DE2558059B1

DE2558059B1 - CV joint coupling

Info

Publication number: DE2558059B1
Application number: DE19752558059
Authority: DE
Inventors: Schmid Leopold F
Original assignee: Individual
Current assignee: Individual
Priority date: 1975-12-22
Filing date: 1975-12-22
Publication date: 1977-01-13

Description

Die Erfindung wird anhand der Zeichnungen näher beschrieben, in denen mögliche Ausführungsformen erfindungsgemäßer Gleichlaufgelenkkupplungen dargestellt sind. Es zeigen F i g. 1 einen Längsschnitt durch eine als Verschiebegelenk ausgebildete Gleichlaufgelenkkupplung gemäß der Erfindung in Strecklage und mit einem ganz nach außen verschobenen inneren Kupplungsteil: Fig.2 einen Längsschnitt durch ein Verschiebegelenk nach F i g. 1, jedoch mit einem einer Winkelbewegung unterworfenen und ganz nach innen verschobenen inneren Kupplungsteil; F i g. 3 einen Längsschnitt durch eine als Festgelenk ausgebildete Gleichlaufgelenkkupplung gemäß der Erfindung in Strecklage; F i g. 4 einen Querschnitt durch ein Festgelenk nach F i g. 3; F i g. 5 einen Längsschnitt durch ein Festgelenk nach F i g. 1, jedoch mit einem einer Winkelbewegung unterworfenen inneren Kupplungsteil; F i g. 6 eine Draufsicht auf das innere Kupplungsteil; The invention is described in more detail with reference to the drawings, in which possible embodiments of constant velocity joint couplings according to the invention are shown are. It shows F i g. 1 shows a longitudinal section through one designed as a sliding joint Constant velocity joint coupling according to the invention in the extended position and with a completely after inner coupling part displaced on the outside: FIG. 2 a longitudinal section through a sliding joint according to FIG. 1, but with an angular movement and quite according to inwardly displaced inner coupling part; F i g. 3 a longitudinal section through a designed as a fixed joint constant velocity joint coupling according to the invention in the extended position; F i g. 4 shows a cross section through a fixed joint according to FIG. 3; F i g. 5 shows a longitudinal section by a fixed joint according to FIG. 1, but with an angular movement inner coupling part; F i g. 6 is a plan view of the inner coupling part;

F i g. 7 eine teils in Ansicht und teils im Schnitt dargestellte komplette Gelenkwelle mit zwei Gleichlaufgelenkkupplungen gemäß der Erfindung für den Antrieb der Vorderräder eines Kraftfahrzeuges; Fig. 8 einen Querschnitt A-A durch eine Gelenkwelle nach Fig. 7; F i g. 9 eine Draufsicht auf eine Gelenkwelle nach F i g. 7 im Maßstab 1 : 2. F i g. 7 shows a partly in view and partly in section complete cardan shaft with two constant velocity joint couplings according to the invention for driving the front wheels of a motor vehicle; Figure 8 shows a cross section A-A by a cardan shaft according to FIG. 7; F i g. 9 is a plan view of a cardan shaft according to FIG. 7 on a scale of 1: 2.

