WO1996033354A1 - Pinch roll freewheel - Google Patents

Pinch roll freewheel Download PDF

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Publication number
WO1996033354A1
WO1996033354A1 PCT/EP1996/000821 EP9600821W WO9633354A1 WO 1996033354 A1 WO1996033354 A1 WO 1996033354A1 EP 9600821 W EP9600821 W EP 9600821W WO 9633354 A1 WO9633354 A1 WO 9633354A1
Authority
WO
WIPO (PCT)
Prior art keywords
ring
clamping
rings
roller freewheel
pinch roller
Prior art date
Application number
PCT/EP1996/000821
Other languages
German (de)
French (fr)
Inventor
Joachim Ritter
Johann Stark
Original Assignee
Ina Wälzlager Schaeffler 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 Ina Wälzlager Schaeffler Kg filed Critical Ina Wälzlager Schaeffler Kg
Priority to DE19680243D priority Critical patent/DE19680243D2/en
Priority to DE19680243A priority patent/DE19680243C1/en
Publication of WO1996033354A1 publication Critical patent/WO1996033354A1/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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D41/00—Freewheels or freewheel clutches
    • F16D41/06—Freewheels or freewheel clutches with intermediate wedging coupling members between an inner and an outer surface
    • F16D41/064—Freewheels or freewheel clutches with intermediate wedging coupling members between an inner and an outer surface the intermediate members wedging by rolling and having a circular cross-section, e.g. balls
    • F16D41/066—Freewheels or freewheel clutches with intermediate wedging coupling members between an inner and an outer surface the intermediate members wedging by rolling and having a circular cross-section, e.g. balls all members having the same size and only one of the two surfaces being cylindrical
    • F16D41/067—Freewheels or freewheel clutches with intermediate wedging coupling members between an inner and an outer surface the intermediate members wedging by rolling and having a circular cross-section, e.g. balls all members having the same size and only one of the two surfaces being cylindrical and the members being distributed by a separate cage encircling the axis of rotation

