WO2024022559A1 - Balancing shaft and method for producing same - Google Patents

Balancing shaft and method for producing same Download PDF

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Publication number
WO2024022559A1
WO2024022559A1 PCT/DE2023/100550 DE2023100550W WO2024022559A1 WO 2024022559 A1 WO2024022559 A1 WO 2024022559A1 DE 2023100550 W DE2023100550 W DE 2023100550W WO 2024022559 A1 WO2024022559 A1 WO 2024022559A1
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WO
WIPO (PCT)
Prior art keywords
bearing
bearing ring
shaft
pin
journal
Prior art date
Application number
PCT/DE2023/100550
Other languages
German (de)
French (fr)
Inventor
Thomas Hußenether
Norbert Geyer
Hannes Schreyer
Original Assignee
Schaeffler Technologies AG & Co. KG
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Schaeffler Technologies AG & Co. KG filed Critical Schaeffler Technologies AG & Co. KG
Publication of WO2024022559A1 publication Critical patent/WO2024022559A1/en

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/22—Compensation of inertia forces
    • F16F15/26—Compensation of inertia forces of crankshaft systems using solid masses, other than the ordinary pistons, moving with the system, i.e. masses connected through a kinematic mechanism or gear system
    • F16F15/264—Rotating balancer shafts
    • F16F15/267—Rotating balancer shafts characterised by bearing support of balancer shafts; Lubrication arrangements

Definitions

  • the invention relates to a balancer shaft and a method for producing it.
  • the balance shaft includes:
  • Balancing shafts are used to balance mass forces and/or moments in reciprocating internal combustion engines.
  • the mass balancing of a four-cylinder in-line engine is carried out by two balancer shafts that rotate in opposite directions at twice the crankshaft speed.
  • a generic balancing shaft with an unbalanced shaft and a bearing ring mounted thereon is known from DE 10 2019 101 320 A1.
  • Another balancing shaft of the type mentioned at the beginning is currently in series use in reciprocating internal combustion engines from BMW. The different radius dimensions of the inner ring and the bearing journal are implemented on these series parts.
  • the present invention is based on the object of considerably simplifying the production of a balance shaft of the type mentioned at the beginning.
  • the enveloping circle of the bearing pin should be concentric with the centering holes, with the drive pin being eccentric to the centering holes by the radius difference R - rz and concentric with the bearing ring.
  • this geometric design significantly simplifies the machining of the unbalanced shaft into the finished part.
  • the drive pin of the finished unbalanced shaft is concentric with its centering holes.
  • the axis of rotation of the balance shaft is concentric to the drive journal and the bearing ring and - in order to avoid deformations of the bearing ring due to component tolerances - the inner radius R of the bearing ring resting on the bearing journal is larger than the enveloping circle radius rz of the bearing journal, the radius difference R - rz must be reduced by eccentric machining of the bearing journal Centering holes are compensated.
  • this eccentricity cannot be created by a simple turning process between centers in the centering holes. Rather, machining requires a complex milling process or a complex eccentric turning process with correspondingly high investment and/or manufacturing costs.
  • the present invention eliminates this disadvantage through the aforementioned eccentricity of the drive pin to the centering holes, so that the machining of the bearing seat is made possible by the comparatively simple and inexpensive turning process of the unbalanced shaft between points in the centering holes.
  • the eccentricity of the drive pin to the centering holes can also be done comparatively easily by turning or milling the drive pin using a bell tool.
  • Figure 1 shows the balance shaft in a perspective view
  • Figure 2 shows the balance shaft in longitudinal section.
  • the balance shaft comprises an unbalance shaft 1 finished from a cast or forged blank with an end drive pin 2, two bearing pins 3 and 4 and unbalance sections 5, 6 and 7.
  • the drive pin 2 takes a deep groove ball bearing (not shown) which supports the balance shaft axially in the internal combustion engine. and a gear (also not shown) driving the balance shaft.
  • the bearing journals 3, 4 only have a partially cylindrical circumference, with the cylindrical partial circumference 8 being oriented in the direction of the shaft unbalance u (see arrow in Figure 2), which is caused by the mass gravity which is eccentric to the operational axis of rotation 9 of the balancing shaft. points of both the unbalance sections 5, 6, 7 and the bearing journals 3, 4 are generated.
  • the unbalanced shaft 1 is radially supported in the internal combustion engine by means of needle bearings 10, the inner raceways 11 of which are each formed by a bearing ring 12 surrounding the bearing journal 3, 4.
  • the bearing rings 12 are also axially fastened to the unbalanced shaft 1 by means of the sheet metal springs 14, which are each axially positively connected to the bearing pin back 13 on the one hand and to the bearing ring 12 on the other.
  • the bearing rings 12 each rest with an inner radius R on the cylindrical partial circumference 8 of the bearing journals 3, 4. A deformation of the exactly cylindrical inner race 11 of each bearing ring 12 is prevented in view of unavoidable component tolerances in that the inner radius R of the bearing ring 12 is larger than the enveloping circle radius rz of the respective bearing journal 3, 4.
  • Figure 2 illustrates the geometric relationships on the dimensioned bearing pin 4, on which the enveloping circle C lying on the cylindrical partial circumference 8 is shown rotated by 90 °.
  • the enveloping circle C is concentric with a machining axis 15, which in turn is concentric with centering holes 16 and 17, which are machined into the end faces of the unbalance shaft 1.
  • the machining of each cylindrical partial circumference 8 is carried out by a simple turning process, namely by holding the unbalanced shaft 1 on tips in the centering bores 16, 17, so that the origin of the enveloping circle radius rz lies on the machining axis 15.
  • the operational axis of rotation 9 of the balance shaft is concentric with the bearing rings 12 and the drive pin 2 and eccentric to the machining axis 15 by the radius difference R - rz.
  • the final machining of the drive pin 2 is carried out using a bell tool, which moves eccentrically to the centering bores 16, 17 by the radius difference R - rz.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Acoustics & Sound (AREA)
  • Aviation & Aerospace Engineering (AREA)
  • Mechanical Engineering (AREA)
  • Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)

