen und zu hohen Lagerbelastungen sehr genau ausgewuchtet werden muss. Der Rotor besteht in der Regel aus einer in einem Lagergehäuse gelagerten Welle, die an einem Ende ein Turbinenrad und am anderen Ende ein Verdichterrad trägt. Die Messung der Unwucht des Rotors erfolgt aus Genauigkeitsgründen in der Regel bei einer im wesentlichen der normalen Arbeitsgeschwindigkeit entsprechenden Winkelgeschwindigkeit.Exhaust-driven turbochargers have a rotor that rotates in operation at a very high speed of often over 100,000 revolutions per minute and therefore must be balanced very precisely to avoid noise and excessive bearing loads. As a rule, the rotor consists of a shaft mounted in a bearing housing which carries a turbine wheel at one end and a compressor wheel at the other end. The measurement of the imbalance of the rotor is made for accuracy reasons usually at a substantially normal operating speed corresponding angular velocity.

Aus EP 0 426 676 B1 ist ein Verfahren der angegebenen Art zum dynamischen Ausgleich der Unwucht des Hochgeschwindigkeitsrotor eines abgasangetriebenen Turboladers bekannt, bei dem das Turbolader-Mittelgehäuse, in dem der Rotor gelagert ist, mit einem das Turbinenrad umschließenden Gehäuse und einem das Verdichterrad umschließenden Gehäuse fest verbunden wird und die so gebildete Einheit mit Hilfe von biegsamen Balgschläuchen, die an den beiden Gehäusen angreifen, in einem Rahmen in allen drei Raumrichtungen bewegbar weich gelagert wird. An den Gehäusen sind Beschleunigungsaufnehmer angeordnet, deren Beschleunigungssignale in Verbindung mit einem optisch gemessenen Phasenwinkel zur Bestimmung von Größe und Lage der Unwucht verarbeitet werden. Hierbei beeinträchtigen die an dem Turbolader-Mittelgehäuse angebrachten Gehäuseteile das Schwingungsverhalten und damit die Messung der Unwucht erheblich.Out EP 0 426 676 B1 is a method of the type specified for dynamically balancing the imbalance of the high-speed rotor of an exhaust-driven turbocharger known in which the turbocharger center housing in which the rotor is mounted, with a turbine housing enclosing the housing and the compressor enclosing housing is firmly connected and the so formed unit by means of flexible bellows hoses, which engage the two housings, is movably stored soft in a frame in all three spatial directions. Accelerometers are arranged on the housings whose acceleration signals are processed in conjunction with an optically measured phase angle to determine the size and position of the imbalance. Here, attached to the turbocharger center housing housing parts affect the vibration behavior and thus the measurement of imbalance considerably.

Bei einem weiteren aus DE 10 2005 053 786 A1 bekannten Verfahren zum dynamischen Messen der Unwucht eines mit hoher Winkelgeschwindigkeit drehenden Turbolader-Rotors, der in einem separaten Mittelgehäuse gelagert ist, wird das Mittelgehäuse mittels Spannpratzen an einem Lagerring befestigt, der unter Zwischenschaltung federnd nachgiebiger Elemente an dem Turbinengehäuse derart befestigt, dass das Mittelgehäuse mit dem Lagerring relativ zum Turbinengehäuse in drei Raumrichtungen bewegbar ist und das Turbinenrad des Rotor in einer zum Antrieb geeigneten Arbeitslage im Turbinengehäuse angeordnet ist. Das Verdichterrad ist zum Schutz mit einer Käfighaube abgedeckt. Zur Beschleunigung des Rotors auf eine im Wesentlichen normale Arbeitsgeschwindigkeit wird das Turbinenrad des Rotors mit Luft angetrieben. Während der Rotor mit verschiedenen Drehzahlen und einer im wesentlichen normalen Arbeitsgeschwindigkeit dreht, erfolgt das Messen der durch Unwucht induzierten Schwingungen und die Bestimmung der Phasenlage der induzierten Schwingungen zur Winkellage des Rotors, um daraus die auszugleichende Unwucht des Rotors zu bestimmen. Dieses Verfahren eignet sich nicht für eine automatische Betriebsweise. Auch hat sich gezeigt, dass die nicht den Betriebsbedingungen entsprechende Anordnung des Verdichterrades die Messgenauigkeit beeinträchtigt.At another DE 10 2005 053 786 A1 known method for dynamically measuring the imbalance of a high angular velocity rotating turbocharger rotor, which is mounted in a separate center housing, the center housing is fixed by means of clamping claws on a bearing ring which secured with the interposition of resilient elements to the turbine housing such that the center housing with the bearing ring is movable relative to the turbine housing in three spatial directions and the turbine wheel of the rotor is arranged in a suitable operating position in the turbine housing. The compressor wheel is covered with a cage hood for protection. To accelerate the rotor to a substantially normal operating speed, the turbine wheel of the rotor is driven with air. While the rotor rotates at different speeds and at a substantially normal operating speed, the measurement of the vibrations induced by imbalance and the determination of the phase angle of the induced vibrations to the angular position of the rotor to determine the unbalance of the rotor to be compensated. This method is not suitable for automatic operation. It has also been found that the arrangement of the compressor wheel that does not correspond to the operating conditions affects the measuring accuracy.

Aus EP 0 922 950 B1 ist ein Verfahren zur Bestimmung der Unwucht eines Aggregats mit einem in einem Gehäuseelement gelagerten Rotor bekannt, bei dem das Aggregat mit dem Gehäuseelement über ein elastisches Lagermittel an einer Lagereinrichtung gelagert und der Rotor in Drehung versetzt wird, wobei das Drehverhalten des Rotors und Schwingungen erfasst und ausgewertet werden. Die Schwingungserfassung erfolgt hierbei an zumindest einer Stelle des Gehäuseelements mit einem kontaktlosen Schwingungssensor, beispielsweise einem Laservibrometer.Out EP 0 922 950 B1 a method for determining the imbalance of an aggregate with a rotor mounted in a housing member is known, in which the unit is mounted with the housing member via an elastic bearing means to a bearing means and the rotor is rotated, wherein the rotational behavior of the rotor and detects vibrations and be evaluated. In this case, the vibration detection takes place at at least one point of the housing element with a contactless vibration sensor, for example a laser vibrometer.