Das äußere Kupplungsteil 1 für das Verschiebegelenk und das äußere Kupplungsteil 2 für das Festgelenk sind mit drei in Umfangsrichtung gleichmäßig verteilten, geraden und achsparallelen Nuten versehen, in die zur Übertragung des Drehmomentes Rollen eingreifen. Die Rollen 7, die mit einer Kugelfläche 11 versehen sind, und die Rollen 8, die eine Kugelfläche 12 haben, sind drehbar und radial verschiebbar auf Zapfen 4 des inneren Kupplungsteiles 3 gelagert, das mit der Welle 6 aus einem Stück gefertigt ist. Die Zapfen 4 sind mit Bohrungen versehen, in denen sich radial verschiebbare Steuerbolzen 26 befinden, die an ihrem äußeren Ende 27 mit einer Planfläche und an ihrem inneren Ende 28 mit einer Kugelfläche 29 versehen sind. Der Krümmungsradius 20 dieser Kugelfläche 29 hat den gleichen Mittelpunkt 21 wie der Krümmungsradius 19 der Kugelflächen 11, 12 der Rollen 7, 8. Die für das Zustandekommen des Gleichlaufs während einer Winkelbewegung erforderliche radiale Verschiebung der Rollen 7, 8 wird mit Hilfe des Steuergliedes 13, 22 erreicht, in dessen Längsrillen 14 sich die Steuerbolzen 26 mit ihrer am inneren Ende 28 angebrachten Kugelfläche 29 abstützen. Da sich die Steuerbolzen 26 mit ihrem äußeren Ende 27 im Grund 10 der Bohrung 9 der Rollen 7, 8 abstützen, übertragen sie ihre ihnen vom Steuerglied 13, 22 aufgezwungene radiale Verschiebung direkt auf die Rollen 7, 8. Wie klein das Maß dieser radialen Verschiebung der Rollen beim Beugen des Gelenkes ist, geht aus der Zeichnung hervor, die eine maßstabsgetreue Darstellung einer Gleichlaufgelenkkupplung für ein maximales Betriebsdrehmoment von 6 500 cm kp ist. Aus der Zeichnung kann auch leicht entnommen werden, wieso es zu diesen minimalen radialen Verschiebewegen kommt, die nur bei etwa einem Drittel der Werte der heutigen Ausführungsformen liegen. Das Absenken der heutigen großen Werte auf die Minimalwerte der beschriebenen Gleichlaufgelenkkupplung resultiert aus der Verlagerung des Mittelpunktes 21 in Richtung auf die Gelenkmitte. The outer coupling part 1 for the sliding joint and the outer Coupling part 2 for the fixed joint are uniform with three in the circumferential direction distributed, straight and axially parallel grooves into which the Engage the torque rolling. The rollers 7, which are provided with a spherical surface 11 are, and the rollers 8, which have a spherical surface 12, are rotatable and radially displaceable mounted on pin 4 of the inner coupling part 3, which with the shaft 6 from a Piece is made. The pins 4 are provided with bores in which are radially displaceable control pin 26 are located at their outer end 27 with a flat surface and are provided with a spherical surface 29 at their inner end 28. The radius of curvature 20 of this spherical surface 29 has the same center point 21 as the radius of curvature 19 of the spherical surfaces 11, 12 of the rollers 7, 8. The ones for bringing about synchronism Radial displacement of the rollers 7, 8 required during an angular movement is achieved with the help of the control member 13, 22, in the longitudinal grooves 14 support the control bolts 26 with their spherical surface 29 attached to the inner end 28. Since the control pin 26 is located with its outer end 27 in the base 10 of the bore 9 the rollers 7, 8 support, they transmit their imposed by the control member 13, 22 radial displacement directly on the rollers 7, 8. How small the dimension of this radial Shifting of the roles when bending the joint is evident from the drawing, which is a true-to-scale representation of a constant velocity joint for a maximum Operating torque of 6 500 cm kp. From the drawing it can also be easily taken why it comes to this minimal radial displacement, which only with about a third of the values of the current embodiments. The lowering of today's great values to the minimum values of the constant velocity joint described results from the displacement of the center point 21 in the direction of the center of the joint.

Durch diese Verschiebung des Mittelpunktes 21 des Krümmungsradius 19 der Rollen 7 erhöht sich zwar die beim Übertragen eines Drehmomentes auf die Rollen einwirkende und nach innen gerichtete Radialkraft, aber diese Erhöhung der Radialkraft hat keine nachteiligen Folgen, weil die Planfläche 27 des Steuerbolzens 26, auf der sie sich abstützt, relativ klein und zentral angeordnet ist, sodaß sich kein die Drehbewegung der Rollen beeinträchtigendes Bremsmoment aufbauen kann. Auch an der Abstützung der Kugelfläche 29 des Steuerbolzens 26 in der Rille 14 des Steuergliedes 13, 22 entsteht infolge dieser erhöhten Radialkraft kein unzulässiger Verschleiß, weil die Relativbewegungen zwischen der Kugelfläche 29 und der Rille 14 sehr klein sind. Das Steuerglied 13, 22 wird ständig mit einer von einer Feder aufgebrachten Kraft 30 mit seiner konvexen Kugelfläche 15 an die konkave Kugelfläche 5 des inneren Kupplungsteiles 3 angedrückt. Diese Feder 17 ist als Schraubenfeder ausgebildet, deren Außendurchmesser in einer Bohrung 18 des äußeren Kupplungsteiles 1 zentriert ist, und deren Innendurchmesser als Zentrierung für den Zapfen 16 des Steuergliedes 13 dient. Der Zapfen 23 des Steuergliedes 22 ist im äußeren Kupplungsteil 2 direkt zentriert. Zur Erzielung einer besonders großen Winkelbeweglichkeit sind die Rollen 8 des Festgelenks mit einer den Beugungswinkel 33 vergrößernden Ausnehmung 24 versehen. In diesem Falle müssen die Rollen 8 mit einem Zapfen 25 versehen sein, der zur Begrenzung ihres Verdrehwinkels 31 gegen das innere Kupplungsteil 3 schlägt. Für den kleineren Beugungswinkel 32 des Verschiebegelenkes benötigen die Rollen 7 weder eine Ausnehmung noch einen Anschlag.By shifting the center point 21 of the radius of curvature 19 of the rollers 7 increases when a torque is transmitted to the Rolling acting and inward radial force, but this increase in Radial force has no disadvantageous consequences because the plane surface 27 of the control pin 26, on which it is supported, is relatively small and centrally located, so that cannot build up a braking torque that would impair the rotation of the rollers. Even on the support of the spherical surface 29 of the control pin 26 in the groove 14 of the control member 13, 22 there is no impermissible wear as a result of this increased radial force, because the relative movements between the spherical surface 29 and the groove 14 are very small are. The control member 13, 22 is always applied with a spring Force 30 with its convex spherical surface 15 to the concave spherical surface 5 of the inner Coupling part 3 pressed on. This spring 17 is designed as a helical spring, the outer diameter of which is centered in a bore 18 of the outer coupling part 1 is, and its inner diameter as a centering for the pin 16 of the control member 13 serves. The pin 23 of the control member 22 is in the outer coupling part 2 directly centered. To achieve a particularly large angular mobility, the rollers 8 of the fixed joint is provided with a recess 24 which enlarges the angle of flexion 33. In this case, the rollers 8 must be provided with a pin 25 to limit their angle of rotation 31 strikes against the inner coupling part 3. For the smaller one Flexion angle 32 of the sliding joint, the rollers 7 neither need a recess another stop.