Definitions

  • the present invention relates to a clamping roller freewheel, with two mutually arranged, mutually facing jacket surfaces, with a cylindrical clamping track formed on one jacket surface, with clamping ramps formed on the other jacket surface and arranged in a circumferential direction, and with against the cylindrical clamping track and the clamping ramps sprung clamping rollers.
  • Such a freewheel is known for example from DE-PS 40 1 5 790.
  • the rings of such freewheels are produced by cutting or non-cutting shaping.
  • the rings are hardened so that the freewheel works safely even under heavy loads and without any significant wear.
  • the heavy machined rings are often hardened.
  • the thin-walled rings produced by non-cutting shaping are only hardened on the outer layer, because in this way the necessary elasticity of the thin-walled rings is retained.
  • the rings produced by machining are expensive and heavy; the rings produced without cutting are, on the other hand, cheaper and lighter, but because of the inherent elasticity of the rings, which are only hardened by the outer layer, they can only be subjected to less stress than the rings hardened by machining.
  • the invention is therefore based on the object of developing a generic clamping roller freewheel in such a way that it is both inexpensive and of low weight and also has low intrinsic elasticity. According to the invention this object is achieved in that at least one of the
  • Rings produced in a forming process without cutting and formed from a hardened steel are produced in a forming process without cutting and formed from a hardened steel.
  • the ring provided with the clamping ramps in particular the outer ring, is manufactured and hardened using the deep-drawing process, the ramps being integrally connected to the ring.
  • the outer ring according to the invention does not require any external support in the region of the clamping ramps, since its elongations in the circumferential direction under load are small to the desired extent due to its inherent rigidity.
  • the outer ring is fully hardened and the inner ring is surface hardened, both rings being produced without cutting in the deep-drawing process.
  • Such an arrangement is useful, for example, when the inner ring is, for example, attached to a shaft and is thus supported radially.
  • the inner ring is rotatably mounted on a drive shaft of a washing machine, a sun gear of the drive shaft meshing with planet gears, which in turn mesh with a ring gear which is flanged to the radial flange.
  • Rolling raceway is formed, can be omitted.
  • this arrangement of the rolling element raceway is particularly interesting for the deep-drawing process because the clear diameter of the inner one
  • a plain bearing ring is provided on the inside of the inner ring, the use of which enables a simple cylindrical inner contour of the inner ring.
  • an annular gap formed between the radial flange and the inner ring is closed by means of a sealing ring, the sealing ring bearing against the end face of the inner ring.
  • This arrangement is particularly favorable when the inner ring is arranged on the drive shaft and balls used as rolling elements are inserted between the inner ring and the drive shaft.
  • the inner ring is displaced radially with respect to the drive shaft; The balls can now be inserted into the sickle-shaped gap.
  • This radial displacement of the inner ring is made possible by the fact that the inner ring is radially displaceable relative to the sealing ring, even if the latter is rigid. With a radial shaft sealing ring, for example, this radial displaceability and thus the assembly described is not possible.
  • FIG. 1 shows a half section of a drive train of a washing machine with a clamping roller freewheel according to the invention
  • FIG. 3 shows another pinch roller freewheel according to the invention
  • the pinch roller freewheel 1 is arranged on a drive shaft 2 of a washing machine, not shown.
  • the clamping roller freewheel 1 has an outer ring 3, an inner ring 4 and clamping rollers 5 arranged therebetween, which are pressed into a gap which is formed by a cylindrical clamping track 6 of the inner ring 4 and by clamping ramps 7 of the outer ring 3. Furthermore, balls 8 are arranged between the rings 3, 4, which roll on ball grooves 9, 10 of the two rings 3, 4.
  • the pinch roller freewheel 1 is attached with its outer ring 3 to a housing 1 1. Between the pinch roller freewheel 1 and the drive shaft 2, a double-row deep groove ball bearing 12 is provided, which is formed from two races 13, 14 and rows of balls 15 arranged between them.
  • the inner ring 4 of the pinch roller freewheel 1 has on its left side a radial flange 16 which is fastened to a ring gear 17 of a planetary gear 18.
  • the ring gear 17 is fastened to a hollow shaft 19 which is arranged concentrically with the drive shaft 2 and which is rotatably mounted with respect to the housing 11 with the interposition of a deep groove ball bearing 20.
  • the drive shaft 2 has a sun gear 21 of the planetary gear 18, the sun gear 21 meshing with planet gears 22, which in turn are in engagement with the ring gear 17.
  • FIG. 2 clearly shows the design of the clamping ramps 7 on the outer ring 3. Furthermore, it can be seen that the clamping rollers 5 are pressed into a gap by means of spring elements 23, which is formed by the cylindrical clamping track 6 and the clamping ramps 7 .
  • the pinch rollers 5 and the spring element 23 are arranged in pockets 24 of a pinch roller cage 25.
  • Figure 3 shows an enlarged view of the cut and modified
  • Pinch roller freewheel 1 from Figure 1, but in a modified design.
  • the arrangement of the balls 8 and the pinch rollers 5 is only exchanged axially.
  • the inner ring 4 additionally has at its end facing the radial flange 16 on the inner circumferential surface a ball groove 26 for balls 27 rolling thereon.
  • An opposing track 28 for the balls 27 is formed on a sleeve 30 provided with a radial rim 29, the balls 27 rolling on the outer surface of the sleeve 30 and the radial rim 29.
  • This arrangement has the advantage that, for example, the inner ring 4 can be moved axially in the direction of the balls 27 until the balls 27 abut the ball groove 26. This arrangement is also particularly advantageous for the deep-drawing process for manufacturing reasons.
  • the clear diameter of the inner ring 4 is only larger in one axial direction and only smaller in the other direction. Because no undercuts can occur here, the inner ring 4 can be produced in a particularly favorable manner using the deep-drawing process.
  • the outer ring 3 is made of a hardenable steel in the deep-drawing process, the clamping ramps 7 getting their final shape in the deep-drawing process.
  • the ball groove 9 is produced in a rolling process. After the steel has hardened through, punctures for the arrangement of seals 31 are possibly formed in a cutting manner, the ball groove 9 possibly being reground. Due to its high inherent stiffness, expansions of the loaded outer ring 3 are so small that no additional components are required to stiffen it.
  • a sealing ring 32 can also be provided, which closes an annular gap 34 formed between the radial flange 16 and an end face 33 of the outer ring 3; the sealing ring 32 is rotatable with respect to the outer ring 3. Furthermore, a slide bearing ring 35 is arranged on the inside of the inner ring 4, via which the inner ring 4 is rotatably mounted with respect to the drive shaft, not shown.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Rolling Contact Bearings (AREA)
  • Friction Gearing (AREA)

Abstract

A pinch roll freewheel (1) has two rings (3, 4) one inside the other. There are pinch ramps (7) on the facing surfaces and a cylindrical pinch track (6) is formed, in which the pinch rolls (5) are spring-loaded against the cylindrical pinch track (6) and the pinch ramps (7). A lighter yet still inherently rigid pinch roll freewheel is to be formed in that at least one of the rings (3, 4) is made by a non-cutting shaping process and consists of fully hardened steel.