Der Erfindung liegt die Aufgabe zugrunde, ein Verfahren der eingangs genannten Art anzugeben, welches eine automatische Durchführung der Unwuchtmessung mit großer Genauigkeit und unter betriebsnahen Bedingungen ermöglicht. Es ist weiterhin Aufgabe der Erfindung, eine zur Durchführung des Verfahrens besonders geeignete, einfache und kostengünstige Vorrichtung zu schaffen.The invention has for its object to provide a method of the type mentioned above, which allows automatic implementation of the imbalance measurement with high accuracy and operating conditions. It is Another object of the invention to provide a particularly suitable for carrying out the method, simple and inexpensive device.

Die genannte Aufgabe wird hinsichtlich des Verfahrens durch die in Patentanspruch 1 angegebenen Merkmale und hinsichtlich der Vorrichtung durch die in Patentanspruch 7 angegebenen Merkmale gelöst. Vorteilhafte Ausgestaltungen des Verfahrens sind in den Ansprüchen 2 bis 6 und der Vorrichtung in den Ansprüchen 8 bis 15 angegeben.The above object is achieved with respect to the method by the features specified in claim 1 and in terms of the device by the features specified in claim 7. Advantageous embodiments of the method are given in claims 2 to 6 and the device in claims 8 to 15.

Nach der Erfindung umfasst das Verfahren zum dynamischen Messen der Unwucht des Rotors einer Turbolader-Rumpfgruppe, bei welcher der Rotor ein Turbinenrad, ein Verdichterrad und eine Welle aufweist, die in einem Mittelgehäuse der Turbolader-Rumpfgruppe gelagert ist, die Schritte:

  • Anordnen eines Turbinengehäuses und eines Verdichtergehäuse in einem einen Zwischenraum bildenden Abstand voneinander an einem Maschinenbett,
  • Befestigen eines ersten Lagerelements an dem Turbinengehäuse auf der dem Verdichtergehäuse zugekehrten Seite mittels axial und radial federnder Mittel, Befestigen eines zweiten Lagerelements an dem Verdichtergehäuse auf der dem Turbinengehäuse zugekehrten Seite mittels axial und radial federnder Mittel,
  • Positionieren und Halten der Turbolader-Rumpfgruppe in dem Zwischenraum und zwischen dem ersten und zweiten Lagerelement der Turbolader-Rumpfgruppe mittels einer an dem Mittelgehäuse angreifenden Haltevorrichtung,
  • Verringern des Abstands zwischen dem Turbinengehäuses und dem Verdichtergehäuse und Einspannen des Mittelgehäuses zwischen dem ersten und zweiten Lagerelement derart, dass das Mittelgehäuse in wenigstens zwei Raumrichtungen federnd gelagert ist und das Verdichtergehäuse das Verdichterrad und das Turbinengehäuse das Turbinenrad mit einem die Federbewegungen in wenigstens zwei Raumrichtungen zulassenden Abstand umgibt, Entfernen der Haltevorrichtung von dem Mittelgehäuse,
  • Anordnen wenigstens eines Schwingungssensors zur Messung der Schwingungen des Mittelgehäuses,
  • Verbinden des Turbinengehäuses mit einer Druckluftquelle und Beschleunigen des Rotors durch Antreiben des Turbinenrads mit Druckluft auf eine im wesentlichen normale Arbeitsgeschwindigkeit,
  • Messen der durch Unwucht induzierten Schwingungen am Mittelgehäuse während der Rotor mit einer im wesentlichen normalen Arbeitsgeschwindigkeit dreht, Bestimmung der Phasenlage der durch Unwucht induzierten Schwingungen zur Winkellage des Rotors bei den Messdrehzahlen, bei denen die durch Unwucht induzierten Schwingungen gemessen werden,
  • Verwendung der gemessenen durch Unwucht induzierten Schwingungen und der Phasenlage, um die auszugleichende Unwucht des Rotors zu bestimmen.
According to the invention, the method of dynamically measuring the rotor imbalance of a turbocharger body group, wherein the rotor comprises a turbine wheel, a compressor wheel, and a shaft supported in a center housing of the turbocharger body group, comprises the steps of:
  • Arranging a turbine housing and a compressor housing at a gap forming a space on a machine bed,
  • Fixing a first bearing element to the turbine housing on the side facing the compressor housing by means of axially and radially resilient means, fastening a second bearing element to the compressor housing on the side facing the turbine housing by means of axially and radially resilient means,
  • Positioning and maintaining the turbocharger body group in the space and between the first and second bearing elements of the turbocharger body group by means of a holding device acting on the center housing,
  • Reducing the distance between the turbine housing and the compressor housing and clamping the center housing between the first and second bearing element such that the center housing is resiliently mounted in at least two spatial directions and the compressor housing the compressor and the turbine housing the turbine wheel with one of the spring movements in at least two spatial directions permitting Distance surrounds, removing the holding device from the middle housing,
  • Arranging at least one vibration sensor for measuring the vibrations of the middle housing,
  • Connecting the turbine housing to a source of pressurized air and accelerating the rotor by driving the turbine wheel with compressed air to a substantially normal operating speed;
  • Measuring the imbalance-induced vibrations at the center housing while the rotor rotates at a substantially normal operating speed, determining the phase angle of the imbalance-induced oscillations to the angular position of the rotor at the measurement speeds at which the vibrations induced by imbalance are measured,
  • Using the measured vibrations induced by imbalance and the phase position to determine the unbalance of the rotor to be compensated.