Für den Fall einer Gelenkwelle mit zwei Gleichlaufgelenkkupplungen der beschriebenen Art gemäß den F i g. 7 bis 9 muß die mit den beiden inneren Kupplungsteilen aus einem Stück gefertigte Welle 6 zur Abdichtung mittels der Dichtungsmanschette 35 mit Bunden 34 versehen sein, die aus Kunststoff bestehen können. In the case of a cardan shaft with two constant velocity joint couplings of the type described according to FIGS. 7 to 9 must be the one with the two inner coupling parts Shaft 6 made from one piece for sealing by means of the sealing sleeve 35 be provided with collars 34, which can be made of plastic.

Claims

Claim: CV joint coupling in which the transmission of the torque over three evenly distributed in the circumferential direction and with one Rolls provided with spherical surfaces are carried out, which run in straight lines and axially parallel Engage grooves of the outer coupling part and the three from the inner coupling part growing out bearing journals are rotatably and radially displaceably mounted. whereby the relative radial displacement of the rollers required for an angular movement to their journals with the help of a centrally located control member and three radially displaceably mounted control pin comes about, which the latter at their inner. the centrally arranged control member facing the end with a spherical surface are provided whose radius of curvature is smaller than the radius of curvature of the spherical surface of roles, characterized. that the spherical surface (29) of the control pin (26) has the same center point (21) as the spherical surface (11, 12) of the rollers (7, 8).

The invention relates to a constant velocity joint coupling in which the Transmission of the torque over three evenly distributed in the circumferential direction and rollers provided with a spherical surface, which are straight and axially parallel extending grooves of the outer coupling part engage and the three from the inner coupling part outgrowing bearing journals rotatable and radially displaceable are stored.

where the radial displacement required for angular movement of the rollers relative to their journals with the help of a centrally arranged control member and three radially displaceably mounted control bolts come about, the latter on your inside. the centrally arranged control member facing end with a Spherical surface are provided.

whose radius of curvature is smaller than the radius of curvature of the spherical surface of the roles.

Constant velocity joint couplings of the aforementioned type have the disadvantage that with angular movements, i.e. when bending the joint. the three the torque transferring roles are shifted radially, so that they twice during assume two extreme positions with each rotation of the joint. In one of these extreme situations the role approaches the center of the inner coupling part by a certain amount. while in the other extreme position it is three times this measure of this Center has moved away. These dimensions change approximately like the squares the diffraction angle. With one dimensioned for a maximum operating torque of 150 mkp The constant velocity joint coupling of today's design results from just one flexion angle of 20 is a measure of this radially outward movement of the roller, which at about 3 mm. Since such constant velocity joint couplings are mainly used for cardan shafts be used to drive the wheels of motor vehicles, and there with a front-wheel drive the diffraction angle increases to 45 °, extreme values can occur in the current embodiments up to about 15 mm can be achieved. When you consider that while transferring of the maximum operating torque of 150 mkp that radial displacement of the rollers on the pin of the inner coupling part only by means of a force of more than 100 kp is possible, then it becomes clear how big this is with today's state of the art inherent disadvantage is.

Constant velocity joint couplings of the type described above have besides this disadvantage but also the disadvantage that when bending of the joint, the center of the inner coupling part relative to the center of the outer one Coupling part shifted eccentrically. As a result of this resulting oscillating movement the smoothness, which is already impaired by the radial displacement of the rollers is further deteriorated.

The invention is based on the object of a constant velocity joint coupling to create the type described above, in which both the dimension of the radial Displacement of the rollers relative to the inner coupling part as well as the degree of the eccentric Displacement of the center of the inner coupling part relative to the center of the outer one Coupling part is more than half smaller than that when the joint is bent of today's embodiments.

The object is achieved according to the invention in that the spherical surface the control pin, the radius of curvature of which is smaller than the radius of curvature of the Spherical surface of the rollers. has the same center point as the spherical surface of the Roll.

The advantages achieved with the invention are varied and greater than what as a result of a technically flawless solution of the invention underlying task may be expected because of the strong degradation the amount of radial displacement of the rollers and the amount of eccentric displacement the middle of the inner coupling part when bending the joint not only ensures smoothness improved and the wear and tear is reduced, but also an improvement in the the kinematics of the joint causing the synchronism to be achieved at large flexion angles will.

Since the funds used for the solution are simple and easy to produce and also have a particularly small footprint, has a Constant velocity joint coupling according to the invention compared to the current embodiments nor the advantages of lower manufacturing costs and smaller external dimensions and the lower weight.