Description

Beschreibung description
KlemmrollenfreilaufPinch roller freewheel
Die vorliegende Erfindung betrifft einen Klemmrollenfreilauf, mit zwei inein- ander angeordneten, einander zugewandte Mantelflächen aufweisende Ringen, mit einer an der einen Mantelfläche ausgebildeten zylindrischen Klemmbahn, mit an der anderen Mantelfläche ausgebildeten, in Umfangsrichtung verteilt angeordneten Klemmrampen, und mit gegen die zylindrische Klemmbahn und die Klemmrampen angefederten Klemmrollen.The present invention relates to a clamping roller freewheel, with two mutually arranged, mutually facing jacket surfaces, with a cylindrical clamping track formed on one jacket surface, with clamping ramps formed on the other jacket surface and arranged in a circumferential direction, and with against the cylindrical clamping track and the clamping ramps sprung clamping rollers.
Ein derartiger Freilauf ist beispielsweise aus der DE-PS 40 1 5 790 bekannt. Die Ringe von derartigen Freiläufen sind durch spangebende oder spanlose Formge¬ bung hergestellt. Damit der Freilauf auch unter größeren Belastungen sicher und ohne nennenswerten Verschleiß funktioniert, werden die Ringe gehärtet. So werden die schweren spangebend hergestellten Ringe oftmals durchgehärtet. Die durch spanlose Formgebung hergestellten dünnwandigen Ringe werden ausschließlich randschichtgehärtet, weil auf diese Art und Weise die nötige Elastizität der dünnwandigen Ringe erhalten bleibt. Die spangebend hergestell¬ ten Ringe sind teuer und schwer; die spanlos hergestellten Ringe dagegen sind billiger und leichter, allerdings wegen der Eigenelastizität der lediglich rand- schichtgehärteten Ringe gegenüber den durchgehärteten spangebend hergestell¬ ten Ringen nur geringer belastbar.Such a freewheel is known for example from DE-PS 40 1 5 790. The rings of such freewheels are produced by cutting or non-cutting shaping. The rings are hardened so that the freewheel works safely even under heavy loads and without any significant wear. The heavy machined rings are often hardened. The thin-walled rings produced by non-cutting shaping are only hardened on the outer layer, because in this way the necessary elasticity of the thin-walled rings is retained. The rings produced by machining are expensive and heavy; the rings produced without cutting are, on the other hand, cheaper and lighter, but because of the inherent elasticity of the rings, which are only hardened by the outer layer, they can only be subjected to less stress than the rings hardened by machining.
Der Erfindung liegt daher die Aufgabe zugrunde, einen gattungsgemäßen Klemmrollenfreilauf derart weiterzubilden, daß dieser sowohl preiswert und von geringem Gewicht, als auch mit geringer Eigenelastizität ausgestattet ist. Erfindungsgemäß wird diese Aufgabe dadurch gelöst, daß wenigstens einer derThe invention is therefore based on the object of developing a generic clamping roller freewheel in such a way that it is both inexpensive and of low weight and also has low intrinsic elasticity. According to the invention this object is achieved in that at least one of the
Ringe in einem Umformverfahren spanlos hergestellt und aus einem durch¬ gehärteten Stahl gebildet ist.Rings produced in a forming process without cutting and formed from a hardened steel.
Gemäß Anspruch 2 ist der mit den Klemmrampen versehene Ring, insbesondere der äußere Ring im Tiefziehverfahren hergestellt und durchgehärtet ist, wobei die Rampen einstückig mit dem Ring verbunden sind. Im Gegensatz zu den le¬ diglich randschichtgehärteten, spanlos hergestellten äußeren Ringen benötigt der erfindungsgemäße Außenring keine äußere Abstützung im Bereich der Klemm- rampen, da seine Dehnungen in Umfangsrichtung unter Belastung aufgrund seiner Eigensteifigkeit im gewünschten Maß gering ist.According to claim 2, the ring provided with the clamping ramps, in particular the outer ring, is manufactured and hardened using the deep-drawing process, the ramps being integrally connected to the ring. In contrast to the outer rings which are only hardened by the outer layer and are produced without cutting, the outer ring according to the invention does not require any external support in the region of the clamping ramps, since its elongations in the circumferential direction under load are small to the desired extent due to its inherent rigidity.
Gemäß Anspruch 3 ist es zweckmäßig, daß der äußere Ring durchgehärtet und der innere Ring randschichtgehärtet ist, wobei beide Ringe im Tiefziehverfahren spanlos hergestellt sind. Eine derartige Anordnung ist beispielsweise dann zweckmäßig, wenn der innere Ring beispielsweise auf eine Welle aufgesteckt und somit radial abgestützt ist.According to claim 3, it is expedient that the outer ring is fully hardened and the inner ring is surface hardened, both rings being produced without cutting in the deep-drawing process. Such an arrangement is useful, for example, when the inner ring is, for example, attached to a shaft and is thus supported radially.