Das erfindungsgemäße Verfahren ermöglicht eine vollautomatische Messung der Unwucht eines Turboladerrotors unter betriebsähnlichen Bedingungen, d.h. bei Belastung. Dennoch ist die schwingfähige Masse vorteilhaft klein, so dass große Schwingungsamplituden erzielt werden können. Durch gekuppelte Gehäuse verursachte Schwingungen und Resonanzen, welche die Messgenauigkeit beeinträchtigen, werden vermieden. Das Verdichtergehäuse benötigt im Gegensatz zum Turbinengehäuse keine Anschlüsse, da die Luft aus der Atmosphäre angesaugt und in diese frei zurückströmen kann, kann aber ohne Nachteil auch an Schläuche angeschlossen sein. Die Vorrichtung zur Durchführung des Verfahrens ist kostengünstig, weil keine komplizierte Spannvorrichtung zum Festspannen des Mittelgehäuses während der Messung benötigt wird. Entsprechend ist die Handhabung beim Einsetzen oder Entnehmen der Turbolader-Rumpfgruppe einfach und automatisch, beispielsweise mit Hilfe eines ein positionsgenau steuerbaren Handhabungsgreifers durchführbar.The method according to the invention enables a fully automatic measurement of the imbalance of a turbocharger rotor under operating-like conditions, i. under pressure. Nevertheless, the oscillatory mass is advantageously small, so that large vibration amplitudes can be achieved. Oscillations and resonances caused by coupled housings, which affect measurement accuracy, are avoided. The compressor housing requires in contrast to the turbine housing no connections, because the air can be sucked from the atmosphere and flow freely back into this, but can be connected to hoses without any disadvantage. The apparatus for carrying out the method is inexpensive, because no complicated clamping device for clamping the center housing during the measurement is needed. Accordingly, the handling when inserting or removing the turbocharger fuselage group is simple and automatic, for example, by means of a positionally precisely controllable handling gripper feasible.

Nach einem weiteren Vorschlag der Erfindung können die Schwingungen des Mittelgehäuses berührungslos gemessen werden, indem beispielsweise ein Laservibrometer zum Messen der Schwingungen verwendet wird. Auf diese Weise können die Lagerelemente sehr einfach und besonders leicht ausgeführt werden, da sie keine Mittel zur Befestigung von Schwingungsaufnehmern benötigen.According to a further proposal of the invention, the vibrations of the center housing can be measured without contact, for example by using a laser vibrometer to measure the vibrations. In this way, the bearing elements can be very easily and very easily performed because they do not need any means to attach vibration sensors.

Nach der Erfindung umfasst eine vorteilhafte Vorrichtung zum dynamischen Messen der Unwucht des Rotors einer Turbolader-Rumpfgruppe, bei welcher der Rotor ein Turbinenrad, ein Verdichterrad und eine Welle aufweist, die in einem Mittelgehäuse der Turbolader-Rumpfgruppe gelagert ist, ein zur Aufnahme des Turbinenrads ausgebildetes, an einem Maschinenbett gelagertes Turbinengehäuse, das zum Beschleunigen des Rotors durch Antreiben des Turbinenrads mittels Druckluft mit einer Druckluftquelle verbindbar ist und das ein mittels Federn in wenigstens zwei Raumrichtungen bewegbar gelagertes erstes Lagerelement aufweist, an dem die Turbinenseite des Mittelgehäuses in einem Bewegungen des Mittelgehäuses und des Turbinenrads in den wenigstens zwei Raumrichtungen zulassenden Abstand von dem Turbinengehäuse abstützbar ist, und ein zur Aufnahme des Verdichterrads ausgebildetes, an dem Maschinenbett gelagertes Verdichtergehäuse, das ein mittels Federn in wenigstens zwei Raumrichtungen bewegbar gelagertes zweites Lagerelement aufweist, an dem die Verdichterseite des Mittelgehäuses in einem Bewegungen des Mittelgehäuses und des Verdichterrads in den wenigstens zwei Raumrichtungen zulassenden Abstand von dem Verdichtergehäuse abstützbar ist, und durch eine an dem Mittelgehäuse angreifende, lösbare Haltevorrichtung, durch welche die Turbolader-Rumpfgruppe zwischen dem Turbinengehäuse und dem Verdichtergehäuse festhaltbar ist, wobei das Turbinengehäuse und/oder das Verdichtergehäuse gegenüber dem Maschinenbett in axialer Richtung derart verstellbar ist, dass der Abstand zwischen dem Turbinengehäuse und dem Verdichtergehäuse verändert und das Mittelgehäuse zwischen dem ersten und zweiten Lagerelement eingespannt werden kann.According to the invention, an advantageous apparatus for dynamically measuring the imbalance of the rotor of a turbocharger body group, wherein the rotor comprises a turbine wheel, a compressor wheel and a shaft which is mounted in a center housing of the turbocharger body group, comprises a turbine wheel adapted to receive the turbine wheel , Turbine housing mounted on a machine bed, which is connected for accelerating the rotor by driving the turbine wheel by means of compressed air to a compressed air source and having a means of springs in at least two spatial directions movably mounted first bearing element on which the turbine side of the center housing in a movement of the center housing and of the turbine wheel in the at least two spatial directions permitting distance from the turbine housing can be supported, and a trained for receiving the compressor wheel, mounted on the machine bed compressor housing, which moves by means of springs in at least two spatial directions having mounted second bearing element, on which the compressor side of the center housing in a movement of the center housing and the compressor in the at least two spatial directions permitting distance from the compressor housing is supported, and by acting on the center housing, releasable holding device through which the turbocharger body group between the turbine housing and the compressor housing is fixed, wherein the turbine housing and / or the compressor housing in the axial direction is adjustable relative to the machine bed so that the distance between the turbine housing and the compressor housing changed and the middle housing between the first and second bearing element can be clamped.