Abstract

The invention relates to a balancing shaft and to a method for producing same. The balancing shaft comprises: - an unbalanced shaft (1) comprising an end-side drive journal (2), end-face centering bores (16, 17) and a bearing journal (3, 4), the periphery of which is merely partially cylindrical, - and a bearing ring (12) which encloses the bearing journal, and an inner radius RL of which rests against the cylindrical partial periphery (8) of the bearing journal, the inner radius RL of the bearing ring being greater than the minimum-circumscribed-circle radius rz of the bearing journal. The minimum circumscribed circle (C) of the bearing journal is concentric with the centering bores, the drive journal being eccentric with respect to the centering bores by the difference between radii RL - rz, and being concentric with the bearing ring.

Description

Ausgleichswelle und Verfahren zu deren Herstellung Balance shaft and process for its manufacture
Die Erfindung betrifft eine Ausgleichswelle und ein Verfahren zu deren Herstellung. Die Ausgleichswelle umfasst: The invention relates to a balancer shaft and a method for producing it. The balance shaft includes:
- eine Unwuchtwelle mit einem endseitigen Antriebszapfen, stirnseitigen Zentrierbohrungen und einem Lagerzapfen, dessen Umfang lediglich teilzylindrisch ist, - an unbalanced shaft with an end drive pin, front centering bores and a bearing pin whose circumference is only partially cylindrical,
- und einen den Lagerzapfen umschließenden Lagerring, der mit einem Innenradius R am zylindrischen Teilumfang des Lagerzapfens anliegt, wobei der Innenradius R des Lagerrings größer als der Hüllkreisradius rz des Lagerzapfens ist. - and a bearing ring enclosing the bearing journal, which rests with an inner radius R on the cylindrical partial circumference of the bearing journal, the inner radius R of the bearing ring being larger than the enveloping circle radius rz of the bearing journal.
Ausgleichswellen dienen dem Ausgleich von Massenkräften und/oder -momenten in Hubkolbenbrennkraftmaschinen. Beispielsweise erfolgt der Massenausgleich einer Vierzylinder-Reihenmaschine durch zwei Ausgleichswellen, die mit doppelter Kurbelwellendrehzahl gegenläufig rotieren. Balancing shafts are used to balance mass forces and/or moments in reciprocating internal combustion engines. For example, the mass balancing of a four-cylinder in-line engine is carried out by two balancer shafts that rotate in opposite directions at twice the crankshaft speed.
Eine gattungsgemäße Ausgleichswelle mit einer Unwuchtwelle und einem darauf montierten Lagerring ist aus der DE 10 2019 101 320 A1 bekannt. Eine weitere Ausgleichswelle der eingangs genannten Art befindet sich aktuell in Hubkolbenbrennkraftmaschinen der Fa. BMW im Serieneinsatz. Die unterschiedliche Radiendimensionierung des Innenrings und des Lagerzapfens ist an diesen Serienteilen verwirklicht. A generic balancing shaft with an unbalanced shaft and a bearing ring mounted thereon is known from DE 10 2019 101 320 A1. Another balancing shaft of the type mentioned at the beginning is currently in series use in reciprocating internal combustion engines from BMW. The different radius dimensions of the inner ring and the bearing journal are implemented on these series parts.
Aus der DE 198 07 180 A1 ist eine Ausgleichswelle mit einem endseitigen Antriebszapfen bekannt, der zur Rotationsachse der Ausgleichswelle exzentrisch ist. From DE 198 07 180 A1 a balance shaft with an end drive pin is known, which is eccentric to the axis of rotation of the balance shaft.