Bei dem bekannten Klemmrollenfreilauf sind an den einander zugewandten Mantelflächen der Ringe Wälzkörperlaufbahnen ausgebildet, an denen Wälzkör¬ per abwälzen. Bei einem derartigen Klemmrollenfreilauf ist es gemäß Anspruch 4 zweckmäßig, daß wenigstens einer der beiden in einem Umformverfahren, insbesondere Tiefziehverfahren hergestellten innere Ringe mit einem Radial¬ flansch versehen ist. In diesem Fall kann ein Gehäuse oder ein anderes dreh- bares Bauteil an dem Radialflansch befestigt werden.In the known clamping roller freewheel, rolling element raceways are formed on the mutually facing lateral surfaces of the rings, on which rolling elements roll. With such a clamping roller freewheel, it is expedient that at least one of the two inner rings produced in a forming process, in particular a deep-drawing process, is provided with a radial flange. In this case, a housing or another rotatable component can be attached to the radial flange.
Gemäß Anspruch 5 ist es zweckmäßig, daß der innere Ring auf einer Antriebs¬ welle einer Waschmaschine drehbar gelagert ist, wobei ein Sonnenrad der Antriebswelle mit Planetenrädern kämmt, die ihrerseits mit einem Hohlrad kämmen, das an den Radialflansch angeflanscht ist.According to claim 5, it is expedient that the inner ring is rotatably mounted on a drive shaft of a washing machine, a sun gear of the drive shaft meshing with planet gears, which in turn mesh with a ring gear which is flanged to the radial flange.
Gemäß Anspruch 6 ist es zweckmäßig, daß am Innenumfang des inneren Ringes an dessen dem Radialflansch zugewandten Ende eine Wälzkörperlaufbahn, insbesondere Kugelrille ausgebildet ist. Auf diese Weise ist eine Lagerung des inneren Ringes an dieser Stelle gegenüber der Antriebswelle auf preiswerte Art und Weise deshalb möglich, weil auf einen zusätzlichen Ring, an dem dieseAccording to claim 6, it is useful that on the inner circumference of the inner ring at its end facing the radial flange a rolling element raceway, ball groove in particular is formed. In this way, a storage of the inner ring at this point in relation to the drive shaft in an inexpensive manner is possible because of an additional ring on which this
Wälzkörperlaufbahn ausgebildet ist, verzichtet werden kann. Fertigungstech- nisch ist diese Anordnung der Wälzkörperlaufbahn für das Tiefziehverfahren deshalb besonders interessant, weil sich der lichte Durchmesser des innerenRolling raceway is formed, can be omitted. In terms of manufacturing technology, this arrangement of the rolling element raceway is particularly interesting for the deep-drawing process because the clear diameter of the inner one
Ringes stufenweise von innen nach außen vergrößert, ohne daß auf einen größeren lichten Durchmesser ein kleinerer lichter Durchmesser folgt. Auf dieseRing gradually enlarged from the inside to the outside without a smaller clear diameter being followed by a smaller clear diameter. To this
Weise ist gewährleistet, daß keine fertigungstechnisch schwer beherrschbare Hinterschneidungen auftreten.This ensures that there are no undercuts that are difficult to control in terms of production technology.
Gemäß Anspruch 7 ist es zweckmäßig, daß an der Innenseite des inneren Ringes ein Gleitlagerring vorgesehen ist, dessen Verwendung eine einfache zylindrische Innenkontur des inneren Ringes ermöglicht.According to claim 7, it is expedient that a plain bearing ring is provided on the inside of the inner ring, the use of which enables a simple cylindrical inner contour of the inner ring.
Gemäß Anspruch 8 ist es zweckmäßig, daß ein zwischen dem Radialflansch und dem inneren Ring gebildeter Ringspalt mittels eines Dichtringes verschlos¬ sen ist, wobei der Dichtring an der Stirnfläche des inneren Ringes anliegt. Diese Anordnung ist dann besonders günstig, wenn der innere Ring auf der Antriebs- welle angeordnet und als Wälzkörper verwendete Kugeln zwischen dem inne¬ ren Ring und die Antriebswelle eingeführt werden. Zu diesem Zweck wird der innere Ring gegenüber der Antriebswelle radial verschoben; in den sichelförmi¬ gen Spalt können nun die Kugeln eingeführt werden. Diese radiale Verschie¬ bung des inneren Ringes wird dadurch möglich, daß der innere Ring gegenüber dem Dichtring radial verschiebbar ist, auch wenn dieser starr ausgebildet ist. Beispielsweise mit einem Radialwellendichtring ist diese radiale Verschieb¬ barkeit und damit die beschriebene Montage nicht möglich.According to claim 8, it is expedient that an annular gap formed between the radial flange and the inner ring is closed by means of a sealing ring, the sealing ring bearing against the end face of the inner ring. This arrangement is particularly favorable when the inner ring is arranged on the drive shaft and balls used as rolling elements are inserted between the inner ring and the drive shaft. For this purpose, the inner ring is displaced radially with respect to the drive shaft; The balls can now be inserted into the sickle-shaped gap. This radial displacement of the inner ring is made possible by the fact that the inner ring is radially displaceable relative to the sealing ring, even if the latter is rigid. With a radial shaft sealing ring, for example, this radial displaceability and thus the assembly described is not possible.