Die erfindungsgemäße Vorrichtung ist einfach zu handhaben und ermöglicht eine vollautomatische Durchführung der Unwuchtmessung. Die Mittel zur Aufnahme der Turbolader-Rumpfgruppe sind einfach und ermöglichen eine kostengünstige Herstellung der Vorrichtung. Das erste und/oder zweite Lagerelement kann ein einfach herzustellender Lagerring sein, der eine Zentrierfläche des Mittelgehäuses umgreift. Am Turbinengehäuse kann vorteilhaft eine flexible Dichtung angebracht, die dichtend mit dem Mittelgehäuse verbindbar ist.The device according to the invention is easy to handle and allows a fully automatic implementation of the imbalance measurement. The means for receiving the turbocharger hull group are simple and allow a cost effective Production of the device. The first and / or second bearing element may be a simple to manufacture bearing ring which engages around a centering surface of the center housing. On the turbine housing can advantageously be attached a flexible seal which is sealingly connectable to the middle housing.

Zur Schwingungsmessung kann nach der Erfindung dem Mittelgehäuse ein berührungslos messender Schwingungssensor, insbesondere ein Laservibrometer zugeordnet sein.For vibration measurement can be assigned to the center housing a non-contact measuring vibration sensor according to the invention, in particular a laser vibrometer.

Als Haltevorrichtung zum Halten der Turbolader-Rumpfgruppe während des Spannvorgangs kann nach der Erfindung eine an dem Turbinengehäuse oder dem Verdichtergehäuse angeordnete Spannvorrichtung oder ein positionsgenau steuerbarer Handhabungsgreifer dienen. Weiterhin kann zum automatischen Spannen das Turbinengehäuse und/oder das Verdichtergehäuse durch einen Aktor in axialer Richtung verstellbar sein.As a holding device for holding the turbocharger body group during the tensioning operation can be used according to the invention arranged on the turbine housing or the compressor housing clamping device or a positionally controllable handling gripper. Furthermore, the turbine housing and / or the compressor housing can be adjusted by an actuator in the axial direction for automatic clamping.

Die Erfindung wird nachfolgend anhand eines Ausführungsbeispiels näher erläutert, das in der Zeichnung dargestellt ist. Die Zeichnung zeigt schematisch die Gestaltung einer Unwuchtmessvorrichtung mit darin angeordneter Turbolader-Rumpfgruppe.The invention will be explained in more detail with reference to an embodiment which is shown in the drawing. The drawing shows schematically the design of an unbalance measuring device with arranged therein turbocharger body group.

Die dargestellte Unwuchtmessvorrichtung umfasst ein Turbinengehäuse 1, ein Verdichtergehäuse 2 und ein Maschinenbett 3. Die Unwuchtmessvorrichtung ist zur Aufnahme einer Turbolader-Rumpfgruppe 4 bestimmt und eingerichtet, die ein Mittelgehäuse 5 mit einem darin gelagerten Rotor 6 umfasst, der an seinem einen Ende ein Turbinenrad 7 und an seinem anderen Ende ein Verdichterrad 8 hat. Das Mittelgehäuse 5 weist auf der dem Verdichterrad 8 zugewandten Seite einen tellerförmigen Flansch 9 auf, an dem die Turbolader-Rumpfgruppe 4 gespannt werden kann. Weiterhin ist an den beiden Stirnseiten des Mittelgehäuses jeweils ein zylindrischer Ringbund 10, 11 ausgebildet. Zwischen dem Turbinenrad 7 und dem Ringbund 10 ist ein Hitzeschutzschild 12 angeordnet. Das Turbinengehäuse 1 der Unwuchtmessvorrichtung weist eine Turbinenkammer 13, einen diese umgebenden Spiralkanal 14 mit nicht dargestelltem Einlass und einen zentralen Auslasskanal 15 auf. An dem Turbinengehäuses 1 ist auf der dem Verdichtergehäuse 2 zugekehrten Seite konzentrisch zur Turbinenachse ein ringförmiges erstes Lagerelement 16 angeordnet, welches axial und radial beweglich mittels Federn 17 an dem Turbinengehäuses 1 gehalten und abgestützt ist. Das Lagerelement 16 weist eine zur Turbinenachse orthogonale Anlagefläche 18 für das Mittelgehäuse 5 bzw. das Hitzeschutzschild 12 auf und kann bei Bedarf zusätzlich mit einer Zentrierfläche versehen sein.The unbalance measuring apparatus shown comprises a turbine housing 1, a compressor housing 2 and a machine bed 3. The unbalance measuring device is intended and arranged to receive a turbocharger body group 4 comprising a center housing 5 with a rotor 6 mounted therein, a turbine wheel 7 at one end thereof and at its other end a compressor 8 has. The middle housing 5 has on the compressor wheel 8 side facing a plate-shaped flange 9, on which the turbocharger body group 4 can be stretched. Furthermore, in each case a cylindrical annular collar 10, 11 is formed on the two end faces of the center housing. Between the turbine wheel 7 and the annular collar 10, a heat shield 12 is arranged. The turbine housing 1 of the unbalance measuring device has a turbine chamber 13, a surrounding spiral channel 14 with not shown inlet and a central outlet channel 15. On the turbine housing 1, an annular first bearing element 16 is arranged on the side facing the compressor housing 2 concentric with the turbine axis, which is held and supported axially and radially movably by means of springs 17 on the turbine housing 1. The bearing element 16 has a bearing surface 18 orthogonal to the turbine axis for the middle housing 5 and the heat shield 12 and may additionally be provided with a centering surface if required.