Der vorliegenden Erfindung liegt die Aufgabe zugrunde, die Herstellung einer Ausgleichswelle der eingangs genannten Art erheblich zu vereinfachen. The present invention is based on the object of considerably simplifying the production of a balance shaft of the type mentioned at the beginning.
Die Lösung dieser Aufgabe ergibt sich durch die Merkmale des Anspruchs 1. Demnach soll der Hüllkreis des Lagerzapfens mit den Zentrierbohrungen konzentrisch sein, wobei der Antriebszapfen zu den Zentrierbohrungen um die Radiendifferenz R - rz exzentrisch und mit dem Lagerring konzentrisch ist. Wie nachfolgend erläutert, wird durch diese geometrische Gestaltung die spanende Bearbeitung der Unwuchtwelle zum Fertigteil erheblich vereinfacht. Bei der aktuellen Serienfertigung ist der Antriebszapfen der fertig bearbeiteten Unwuchtwelle mit deren Zentrierbohrungen konzentrisch. Da die betriebliche Drehachse der Ausgleichswelle konzentrisch zum Antriebszapfen und zum Lagerring ist und - zwecks Vermeidung bauteiltoleranzbedingter Verformungen des Lagerrings - der am Lagerzapfen anliegende Innenradius R des Lagerrings größer als der Hüllkreisradius rz des Lagerzapfens ist, muss die Radiendifferenz R - rz durch eine exzentrische Bearbeitung des Lagerzapfens zu den Zentrierbohrungen kompensiert werden. Diese Exzentrizität kann durch einen einfachen Drehprozess zwischen Spitzen in den Zentrierbohrungen selbstverständlich nicht erzeugt werden. Für die Bearbeitung ist vielmehr ein aufwändiger Fräsprozess oder ein aufwändiger exzentrischer Drehprozess mit entsprechend hohen Investitions- und/oder Fertigungskosten erforderlich. Die vorliegende Erfindung beseitigt diesen Nachteil durch die genannte Exzentrizität des Antriebszapfens zu den Zentrierbohrungen, so dass die spanende Bearbeitung des Lagersitzes durch den vergleichsweise einfachen und kostengünstigen Drehprozess der Unwuchtwelle zwischen Spitzen in den Zentrierbohrungen ermöglicht ist. Die Exzentrizität des Antriebszapfens zu den Zentrierbohrungen kann ebenfalls vergleichsweise einfach durch Drehen oder Fräsen des Antriebszapfens mittels eines Glockenwerkzeugs erfolgen. The solution to this problem results from the features of claim 1. Accordingly, the enveloping circle of the bearing pin should be concentric with the centering holes, with the drive pin being eccentric to the centering holes by the radius difference R - rz and concentric with the bearing ring. As explained below, this geometric design significantly simplifies the machining of the unbalanced shaft into the finished part. In current series production, the drive pin of the finished unbalanced shaft is concentric with its centering holes. Since the operational The axis of rotation of the balance shaft is concentric to the drive journal and the bearing ring and - in order to avoid deformations of the bearing ring due to component tolerances - the inner radius R of the bearing ring resting on the bearing journal is larger than the enveloping circle radius rz of the bearing journal, the radius difference R - rz must be reduced by eccentric machining of the bearing journal Centering holes are compensated. Of course, this eccentricity cannot be created by a simple turning process between centers in the centering holes. Rather, machining requires a complex milling process or a complex eccentric turning process with correspondingly high investment and/or manufacturing costs. The present invention eliminates this disadvantage through the aforementioned eccentricity of the drive pin to the centering holes, so that the machining of the bearing seat is made possible by the comparatively simple and inexpensive turning process of the unbalanced shaft between points in the centering holes. The eccentricity of the drive pin to the centering holes can also be done comparatively easily by turning or milling the drive pin using a bell tool.