Nachstehend wird die Erfindung anhand von zwei in insgesamt zwei Figuren dargestellten erfindungsgemäßen Ausführungsbeispielen näher erläutert. Es zeigen: Figur 1 einen Halbschnitt eines Antriebsstrangs einer Waschmaschine mit erfindungsgemäßem Klemmrollenfreilauf,The invention is explained in more detail below with reference to two exemplary embodiments according to the invention shown in a total of two figures. Show it: FIG. 1 shows a half section of a drive train of a washing machine with a clamping roller freewheel according to the invention,
Figur 2 einen Längsschnitt durch einen weiteren erfindungsgemäßen Klemmrollenfreilauf, und2 shows a longitudinal section through a further clamping roller freewheel according to the invention, and
Figur 3 einen weiteren erfindungsgemäßen KlemmrollenfreilaufFigure 3 shows another pinch roller freewheel according to the invention
Der erfindungsgemäße Klemmrollenfreilauf 1 ist auf einer Antriebswelle 2 einer nicht näher dargestellten Waschmaschine angeordnet. Der Klemmrollenfreilauf 1 weist einen äußeren Ring 3, einen inneren Ring 4 und dazwischen angeord¬ nete Klemmrollen 5 auf, die in einen Spalt hineingedrückt sind, der von einer zylindrischen Klemmbahn 6 des inneren Rings 4 und von Klemmrampen 7 des äußeren Rings 3 gebildet ist. Weiterhin sind zwischen den Ringen 3, 4 Kugeln 8 angeordnet, die an Kugelrillen 9, 10 der beiden Ringe 3, 4 abwälzen. Der Klemmrollenfreilauf 1 ist mit seinem äußeren Ring 3 an einem Gehäuse 1 1 befestigt. Zwischen dem Klemmrollenfreilauf 1 und der Antriebswelle 2 ist ein doppelreihiges Rillenkugellager 12 vorgesehen, das aus zwei Laufringen 1 3, 14 und dazwischen angeordneten Kugelreihen 1 5 gebildet ist. Der innere Ring 4 des Klemmrollenfreilaufs 1 weist an seiner linken Seite einen Radialflansch 16 auf, der an einem Hohlrad 1 7 eines Planetengetriebes 18 befestigt ist. Das Hohlrad 1 7 ist an einer zu der Antriebswelle 2 konzentrisch angeordneten Hohlwelle 19 befestigt, die unter Zwischenschaltung eines Rillenkugellagers 20 gegenüber dem Gehäuse 1 1 drehbar gelagert ist. Die Antriebswelle 2 weist ein Sonnenrad 21 des Planetengetriebes 18 auf, wobei das Sonnenrad 21 mit Planetenrädern 22 kämmt, die wiederum mit dem Hohlrad 1 7 in Eingriff stehen.The pinch roller freewheel 1 according to the invention is arranged on a drive shaft 2 of a washing machine, not shown. The clamping roller freewheel 1 has an outer ring 3, an inner ring 4 and clamping rollers 5 arranged therebetween, which are pressed into a gap which is formed by a cylindrical clamping track 6 of the inner ring 4 and by clamping ramps 7 of the outer ring 3. Furthermore, balls 8 are arranged between the rings 3, 4, which roll on ball grooves 9, 10 of the two rings 3, 4. The pinch roller freewheel 1 is attached with its outer ring 3 to a housing 1 1. Between the pinch roller freewheel 1 and the drive shaft 2, a double-row deep groove ball bearing 12 is provided, which is formed from two races 13, 14 and rows of balls 15 arranged between them. The inner ring 4 of the pinch roller freewheel 1 has on its left side a radial flange 16 which is fastened to a ring gear 17 of a planetary gear 18. The ring gear 17 is fastened to a hollow shaft 19 which is arranged concentrically with the drive shaft 2 and which is rotatably mounted with respect to the housing 11 with the interposition of a deep groove ball bearing 20. The drive shaft 2 has a sun gear 21 of the planetary gear 18, the sun gear 21 meshing with planet gears 22, which in turn are in engagement with the ring gear 17.
Der in Figur 2 dargestellte Querschnitt zeigt deutlich die Ausbildung der Klemmrampen 7 an dem äußeren Ring 3. Weiterhin ist erkennbar, daß die Klemmrollen 5 mittels Federelementen 23 in einen Spalt hineingedrückt wer¬ den, der von der zylindrischen Klemmbahn 6 und den Klemmrampen 7 gebildet ist. Die Klemmrollen 5 und die Federelement 23 sind in Taschen 24 eines Klemmrollenkäfigs 25 angeordnet. Figur 3 zeigt in vergrößerter Darstellung den geschnittenen und modifiziertenThe cross section shown in FIG. 2 clearly shows the design of the clamping ramps 7 on the outer ring 3. Furthermore, it can be seen that the clamping rollers 5 are pressed into a gap by means of spring elements 23, which is formed by the cylindrical clamping track 6 and the clamping ramps 7 . The pinch rollers 5 and the spring element 23 are arranged in pockets 24 of a pinch roller cage 25. Figure 3 shows an enlarged view of the cut and modified