Das Verdichtergehäuse 2 weist auf der dem Turbinengehäuse 1 zugekehrten Seite eine Verdichterkammer 20 mit einem zentralen Einlasskanal 21 und einem Spiralkanal 22 auf, der sich an den radial äußeren Rand der Verdichterkammer 20 anschließt. Der Auslass des Spiralkanals 22 ist nicht dargestellt. Das Verdichtergehäuse 2 ist weiterhin mit einer Spannvorrichtung 23 mit drehbaren Spannhebeln 24 versehen. Auf der dem Turbinengehäuses 1 zugekehrten Seite weist das Verdichtergehäuse 2 ein ringförmiges zweites Lagerelement 25 auf, das konzentrisch zur Verdichterachse angeordnet und in radialer und axialer Richtung mittels Federn 26 am Verdichtergehäuse 2 abgestützt und gehalten ist. Das Lagerelement 25 hat eine zur Verdichterachse orthogonale Anlagefläche 27 und eine zylindrische Zentrierbohrung 28.The compressor housing 2 has, on the side facing the turbine housing 1, a compression chamber 20 with a central inlet channel 21 and a spiral channel 22, which adjoins the radially outer edge of the compression chamber 20. The outlet of the spiral channel 22 is not shown. The compressor housing 2 is further provided with a clamping device 23 with rotatable clamping levers 24. On the turbine housing 1 side facing the compressor housing 2, an annular second bearing element 25 which is arranged concentrically to the compressor axis and supported and held in the radial and axial directions by means of springs 26 on the compressor housing 2. The bearing element 25 has a contact surface orthogonal to the compressor axis 27 and a cylindrical centering bore 28.

Das Turbinengehäuse 1 ist durch starre Befestigungsmittel 30 mit dem Maschinenbett 3 verbunden. Die Befestigungsmittel 30 sind lösbar und ermöglichen nach dem Lösen ein Bewegen des Turbinengehäuses 1 in axialer Richtung, um den Abstand zwischen dem Turbinengehäuse 1 und dem Verdichtergehäuse 2 auf das für die Unwuchtmessung oder für das Einsetzen und Entnehmen jeweils erforderliche Maß ändern zu können. Alternativ kann auch die Lagerung des Verdichtergehäuses 2 mit einer zur Änderung des Abstands erforderlichen Bewegbarkeit ausgebildet sein. Als Befestigungsmittel und Mittel zum Bewegen des Turbinengehäuses 1 oder des Verdichtergehäuses 2 kann ein blockierbarer Aktor, z.B. ein pneumatischer oder hydraulischer Hubzylinder oder ein Linearmotor verwendet werden.The turbine housing 1 is connected to the machine bed 3 by rigid attachment means 30. The fasteners 30 are releasable and allow after loosening a movement of the turbine housing 1 in the axial direction to change the distance between the turbine housing 1 and the compressor housing 2 to the measure required for the imbalance measurement or for insertion and removal. Alternatively, the storage of the compressor housing 2 may be formed with a mobility required for changing the distance. As a fastener and means of moving the turbine housing 1 or the compressor housing 2, a blockable actuator, such as a pneumatic or hydraulic lifting cylinder or a linear motor can be used.

Zur Erfassung von Schwingungen ist an Maschinenbett 3 ein berührungslos messender Schwingungsaufnehmer 31 angebracht, welcher Schwingungen des Mittelgehäuses 5 der Turbolader-Rumpfgruppe 4 erfasst.For detecting vibrations, a non-contact measuring vibration sensor 31 is attached to the machine bed 3, which detects vibrations of the center housing 5 of the turbocharger body group 4.

Für das Einsetzen der Turbolader-Rumpfgruppe 4 in die Unwuchtmessvorrichtung wird zuvor das Turbinengehäuse 1 an dem Maschinenbett 3 gelöst und vom Verdichtergehäuse 2 axial soweit entfernt, bis der für das Einsetzen notwendige Abstand zwischen Turbinen- und Verdichtergehäuse besteht. Danach wird die Turbolader-Rumpfgruppe 4 in die Unwuchtmessvorrichtung eingesetzt und zunächst an dem Verdichtergehäuse 2 angebracht, indem die Turbolader-Rumpfgruppe 4 mit dem Verdichterrad 8 in das Verdichtergehäuse 2 eingesetzt und das Mittelgehäuse 5 mit Hilfe der Spannvorrichtung 23 an dem Flansch 9 gespannt wird. Das Mittelgehäuse 5 ist hierdurch an dem Verdichtergehäuse 2 vorausgerichtet gehalten. Der Ringbund 11 des Mittelgehäuses 5 liegt axial an der Anlagefläche 27 des Lagerelements 25 an und greift in die Zentrierbohrung 28 ein.For the onset of the turbocharger fuselage group 4 in the unbalance measuring device, the turbine housing 1 is previously solved on the machine bed 3 and axially removed from the compressor housing 2 until the necessary for the insertion distance between the turbine and compressor housing. Thereafter, the turbocharger body group 4 is inserted into the unbalance measuring device and first attached to the compressor housing 2 by the turbocharger body group 4 is inserted with the compressor 8 in the compressor housing 2 and the middle housing 5 is clamped by means of the clamping device 23 to the flange 9. The middle housing 5 is thereby kept in front of the compressor housing 2. The annular collar 11 of the middle housing 5 abuts axially against the contact surface 27 of the bearing element 25 and engages in the centering bore 28.