Weitere Merkmale der Erfindung ergeben sich aus der nachfolgenden Beschreibung und aus der Zeichnung mit einem Ausführungsbeispiel einer erfindungsgemäßen Ausgleichswelle für den Massenausgleich zweiter Ordnung einer Reihenvierzylinder- Brennkraftmaschine. Die dort dargestellten Exzentrizitäten sind zwecks Veranschaulichung der Erfindung stark übertrieben dimensioniert. Es zeigen: Further features of the invention emerge from the following description and from the drawing with an exemplary embodiment of a balancing shaft according to the invention for second-order mass balancing of a four-cylinder in-line internal combustion engine. The eccentricities shown there are greatly exaggerated for the purpose of illustrating the invention. Show it:
Figur 1 die Ausgleichswelle in perspektivischer Darstellung; Figure 1 shows the balance shaft in a perspective view;
Figur 2 die Ausgleichswelle im Längsschnitt. Figure 2 shows the balance shaft in longitudinal section.
Die Ausgleichswelle umfasst eine aus einem Guss- oder Schmiederohling fertig bearbeitete Unwuchtwelle 1 mit einem endseitigen Antriebszapfen 2, zwei Lagerzapfen 3 und 4 sowie Unwuchtabschnitten 5, 6 und 7. Der Antriebszapfen 2 nimmt ein die Ausgleichswelle axial in der Brennkraftmaschine lagerndes Rillenkugellager (nicht dargestellt) und ein die Ausgleichswelle antreibendes Zahnrad (ebenfalls nicht dargestellt) auf. Die Lagerzapfen 3, 4 haben einen lediglich teilzylindrischen Umfang, wobei jeweils der zylindrische Teilumfang 8 in Richtung der Wellenunwucht u (s. Pfeil in Figur 2) orientiert ist, die durch die zur betrieblichen Drehachse 9 der Ausgleichswelle exzentrischen Massenschwer- punkte sowohl der Unwuchtabschnitte 5, 6, 7 als auch der Lagerzapfen 3, 4 erzeugt wird. The balance shaft comprises an unbalance shaft 1 finished from a cast or forged blank with an end drive pin 2, two bearing pins 3 and 4 and unbalance sections 5, 6 and 7. The drive pin 2 takes a deep groove ball bearing (not shown) which supports the balance shaft axially in the internal combustion engine. and a gear (also not shown) driving the balance shaft. The bearing journals 3, 4 only have a partially cylindrical circumference, with the cylindrical partial circumference 8 being oriented in the direction of the shaft unbalance u (see arrow in Figure 2), which is caused by the mass gravity which is eccentric to the operational axis of rotation 9 of the balancing shaft. points of both the unbalance sections 5, 6, 7 and the bearing journals 3, 4 are generated.
Die Radiallagerung der Unwuchtwelle 1 in der Brennkraftmaschine erfolgt mittels Nadellager 10, deren Innenlaufbahnen 11 jeweils durch einen den Lagerzapfen 3, 4 umschließenden Lagerring 12 gebildet sind. Jeder Lagerring 12 begrenzt zusammen mit einem dem zylindrischen Teilumfang 8 radial gegenüberliegenden Lagerzapfenrücken 13 einen Freiraum, in dem eine Blechfeder 14 gegen den Lagerzapfenrücken 13 einerseits und den Lagerring 12 andererseits gespannt ist und den Lagerring 12 radial gegen den zylindrischen Teilumfang 8 spannt. Auch die axiale Befestigung der Lagerringe 12 auf der Unwuchtwelle 1 erfolgt mittels der Blechfedern 14, die jeweils axial formschlüssig mit dem Lagerzapfenrücken 13 einerseits und dem Lagerring 12 andererseits verbunden sind. The unbalanced shaft 1 is radially supported in the internal combustion engine by means of needle bearings 10, the inner raceways 11 of which are each formed by a bearing ring 12 surrounding the bearing journal 3, 4. Each bearing ring 12, together with a bearing pin back 13 radially opposite the cylindrical partial circumference 8, delimits a free space in which a sheet metal spring 14 is tensioned against the bearing pin back 13 on the one hand and the bearing ring 12 on the other hand and tensions the bearing ring 12 radially against the cylindrical partial circumference 8. The bearing rings 12 are also axially fastened to the unbalanced shaft 1 by means of the sheet metal springs 14, which are each axially positively connected to the bearing pin back 13 on the one hand and to the bearing ring 12 on the other.