Klemmrollenfreilauf 1 aus der Figur 1 , allerdings in modifizierter Bauweise. Die Anordnung der Kugeln 8 und der Klemmrollen 5 ist lediglich axial vertauscht. Der innere Ring 4 weist zusätzlich an seinem dem Radialflansch 16 zugewand- ten Ende an der inneren Mantelfläche eine Kugelrille 26 für daran abwälzende Kugeln 27 auf. Eine Gegenlaufbahn 28 für die Kugeln 27 ist an einer mit einem Radialbord 29 versehenen Hülse 30 ausgebildet, wobei die Kugeln 27 auf der Mantelfläche der Hülse 30 und des Radialbordes 29 abwälzen. Diese Anord¬ nung hat den Vorteil, daß beispielsweise der innere Ring 4 axial in Richtung auf die Kugeln 27 bewegt werden kann, bis die Kugeln 27 an der Kugelrille 26 anliegen. Auch aus fertigungstechnischen Gründen ist diese Anordnung ins¬ besondere für das Tiefziehverfahren vorteilhaft. Aus der Figur 3 ist ersichtlich, daß der lichte Durchmesser des inneren Ringes 4 in der einen axialen Richtung nur größer bzw. in der anderen Richtung nur kleiner wird. Weil hier keine Hinterschneidungen auftreten können, läßt sich der innere Ring 4 in besonders günstiger Weise im Tiefziehverfahren herstellen. Der äußere Ring 3 ist aus einem durchhärtbaren Stahl im Tiefziehverfahren hergestellt, wobei im Tiefzieh¬ vorgang die Klemmrampen 7 ihre endgültige Form bekommen. Die Kugelrille 9 wird in einem Rolliervorgang erzeugt. Nach dem Durchhärten des Stahls werden ggf. in spangebender Weise Einstiche für die Anordnung von Dichtun¬ gen 31 ausgebildet, wobei die Kugelrille 9 unter Umständen nachgeschliffen wird. Aufgrund seiner hohen Eigensteifigkeit sind Dehnungen des belasteten äußeren Rings 3 derart gering, daß keine weiteren zusätzlichen Bauteile zu seiner Versteifung nötig sind. Alternativ zu dem in Figur 3 links angeordneten Dichtring 31 kann auch ein Dichtring 32 vorgesehen sein, der einen zwischen dem Radialflansch 16 und einer Stirnfläche 33 des äußeren Ringes 3 gebildeten Ringspalt 34 verschließt; der Dichtring 32 ist in Bezug auf den äußeren Ring 3 drehbar. Weiterhin ist an der Innenseite des inneren Ringes 4 ein Gleitlagerring 35 angeordnet, über den der innere Ring 4 gegenüber der nicht dargestellten Antriebswelle drehbar gelagert ist. BezugszahlenlistePinch roller freewheel 1 from Figure 1, but in a modified design. The arrangement of the balls 8 and the pinch rollers 5 is only exchanged axially. The inner ring 4 additionally has at its end facing the radial flange 16 on the inner circumferential surface a ball groove 26 for balls 27 rolling thereon. An opposing track 28 for the balls 27 is formed on a sleeve 30 provided with a radial rim 29, the balls 27 rolling on the outer surface of the sleeve 30 and the radial rim 29. This arrangement has the advantage that, for example, the inner ring 4 can be moved axially in the direction of the balls 27 until the balls 27 abut the ball groove 26. This arrangement is also particularly advantageous for the deep-drawing process for manufacturing reasons. From Figure 3 it can be seen that the clear diameter of the inner ring 4 is only larger in one axial direction and only smaller in the other direction. Because no undercuts can occur here, the inner ring 4 can be produced in a particularly favorable manner using the deep-drawing process. The outer ring 3 is made of a hardenable steel in the deep-drawing process, the clamping ramps 7 getting their final shape in the deep-drawing process. The ball groove 9 is produced in a rolling process. After the steel has hardened through, punctures for the arrangement of seals 31 are possibly formed in a cutting manner, the ball groove 9 possibly being reground. Due to its high inherent stiffness, expansions of the loaded outer ring 3 are so small that no additional components are required to stiffen it. As an alternative to the sealing ring 31 arranged on the left in FIG. 3, a sealing ring 32 can also be provided, which closes an annular gap 34 formed between the radial flange 16 and an end face 33 of the outer ring 3; the sealing ring 32 is rotatable with respect to the outer ring 3. Furthermore, a slide bearing ring 35 is arranged on the inside of the inner ring 4, via which the inner ring 4 is rotatably mounted with respect to the drive shaft, not shown. List of reference numbers
1 Klemmrollenfreilauf 19 Hohlwelle1 pinch roller freewheel 19 hollow shaft
2 Antriebswelle 20 Rillenkugellager2 drive shaft 20 deep groove ball bearings
3 äußerer Ring 21 Sonnen rad3 outer ring 21 sun wheel
4 innerer Ring 22 Planetenrad4 inner ring 22 planet gear
5 Klemmrolle 23 Federelement 6 Klemmbahn 24 Tasche5 Pinch roller 23 Spring element 6 Clamp track 24 Pocket
7 Klemmrampe 25 Klemmrollenkäfig7 clamping ramp 25 clamping roller cage
8 Kugel 26 Kugelrille8 ball 26 ball groove
9 Kugelrille 27 Kugel9 ball groove 27 ball
10 Kugelrille 28 Gegenlaufbahn 1 1 Gehäuse 29 Radialbord10 ball groove 28 mating track 1 1 housing 29 radial rim
1 2 doppelreihiges Rillenkugellager 30 Hülse1 2 double row deep groove ball bearing 30 sleeve
13 Laufring 31 Dichtring13 race 31 sealing ring
14 Laufring 32 Dichtring14 race 32 sealing ring
1 5 Kugelreihe 33 Stirnfläche 16 Radialflansch 34 Ringspalt1 5 row of balls 33 end face 16 radial flange 34 annular gap
1 7 Hohlrad 35 Gleitlagerring1 7 ring gear 35 plain bearing ring
18 Planetengetriebe 18 planetary gears

