DE4410377A1 - Double-cam joint with internal length adaptation for 90 DEG homokinetic joints with radius gears - Google Patents

Abstract

A homokinetic joint with a bend angle of up to 90 DEG is held in interengagement by a sprung inner joint so as resiliently to compensate the change in the centre of rotation of the inner joint during bending. The inner joint must here have the ability to bend in two planes. Due to the sprung inner joint, the homokinetic joint attempts to assume its extended position since, in all positions, it is acted upon by the spring load. In order to hold together a homokinetic joint with a bend angle of up to 90 DEG by means of an inner joint without the homokinetic joint having a tendency to assume its extended position, a double-cam joint is used. By virtue of spiders mounted in guides, this double-cam joint can compensate the required change in the centre of rotation. <IMAGE>

Description

The invention relates to a double cam joint according to the Preamble of claim 1.

A 90 ° constant velocity joint with radius gears is replaced by a Internal joint held together. The inner joint have at least the properties in two levels to be angled, the radius gears in play to maintain mutual engagement and each other Adjust joint position. This is, for example, by a resilient mounted eyelet or universal joint realized.

It is known to meet the requirement of a 90 ° constant velocity joint with radius gears in to keep mutual engagement, a spring-loaded To use inner joint according to DE 40 30 737 C2, the Inner joint is realized by an eyelet joint. Here there are two spring-mounted draw bolts that are attached to a ring eyelet on the side facing the center of the joint have, which in the eyelet of the other draw bolt in two levels intervening.

However, the resilient support of the draw bolts has an effect on the behavior of the constant velocity joint as it is caused by the spring preload strives to be stretched Taking position despite a bent position, which Power loss in torque transmission in one approx. 15 ° angled position are recorded.

The invention is based on the object To provide double cam joint as an inner joint, which in can be angled through two planes through the radial gears Disc spring assemblies hold each other without play and adapts to the respective joint position without  the constant velocity joint tends to be its stretched position despite a bent position to take.

This object is achieved by the im Labeling part of claim 1 specified Features resolved.

The advantages achieved with the invention exist especially in providing a double cam joint, the properties of the previous internal joints same, but for the diffraction angle between approx. 3 and 90 ° an internal pivot point shift of the Double curve joint enables. This keeps it Constant velocity joint in the selected flexion position without that Aim to show yourself in the stretched position push back. At a diffraction angle approximately smaller than 3 °, a length compensation of a few tenths is sufficient Millimeters, so that the deflection is not due to the Double curve joint can be achieved, but through the respective length compensation of the disc springs takes place, as the double cam joint in the extended position in one self-locking position. This locked position is necessary to a deflection in two levels of the Allow double cam joint because of the deflecting Part that is centered in relation to the Ends of the constant velocity joint remains arranged, either from Swing, then the axes are fixed and therefore in the locked position or from the two axles, which then due to the swing arms in the locked position held together, can exist. Only with one The constant velocity joint is bent over approx. 3 ° Deflection of the double cam joint causes.

Advantageous refinements of the invention result from the characteristics of the subclaims.

An embodiment of the invention is in the following Drawings shown and described in more detail below. It shows

Fig. 1 shows the full section of the stretched constant velocity joint with the double cam joint in front view,

Fig. 2 is a full sectional view of the constant velocity joint in the 90 ° position with the deflected double cam joint in front view,

Fig. 3 shows the full section of the stretched constant velocity joint with the double cam joint in the side view,

FIG. 4 is a full sectional view of the constant velocity joint in the 90 ° position with the deflected double cam joint in the side view,

FIG. 5 is a full sectional view of the stretched constant velocity joint and the double cam joint in plan view,

Fig. 6 shows the section of a full radii gear for explaining the profile contact ratio (particularly in the extended position) of the constant velocity joint,

Fig. 7, the linear guide of the double cam joint and

Fig. 8, the circular arc of the double cam joint.

The constant velocity joint shown in Fig. 1 is shown with two radial gears ( 1 ) in the stretched state (180 °) in the front view. A radius gear ( 1 ) has two coaxial recesses, one centering bush ( 2 ) being embedded in each of the radius gear ( 1 ). In order to keep the radial gears ( 1 ) in mutual engagement in each joint position, a double cam joint is accommodated via the centering bushes ( 2 ). The centering bushing ( 2 ) is preferably provided with a collar on a side facing away from the center of the joint in order to be able to absorb axial forces. An axial deep groove ball bearing ( 3 ) is arranged in the other coaxial recess for each radial gear ( 1 ) in order to absorb the occurring axial forces and to separate the rotating radial gears ( 1 ) including the respective centering bush ( 2 ) from the stationary double cam joint. For example, an axial roller bearing should be used for higher loads.