Nach dem Festspannen der Turbolader-Rumpfgruppe 4 an dem Verdichtergehäuse 2 wird das Turbinengehäuse 1 in die in der Zeichnung dargestellte Position gebracht und am Maschinenbett 3 befestigt. Durch einen einstellbaren Anschlag 32 kann die geeignete Stellung des Turbinengehäuses 1 am Maschinenbett festgelegt sein. In dieser Stellung gelangt das an dem Ringbund 10 anliegende Hitzeschutzschild 12 des Mittelgehäuses 5 zur Ablage an dem Lagerelement 16 und die Federn 17 und 26 werden in axialer Richtung soweit gespannt, dass das Mittelgehäuse 5 sicher und begrenzt beweglich von den Lagerelementen 16, 25 gehalten ist. In dieser Position haben der Rotor 6 und das Mittelgehäuse 5 gegenüber dem Turbinengehäuse 1 und dem Verdichtergehäuse 2 jeweils einen solchen Abstand, dass es infolge der während eines Messlaufs auftretenden Schwingungen nicht zu einer Berührung zwischen ihnen kommt. Nachdem das Mittelgehäuse 5 zwischen den Lagerelementen 15, 25 eingespannt ist, wird die Spannvorrichtung 23 geöffnet, wodurch die Spannhebel 24, wie in der unteren Hälfte der Zeichnung gezeigt, von dem Flansch 9 entfernt werden. Die Turbolader-Rumpfgruppe 4 kann nun zusammen mit den Lagerelementen 16, 25 in den Federn 17, 26 frei schwingen, wie es für eine genaue Messung der Unwuchten des Rotors 6 erforderlich ist.After tightening the turbocharger body group 4 to the compressor housing 2, the turbine housing 1 is brought into the position shown in the drawing and attached to the machine bed 3. By an adjustable stop 32, the appropriate position of the turbine housing 1 can be set on the machine bed. In this position, the voltage applied to the annular collar 10 heat shield 12 of the middle housing 5 passes to the storage on the bearing element 16 and the springs 17 and 26 are tensioned in the axial direction so far that the middle housing 5 is securely and limited movable from the bearing elements 16, 25 is held , In this position, the rotor 6 and the middle housing 5 have opposite the turbine housing 1 and the compressor housing 2 each such a distance that it does not come to a contact between them due to the vibrations occurring during a measurement run. After the center housing 5 is clamped between the bearing elements 15, 25, the clamping device 23 is opened, whereby the clamping lever 24, as shown in the lower half of the drawing, are removed from the flange 9. The turbocharger fuselage group 4 can now vibrate freely together with the bearing elements 16, 25 in the springs 17, 26, as required for an accurate measurement of the imbalances of the rotor 6.

Alternativ kann das Einsetzen und Halten der Turbolader-Rumpfgruppe 4 beim Spannen mittels eines positionsgenau steuerbaren Handhabungsgreifers erfolgen, der das Mittelgehäuse greift, einsetzt und in Position hält. Nach Beendigung des Spannvorgangs wird der Handhabungsgreifer geöffnet und vom Mittelgehäuse entfernt.Alternatively, the insertion and holding of the turbocharger fuselage group 4 can take place during clamping by means of a positionally controllable handling gripper, which grips, inserts and holds the middle housing in position. After completion of the clamping operation of the handling gripper is opened and removed from the center housing.

Zur Messung einer Unwucht des Rotors 6 wird das Turbinenrad 7 mit Druckluft angetrieben und der Rotor 6 bis auf eine im Wesentlichen seiner normalen Arbeitsgeschwindigkeit entsprechenden Drehzahl beschleunigt. Zur Vermeidung von Blasgeräuschen kann am Turbinengehäuse 1 eine flexible Dichtung angebracht sein, die sich dichtend an das Hitzeschutzschild anlegt.To measure an imbalance of the rotor 6, the turbine wheel 7 is driven by compressed air and the rotor 6 is accelerated to a speed substantially corresponding to its normal operating speed. To avoid blast noise, a flexible seal may be attached to the turbine housing 1, which bears sealingly against the heat shield.

Durch eine vorhandene Unwucht des beschleunigten Rotors 6 werden in die schwingende Masse aus Turbolader-Rumpfgruppe 4 und Lagerelementen 16, 25 Schwingungen induziert, die mit Hilfe des Schwingungsaufnehmers 31 bei verschiedenen Drehzahlen gemessen werden. Gleichzeitig wird durch einen Drehwinkelgeber die jeweilige Phasenlage der gemessenen Schwingungen in Bezug auf den Rotor 6 bestimmt. Aus den gemessenen Werten wird dann mit Hilfe eines elektronische Rechners Winkellage und Größe der auszugleichenden Unwucht berechnet.By an existing imbalance of the accelerated rotor 6 vibrations are induced in the oscillating mass of turbocharger fuselage group 4 and bearing elements 16, 25, which are measured by means of the vibration sensor 31 at different speeds. At the same time, the respective phase position of the measured vibrations with respect to the rotor 6 is determined by a rotary encoder. From the measured values, the angular position and size of the imbalance to be compensated is then calculated with the aid of an electronic computer.

Claims (15)