Claims

Ansprüche Expectations
1. Klemmrollenfreilauf (1 ), mit zwei ineinander angeordneten, einander zuge¬ wandte Mantelflächen aufweisende Ringen (3, 4), mit einer an der einen Man¬ telfläche ausgebildeten zylindrischen Klemmbahn (6), mit an der anderen Mantelfläche ausgebildeten, in Umfangsrichtung verteilt angeordneten Klemm- rampen (7), und mit gegen die zylindrische Klemmbahn (6) und die Klemm¬ rampen (7) angefederten Klemmrollen (5), dadurch gekennzeichnet, daß wenig¬ stens einer der Ringe (3, 4) in einem Umformverfahren spanlos hergestellt und aus einem durchgehärteten Stahl gebildet ist.1. Clamping roller freewheel (1), with two rings (3, 4) arranged one inside the other and facing each other, with a cylindrical clamping track (6) formed on one surface, with circumferentially formed on the other surface arranged clamping ramps (7), and with clamping rollers (5) spring-loaded against the cylindrical clamping track (6) and the clamping ramps (7), characterized in that at least one of the rings (3, 4) is non-cutting in a forming process is made and made of hardened steel.
2. Klemmrollenfreilauf (1 ) nach Anspruch 1 , dadurch gekennzeichnet, daß der mit den Klemmrampen (7) versehene Ring, insbesonder der äußere Ring (3) im Tiefziehverfahren hergestellt und durchgehärtet ist, wobei die Rampen (7) einstückig mit dem Ring (3) verbunden sind.2. Clamping roller freewheel (1) according to claim 1, characterized in that the ring provided with the clamping ramps (7), in particular the outer ring (3), is produced and hardened in the deep-drawing process, the ramps (7) being integral with the ring (3 ) are connected.
3. Klemmrollenfreilauf (1 ) nach Anspruch 1 , dadurch gekennzeichnet, daß der äußere Ring (3) durchgehärtet und der innere Ring (4) randschichtgehärtet ist. wobei beide Ringe (3, 4) im Tiefziehverfahren spanlos hergestellt sind.3. pinch roller freewheel (1) according to claim 1, characterized in that the outer ring (3) is fully hardened and the inner ring (4) is surface hardened. wherein both rings (3, 4) are made without cutting in the deep-drawing process.
4. Klemmrollenfreilauf (1 ) nach Anspruch 1 , bei dem an einander zugewandten Mantelflächen der Ringe (3, 4) Wälzkörperlaufbahnen (9, 10) ausgebildet sind, an denen Wälzkörper (8) abwälzen, dadurch gekennzeichnet, daß wenigstens einer der beiden in einem Umformverfahren, insbesondere Tiefziehverfahren, hergestellten Ringe (4) mit einem Radialflansch (16) versehen ist.4. clamping roller freewheel (1) according to claim 1, in which on mutually facing lateral surfaces of the rings (3, 4) rolling element raceways (9, 10) are formed, on which rolling elements (8) roll, characterized in that at least one of the two in one Forming process, in particular deep-drawing process, rings (4) produced is provided with a radial flange (16).
5. Klemmrollenfreilauf (1 ) nach Anspruch 4, dadurch gekennzeichnet, daß der innere Ring (4) auf einer Antriebswelle (2) einer Waschmaschine drehbar gelagert ist, wobei ein Sonnenrad (21 ) der Antriebswelle (2) mit Planetenrädern (22) kämmt, die ihrerseits mit einem Hohlrad (1 7) kämmen, das an den Radial¬ flansch (16) angeflanscht ist.5. pinch roller freewheel (1) according to claim 4, characterized in that the inner ring (4) on a drive shaft (2) of a washing machine is rotatably mounted, wherein a sun gear (21) of the drive shaft (2) with planet wheels (22) combs, which in turn mesh with a ring gear (17) which is flanged to the radial flange (16).
6. Klemmrollenfreilauf (1 ) nach Anspruch 5, dadurch gekennzeichnet, daß am Innenumfang des inneren Ringes (4) an dessen dem Radialflansch (16) zuge¬ wandten Ende eine Wälzkörperlaufbahn, insbesondere Kugelrille (26) ausgebil¬ det ist.6. pinch roller freewheel (1) according to claim 5, characterized in that on the inner circumference of the inner ring (4) at its end facing the radial flange (16) a rolling element raceway, in particular ball groove (26) is ausgebil¬ det.
7. Klemmrollenfreilauf nach Anspruch 5, dadurch gekennzeichnet, daß an der Innenseite des inneren Ringes (4) ein Gleitlagerring (35) vorgesehen ist.7. pinch roller freewheel according to claim 5, characterized in that on the inside of the inner ring (4) a sliding bearing ring (35) is provided.
8. Klemmrollenfreilauf nach Anspruch 5, dadurch gekennzeichnet, daß ein zwischen dem Radialflansch (16) und dem äußeren Ring (3) gebildeter Ringspalt (34) mittels eines Dichtringes (32) verschlossen ist, wobei der Dichtring (32) an der Stirnfläche (33) des äußeren Ringes (3) anliegt. 8. Pinch roller freewheel according to claim 5, characterized in that an annular gap (34) formed between the radial flange (16) and the outer ring (3) is closed by means of a sealing ring (32), the sealing ring (32) on the end face (33 ) of the outer ring (3).
PCT/EP1996/000821 1995-04-19 1996-02-29 Pinch roll freewheel WO1996033354A1 (en)