Die Lagerringe 12 liegen jeweils mit einem Innenradius R am zylindrischen Teilumfang 8 der Lagerzapfen 3, 4 an. Eine Verformung der exakt zylindrischen Innenlaufbahn 11 jedes Lagerrings 12 wird im Hinblick auf unvermeidliche Bauteiltoleranzen dadurch verhindert, dass der Innenradius R des Lagerrings 12 größer als der Hüllkreisradius rz des jeweiligen Lagerzapfens 3, 4 ist. The bearing rings 12 each rest with an inner radius R on the cylindrical partial circumference 8 of the bearing journals 3, 4. A deformation of the exactly cylindrical inner race 11 of each bearing ring 12 is prevented in view of unavoidable component tolerances in that the inner radius R of the bearing ring 12 is larger than the enveloping circle radius rz of the respective bearing journal 3, 4.
Figur 2 verdeutlicht die geometrischen Verhältnisse am bemaßten Lagerzapfen 4, an dem auch der auf dem zylindrischen Teilumfang 8 liegende Hüllkreis C um 90° verdreht eingezeichnet ist. Der Hüllkreis C ist mit einer Bearbeitungsachse 15 konzentrisch, die ihrerseits mit Zentrierbohrungen 16 und 17 konzentrisch ist, die in den Stirnseiten der Unwuchtwelle 1 eingearbeitet sind. Die spanende Bearbeitung jedes zylindrischen Teilumfangs 8 erfolgt durch einen einfachen Drehprozess, nämlich unter Aufnahme der Unwuchtwelle 1 auf Spitzen in den Zentrierbohrungen 16, 17, so dass der Ursprung des Hüllkreisradius rz auf der Bearbeitungsachse 15 liegt. Figure 2 illustrates the geometric relationships on the dimensioned bearing pin 4, on which the enveloping circle C lying on the cylindrical partial circumference 8 is shown rotated by 90 °. The enveloping circle C is concentric with a machining axis 15, which in turn is concentric with centering holes 16 and 17, which are machined into the end faces of the unbalance shaft 1. The machining of each cylindrical partial circumference 8 is carried out by a simple turning process, namely by holding the unbalanced shaft 1 on tips in the centering bores 16, 17, so that the origin of the enveloping circle radius rz lies on the machining axis 15.
Die betriebliche Drehachse 9 der Ausgleichswelle ist mit den Lagerringen 12 und dem Antriebszapfen 2 konzentrisch und zur Bearbeitungsachse 15 um die Radiendifferenz R - rz exzentrisch. Die spanende Fertigbearbeitung des Antriebszapfens 2 erfolgt mittels eines Glockenwerkzeugs, das entsprechend um die Radiendifferenz R - rz exzentrisch zu den Zentrierbohrungen 16, 17 verfährt. The operational axis of rotation 9 of the balance shaft is concentric with the bearing rings 12 and the drive pin 2 and eccentric to the machining axis 15 by the radius difference R - rz. The final machining of the drive pin 2 is carried out using a bell tool, which moves eccentrically to the centering bores 16, 17 by the radius difference R - rz.
Die in den Figuren dargestellten Exzentrizitäten sind zwecks Veranschaulichung der Er- findung im Millimeterbereich und folglich stark übertrieben dimensioniert. In der Realität beträgt die Radiendifferenz R - rz beispielsweise nur 35 Mikrometer. The eccentricities shown in the figures are for the purpose of illustrating the found in the millimeter range and therefore greatly exaggerated. In reality, for example, the radius difference R - rz is only 35 micrometers.