Verfahren zum dynamischen Messen der Unwucht des Rotors einer Turbolader-Rumpfgruppe, bei welcher der Rotor ein Turbinenrad, ein Verdichterrad und eine Welle aufweist, die in einem Mittelgehäuse der Turbolader-Rumpfgruppe gelagert ist, gekennzeichnet durch die Schritte: Anordnen eines Turbinengehäuses (1) und eines Verdichtergehäuse (2) in einem einen Zwischenraum bildenden Abstand voneinander an einem Maschinenbett (3), Befestigen eines ersten Lagerelements (16) an dem Turbinengehäuse (1) auf der dem Verdichtergehäuse (2) zugekehrten Seite mittels axial und radial federnder Mittel, Befestigen eines zweiten Lagerelements (25) an dem Verdichtergehäuse (2) auf der dem Turbinengehäuse (1) zugekehrten Seite mittels axial und radial federnder Mittel, Positionieren und Halten der Turbolader-Rumpfgruppe (4) in dem Zwischenraum und zwischen dem ersten und zweiten Lagerelement (16, 25) der Turbolader-Rumpfgruppe (4) mittels einer an dem Mittelgehäuse (5) angreifenden Haltevorrichtung, Verringern des Abstands zwischen dem Turbinengehäuses (1) und dem Verdichtergehäuse (2) und Einspannen des Mittelgehäuses (5) zwischen dem ersten und zweiten Lagerelement (16, 25) derart, dass das Mittelgehäuse (5) in wenigstens zwei Raumrichtungen federnd gelagert ist und das Verdichtergehäuse (2) das Verdichterrad (8) und das Turbinengehäuse (1) das Turbinenrad (7) mit einem die Federbewegungen in wenigstens zwei Raumrichtungen zulassenden Abstand umgibt, Entfernen der Haltevorrichtung von dem Mittelgehäuse, Anordnen wenigstens eines Schwingungssensors (31) zur Messung der Schwingungen des Mittelgehäuses (5), Verbinden des Turbinengehäuses (1) mit einer Druckluftquelle und Beschleunigen des Rotors (6) durch Antreiben des Turbinenrads (7) mit Druckluft auf eine im wesentlichen normale Arbeitsgeschwindigkeit, Messen der durch Unwucht induzierten Schwingungen am am Mittelgehäuse (5) während der Rotor (6) mit einer im wesentlichen normalen Arbeitsgeschwindigkeit dreht, Bestimmung der Phasenlage der durch Unwucht induzierten Schwingungen zur Winkellage des Rotors (6) bei den Messdrehzahlen, bei denen die durch Unwucht induzierten Schwingungen gemessen werden, Verwendung der gemessenen durch Unwucht induzierten Schwingungen und der Phasenlage, um die auszugleichende Unwucht des Rotors (6) zu bestimmen. A method of dynamically measuring the imbalance of the rotor of a turbocharger body group, wherein the rotor comprises a turbine wheel, a compressor wheel, and a shaft supported in a center housing of the turbocharger body group, characterized by the steps of: Arranging a turbine housing (1) and a compressor housing (2) at an interval forming a gap on a machine bed (3), Fastening a first bearing element (16) to the turbine housing (1) on the side facing the compressor housing (2) by means of axially and radially resilient means, Attaching a second bearing element (25) to the compressor housing (2) on the side facing the turbine housing (1) by means of axially and radially resilient means, Positioning and maintaining the turbocharger body group (4) in the space and between the first and second bearing elements (16, 25) of the turbocharger body group (4) by means of a holding device acting on the center housing (5), Reducing the distance between the turbine housing (1) and the compressor housing (2) and clamping the middle housing (5) between the first and second bearing element (16, 25) such that the center housing (5) is resiliently mounted in at least two spatial directions and the compressor housing (2) surrounds the compressor wheel (8) and the turbine housing (1) surrounds the turbine wheel (7) with a spacing permitting the spring movements in at least two spatial directions, Removing the holding device from the middle housing, Arranging at least one vibration sensor (31) for measuring the vibrations of the middle housing (5), Connecting the turbine housing (1) with a compressed air source and accelerating the rotor (6) by driving the turbine wheel (7) with Compressed air to a substantially normal operating speed, Measuring the induced by unbalance vibrations at the center housing (5) while the rotor (6) rotates at a substantially normal working speed, Determining the phase position of the vibrations induced by unbalance to the angular position of the rotor (6) at the measuring speeds at which the vibrations induced by unbalance are measured, Using the measured vibrations induced by imbalance and the phase position to determine the imbalance of the rotor (6) to be compensated. Verfahren nach Anspruch 1, dadurch gekennzeichnet, dass die Schwingungen des Mittelgehäuses (5) berührungslos gemessen werden.A method according to claim 1, characterized in that the vibrations of the center housing (5) are measured without contact. Verfahren nach Anspruch 2, dadurch gekennzeichnet, dass ein Laservibrometer zum Messen der Schwingungen verwendet wird.A method according to claim 2, characterized in that a laser vibrometer is used to measure the vibrations. Verfahren nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, dass als Haltevorrichtung eine am Turbinengehäuses (1) oder am Verdichtergehäuse (2) angeordnete Spannvorrichtung (23) verwendet wird.Method according to one of claims 1 to 3, characterized in that as a holding device on the turbine housing (1) or on the compressor housing (2) arranged clamping device (23) is used. Verfahren nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, dass als Haltevorrichtung ein positionsgenau steuerbarer Handhabungsgreifer verwendet wird.Method according to one of claims 1 to 3, characterized in that as a holding device a positionally precisely controllable handling gripper is used. Verfahren nach einem der Ansprüche 1 bis 5, dadurch gekennzeichnet, dass das Mittelgehäuse (5) von wenigstens einem der ersten und zweiten Lagerelemente (16, 25) zentriert wird.Method according to one of claims 1 to 5, characterized in that the middle housing (5) of at least one of the first and second bearing elements (16, 25) is centered. Vorrichtung zum dynamischen Messen der Unwucht des Rotors (6) einer Turbolader-Rumpfgruppe (4), bei welcher der Rotor (6) ein Turbinenrad (7), ein Verdichterrad (8) und eine Welle aufweist, die in einem Mittelgehäuse (5) der Turbolader-Rumpfgruppe (4) gelagert ist, mit einem zur Aufnahme des Turbinenrads (7) ausgebildeten, an einem Maschinenbett (3) gelagerten Turbinengehäuse (1), das zum Beschleunigen des Rotors (6) durch Antreiben des Turbinenrads (7) mittels Druckluft mit einer Druckluftquelle verbindbar ist und das ein mittels Federn (17) in wenigstens zwei Raumrichtungen bewegbar gelagertes erstes Lagerelement (16) aufweist, an dem die Turbinenseite des Mittelgehäuses (5) in einem Bewegungen des Mittelgehäuses (5) und des Turbinenrads (7) in den wenigstens zwei Raumrichtungen zulassenden Abstand von dem Turbinengehäuse (1) abstützbar ist, gekennzeichnet durch ein zur Aufnahme des Verdichterrads (8) ausgebildetes, an dem Maschinenbett (3) gelagertes Verdichtergehäuse (2), das ein mittels Federn (26) in wenigstens zwei Raumrichtungen bewegbar gelagertes zweites Lagerelement (25) aufweist, an dem die Verdichterseite des Mittelgehäuses (5) in einem Bewegungen des Mittelgehäuses (5) und des Verdichterrads (7) in den wenigstens zwei Raumrichtungen zulassenden Abstand von dem Verdichtergehäuse (2) abstützbar ist, und durch eine an dem Mittelgehäuse (5) angreifende, lösbare Haltevorrichtung, durch welche die Turbolader-Rumpfgruppe (4) zwischen dem Turbinengehäuse (1) und dem Verdichtergehäuse (2) festhaltbar ist, wobei das Turbinengehäuse (1) und das Verdichtergehäuse (2) an dem Maschinenbett (3) in axialer Richtung relativ zueinander derart verstellbar sind, dass das Mittelgehäuse (5) durch Veränderung des Abstands von Turbinengehäuse (1) und Verdichtergehäuse (2) zwischen dem ersten und zweiten Lagerelement (16, 25) eingespannt werden kann.Device for dynamically measuring the imbalance of the rotor (6) of a turbocharger body group (4), in which the rotor (6) is a turbine wheel (7), a compressor wheel (8) and a shaft, which is mounted in a center housing (5) of the turbocharger body group (4), with a turbine housing for receiving the turbine (7) formed on a machine bed (3) mounted turbine housing (1), which is for accelerating the rotor (6) by driving the turbine wheel (7) by means of compressed air to a compressed air source connectable and which by means of springs (17) in at least two spatial directions movably mounted first bearing element (16) on which the Turbine side of the central housing (5) in a movement of the center housing (5) and the turbine wheel (7) in the at least two spatial directions permitting distance from the turbine housing (1) can be supported, characterized by a for receiving the compressor wheel (8) formed on the Machine bed (3) mounted compressor housing (2) having a means of springs (26) in at least two spatial directions movably mounted second bearing element (25) on which the compressor eitte of the central housing (5) in a movement of the central housing (5) and the compressor wheel (7) in the at least two spatial directions permitting distance from the compressor housing (2) can be supported, and by a on the center housing (5) engaging, releasable holding device, by which the turbocharger body group (4) between the turbine housing (1) and the compressor housing (2) is fixed, wherein the turbine housing (1) and the compressor housing (2) on the machine bed (3) in the axial direction relative to each other are adjustable in that the middle housing (5) can be clamped between the first and second bearing element (16, 25) by changing the distance between turbine housing (1) and compressor housing (2). Vorrichtung nach Anspruch 7, dadurch gekennzeichnet, dass das erste und/oder zweite Lagerelement (16, 25) ein Lagerring ist, der eine Zentrierfläche des Mittelgehäuses (5) umgreift.Apparatus according to claim 7, characterized in that the first and / or second bearing element (16, 25) is a bearing ring which engages around a centering surface of the center housing (5). Vorrichtung nach einem der Ansprüche 7 oder 8, dadurch gekennzeichnet, dass am Turbinengehäuse (1) eine flexible Dichtung angebracht ist, die dichtend mit dem Mittelgehäuse (5) verbindbar ist.Device according to one of claims 7 or 8, characterized in that on the turbine housing (1) a flexible seal is attached, which is sealingly connectable to the central housing (5). Vorrichtung nach einem der Ansprüche 7 bis 9, dadurch gekennzeichnet, dass dem Mittelgehäuse (5) ein berührungslos messender Schwingungssensor (31) zugeordnet ist.Device according to one of claims 7 to 9, characterized in that the central housing (5) is associated with a non-contact measuring vibration sensor (31). Vorrichtung nach Anspruch 10, dadurch gekennzeichnet, dass der Schwingungssensor (31) ein Laservibrometer ist.Apparatus according to claim 10, characterized in that the vibration sensor (31) is a laser vibrometer. Vorrichtung nach einem der Ansprüche 7 bis 11, dadurch gekennzeichnet, dass die Haltevorrichtung eine an dem Turbinengehäuse (1) oder dem Verdichtergehäuse (2) angeordnete Spannvorrichtung (23) ist.Device according to one of claims 7 to 11, characterized in that the holding device is a on the turbine housing (1) or the compressor housing (2) arranged clamping device (23). Vorrichtung nach einem der Ansprüche 7 bis 11, dadurch gekennzeichnet, dass die Haltevorrichtung ein positionsgenau steuerbarer Handhabungsgreifer ist.Device according to one of claims 7 to 11, characterized in that the holding device is a positionally precisely controllable handling gripper. Vorrichtung nach einem der Ansprüche 7 bis 13, dadurch gekennzeichnet, dass an dem Maschinenbett (3) ein einstellbarer Anschlag (32) zur Begrenzung der axialen Annäherung zwischen dem Turbinengehäuse (1) und dem Verdichtergehäuse (2) angeordnet ist.Device according to one of claims 7 to 13, characterized in that on the machine bed (3) an adjustable stop (32) for limiting the axial approach between the turbine housing (1) and the compressor housing (2) is arranged. Vorrichtung nach einem der Ansprüche 7 bis 14, dadurch gekennzeichnet, dass das Turbinengehäuse (1) und/oder das Verdichtergehäuse (2) durch einen Aktor in axialer Richtung verstellbar ist.Device according to one of claims 7 to 14, characterized in that the turbine housing (1) and / or the compressor housing (2) by an actuator in the axial direction is adjustable.
EP11184723.2A 2011-10-11 2011-10-11 Method and device for dynamically measuring the imbalance of the rotor of a turbocharger core assembly Active EP2581553B9 (en)

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PL11184723T PL2581553T3 (en) 2011-10-11 2011-10-11 Method and device for dynamically measuring the imbalance of the rotor of a turbocharger core assembly
HUE11184723A HUE037381T2 (en) 2011-10-11 2011-10-11 Method and device for dynamically measuring the imbalance of the rotor of a turbocharger core assembly
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CN107560791B (en) * 2017-09-25 2023-08-15 杭州集智机电股份有限公司 Connecting rod slide block device for gas-driven centering variable-diameter rotor
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CN111656151A (en) * 2018-09-06 2020-09-11 三菱重工发动机和增压器株式会社 Vibration-damping holding device
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CN112177963A (en) * 2020-09-30 2021-01-05 张富宝 Automobile cooling fan with dynamic balance monitoring function

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HUE037381T2 (en) 2018-08-28
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EP2581553B9 (en) 2018-09-26

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