Priority Applications (2)

Application Number Priority Date Filing Date Title
DE19680243D DE19680243D2 (en) 1995-04-19 1996-02-29 Pinch roller freewheel
DE19680243A DE19680243C1 (en) 1995-04-19 1996-02-29 Clamping roller freewheel

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19514506.2 1995-04-19
DE19514506A DE19514506A1 (en) 1995-04-19 1995-04-19 Pinch roller freewheel

Publications (1)

Publication Number Publication Date
WO1996033354A1 true WO1996033354A1 (en) 1996-10-24

Family

ID=7759926

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP1996/000821 WO1996033354A1 (en) 1995-04-19 1996-02-29 Pinch roll freewheel

Country Status (4)

Country Link
KR (1) KR19980703723A (en)
CN (1) CN1182472A (en)
DE (2) DE19514506A1 (en)
WO (1) WO1996033354A1 (en)

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EP1275868A1 (en) * 2001-07-13 2003-01-15 Koyo Seiko Co., Ltd. One-way clutch unit
DE202015101730U1 (en) 2015-04-09 2015-04-22 Knorr-Bremse Systeme für Nutzfahrzeuge GmbH Clamping roller freewheel

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DE19644045C2 (en) * 1996-10-31 2002-04-18 Ina Schaeffler Kg freewheel
DE19812253A1 (en) * 1998-03-20 1999-10-07 Schaeffler Waelzlager Ohg Roller bearing combined with free-run coupling, particularly radially grooved ball bearing
DE19952120A1 (en) * 1999-10-29 2001-05-03 Schaeffler Waelzlager Ohg Combined axial/radial ball bearing for mounting spindles in machine tools has axial cage with seatings for balls and radial races containing second set of balls, axial cage having plate with seatings which have tapering edges
DE10159440A1 (en) * 2001-12-04 2003-06-12 Ina Schaeffler Kg Freewheel clutch, for a vehicle automatic drive transmission train, has outer and inner sections with clamping gaps between them mounted on an angular roller bearing on one side and a sliding bearing ring on the other side
DE20305473U1 (en) 2003-04-03 2003-06-12 Novopress GmbH Pressen und Presswerkzeuge & Co. KG, 41460 Neuss Hand-driven press has a driver and a motor with a linear guide and linear drive
JP5153269B2 (en) * 2007-09-05 2013-02-27 株式会社シマノ Roller clutch
DE102008021960A1 (en) * 2008-05-02 2009-11-05 Schaeffler Kg Free-wheel e.g. directional clutch, for use in machine construction, has free-wheel cage arranged between outer ring and inner ring, where outer ring is formed by self-supporting angle flange that is designed as cold-transformed component
DE102011082951A1 (en) * 2011-09-19 2013-03-21 Schaeffler Technologies AG & Co. KG Freewheel support bearing assembly for a machine element
DE102014200477A1 (en) 2014-01-14 2015-07-16 Schaeffler Technologies AG & Co. KG Fine stamped ring element for a freewheel
DE102016218929A1 (en) * 2016-09-29 2018-03-29 Schaeffler Technologies AG & Co. KG Sleeve freewheel with torque limiter for two-wheel starter applications
EP3627003A1 (en) 2018-09-20 2020-03-25 Rolls-Royce Deutschland Ltd & Co KG Epicyclic gear system and gas turbine engine

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Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1275868A1 (en) * 2001-07-13 2003-01-15 Koyo Seiko Co., Ltd. One-way clutch unit
US6705444B2 (en) 2001-07-13 2004-03-16 Koyo Seiko Co., Ltd. One-way clutch unit
KR100502738B1 (en) * 2001-07-13 2005-07-20 고요 세이코 가부시키가이샤 One-way clutch unit
DE202015101730U1 (en) 2015-04-09 2015-04-22 Knorr-Bremse Systeme für Nutzfahrzeuge GmbH Clamping roller freewheel
WO2016162411A1 (en) 2015-04-09 2016-10-13 Knorr-Bremse Systeme für Nutzfahrzeuge GmbH One-way roller clutch
US10941820B2 (en) 2015-04-09 2021-03-09 Knorr-Bremse Systeme Fuer Nutzfahrzeuge Gmbh One-way roller clutch

Also Published As

Publication number Publication date
CN1182472A (en) 1998-05-20
KR19980703723A (en) 1998-12-05
DE19680243C1 (en) 2002-04-11
DE19514506A1 (en) 1996-10-24

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