Claims

Patentansprüche Ausgleichswelle, umfassend: Claims balancing shaft, comprising:
- eine Unwuchtwelle (1) mit einem endseitigen Antriebszapfen (2), stirnseitigen Zentrierbohrungen (16, 17) und einem Lagerzapfen (3, 4), dessen Umfang lediglich teilzylindrisch ist, - an unbalanced shaft (1) with an end drive pin (2), front centering bores (16, 17) and a bearing pin (3, 4), the circumference of which is only partially cylindrical,
- und einen den Lagerzapfen (3, 4) umschließenden Lagerring (12), der mit einem Innenradius R am zylindrischen Teilumfang (8) des Lagerzapfens (3, 4) anliegt, wobei der Innenradius R des Lagerrings (12) größer als der Hüllkreisradius rz des Lagerzapfens (3, 4) ist, dadurch gekennzeichnet, dass der Hüllkreis (C) des Lagerzapfens (3, 4) mit den Zentrierbohrungen (16, 17) konzentrisch ist, wobei der Antriebszapfen (2) zu den Zentrierbohrungen (16, 17) um die Radiendifferenz R - rz exzentrisch und mit dem Lagerring (12) konzentrisch ist. Ausgleichswelle nach Anspruch 1 , dadurch gekennzeichnet, dass der Lagerring (12) zusammen mit einem dem zylindrischen Teilumfang (8) radial gegenüberliegenden Lagerzapfenrücken (13) einen Freiraum begrenzt, wobei die Ausgleichswelle eine Blechfeder (14) umfasst, die im Freiraum gegen den Lagerzapfenrücken (13) einerseits und den Lagerring (12) andererseits gespannt ist und den Lagerring (12) radial gegen den zylindrischen Teilumfang (8) spannt. Verfahren zur Herstellung einer Ausgleichswelle gemäß einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass der Antriebszapfen (2) mittels eines Glockenwerkzeugs spanend bearbeitet wird. - and a bearing ring (12) surrounding the bearing pin (3, 4), which rests with an inner radius R on the cylindrical partial circumference (8) of the bearing pin (3, 4), the inner radius R of the bearing ring (12) being larger than the enveloping circle radius rz of the bearing pin (3, 4), characterized in that the envelope circle (C) of the bearing pin (3, 4) is concentric with the centering bores (16, 17), the drive pin (2) facing the centering bores (16, 17) is eccentric by the radius difference R - rz and concentric with the bearing ring (12). Balancing shaft according to claim 1, characterized in that the bearing ring (12) together with a bearing pin back (13) radially opposite the cylindrical partial circumference (8) delimits a free space, the balancing shaft comprising a sheet metal spring (14) which in the free space against the bearing pin back ( 13) on the one hand and the bearing ring (12) on the other hand and tensions the bearing ring (12) radially against the cylindrical partial circumference (8). Method for producing a balance shaft according to one of the preceding claims, characterized in that the drive pin (2) is machined using a bell tool.
PCT/DE2023/100550 2022-07-27 2023-07-26 Balancing shaft and method for producing same WO2024022559A1 (en)

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DE102022118782.9A DE102022118782A1 (en) 2022-07-27 2022-07-27 Balance shaft and process for its manufacture
DE102022118782.9 2022-07-27

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Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19807180A1 (en) 1998-02-20 1999-08-26 Bayerische Motoren Werke Ag Mechanical mass balance for reciprocating piston engine
US20140311280A1 (en) * 2010-08-13 2014-10-23 Schaeffler Technologies AG & Co. KG Unbalanced shaft and method for producing same
DE102019101320A1 (en) 2018-08-30 2020-03-05 Schaeffler Technologies AG & Co. KG Balance shaft

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19807180A1 (en) 1998-02-20 1999-08-26 Bayerische Motoren Werke Ag Mechanical mass balance for reciprocating piston engine
US20140311280A1 (en) * 2010-08-13 2014-10-23 Schaeffler Technologies AG & Co. KG Unbalanced shaft and method for producing same
DE102019101320A1 (en) 2018-08-30 2020-03-05 Schaeffler Technologies AG & Co. KG Balance shaft

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