The double cam joint essentially represents a double universal joint equipped with cube-shaped ax crosses ( 7 ) mounted in guides ( Fig. 7, Fig. 8), which is supported on two axial deep groove ball bearings ( 3 ) by means of two nuts ( 4 ) and disc springs ( 5 ). The disc springs ( 5 ) are axially displaceably received via a collar of the double cam joint fork ( 6 ), the collar having to correspond to the inside diameter of the disc springs ( 5 ) in order to prevent radial displacement of the disc springs ( 5 ). Likewise, the outside diameter of the disc springs ( 5 ) must be selected according to the diameter of the axial deep groove ball bearing in order to prevent the disc springs ( 5 ) from slipping off the axial deep groove ball bearing ( 3 ). A hole nut ( 4 ) has two bores on the end face, which have the same radial distance from the central axis of the hole nut ( 4 ). In addition, the perforated nut ( 4 ) has a coaxial recess to accommodate the collar of the double cam joint fork ( 6 ) and a coaxially arranged internal thread, similar to the external thread of the double cam joint fork ( 6 ). Via this threaded connection, the constant velocity joint can be adjusted without play by tightening the nuts ( 4 ) just enough that no more play is noticeable in the guides ( Fig. 7, Fig. 8). It is important to ensure that the double cam joint remains in the center of the ends of the constant velocity joint in order to ensure uniform deflection of the respective deflecting parts. Therefore both hole nuts ( 4 ) have to be adjusted accordingly. If play is caused by wear, the hole nuts ( 4 ) can be adjusted accordingly. A slight preload can also preferably be applied in order to be able to automatically compensate for play that occurs later. So that the perforated nuts ( 4 ) do not turn automatically during operation, a locking plate should preferably be attached as a thread lock (not shown).

Compared to a double universal joint, which has one bearing point on four sides on each axis and thus has eight bearings on the entire joint with two axles, four bearing points occur on four sides of the double joint ( 7 ) on each side, which means that the entire double curve joint has two Axis crosses ( 7 ) create thirty-two bearings. That is, occur with respect to a bearing point at the double universal joint, four bearing points in the double-curved joint, in Fig. 1, 2, 3 and 4, by four in guides (Fig. 7, Fig. 8) bolts absorbed (9) can be realized. For each double-curve joint fork ( 6 ), guides ( Fig. 7, Fig. 8) in Fig. 1 and 2, an axle cross ( 7 ) is added. The two coordinate systems (7) of the double cam joint are opposed via two guides (Fig. 7, Fig. 8) mounted to the double-curved joint forks (6) by 90 ° staggered wings (8) connected to each other. Each rocker ( 8 ) has four fixed bolts ( 9 ), two bolts ( 9 ) each engaging in the circular arc guide ( Fig. 8) of a cross ( 7 ). At the same time, each rocker ( 8 ) has two linear guides ( Fig. 7) in which in turn two of the bolts ( 9 ) fixed on the axles ( 7 ) on each side are guided. As already mentioned, this creates four bearings per side.

Accordingly, it also behaves in Figs. 3 and 4 drawings, there occur relative to a bearing point at the double universal joint, four bearing points in the double-cam hinge by four in guides (Fig. 7, Fig. 8) bolts absorbed (9) can be realized. Two fixed bolts ( 9 ) are attached to each double cam joint fork side, which in turn engage in the linear guide ( Fig. 7) of the axles ( 7 ). At the same time, two bolts ( 9 ) fixed on the axles ( 7 ) reach into the circular arc guide ( Fig. 8) of the double cam joint fork ( 6 ) on each side. This also creates four bearings on each side.

To enable assembly, the two rockers ( 8 ) must be held together with a detachable connection. A thread is therefore preferably placed in the middle of each rocker arm ( 8 ), in which a threaded pin ( 10 ) can be received, which is provided with a right-hand and a left-hand thread at its ends, and preferably on the lateral surface of the threaded pin ( 10 ) has two mutually parallel surfaces in order to enable the set screw ( 10 ) to be rotated with an open-end wrench (not shown) in order to connect the two rockers ( 8 ) to one another. Visible in FIG. 5. Accordingly, one rocker ( 8 ) has a right-hand thread and the other rocker ( 8 ) has a left-hand thread. It is necessary to glue the threads, for example, to prevent the thread connection from being loosened unintentionally. So that in the extended position of the constant velocity joint the set screw ( 10 ) does not collide with the axis crosses ( 7 ), a continuous semicircular recess is made on the side facing the center of the joint depending on the direction and the diameter of the set screw ( 10 ) for each axis cross ( 7 ).

From Fig. 1 and 2 it can be seen that the wings ( 8 ), here the deflecting parts, can perform a longitudinal movement due to their linear guide ( Fig. 7) and at the same time through the circular arc guide ( Fig. 8) of the axis cross ( 7 ), endeavor to adapt their rotary movement to the circular arc guide ( FIG. 8).

Also in Fig. 3 and 4 it can be seen that the axis crosses (7), representing here the deflecting parts, which are held together by the wings (8), as mentioned above, undergo a longitudinal movement as a result of its linear guide (Fig. 7) can and at the same time by the circular arc guide ( Fig. 8) of the double cam joint fork ( 6 ) endeavor to adapt their rotary motion to the circular arc guide ( Fig. 8). In order to be able to move the deflecting part into the desired positions without colliding with the surrounding space, it is necessary to attach the linear guide ( Fig. 7) to the deflecting parts and to arrange the circular arc guide ( Fig. 8) accordingly on the fixed parts. Furthermore, it is necessary to provide the respective deflecting parts with corresponding radii or chamfers on their outer contours so that a collision-free deflection can take place.

In Fig. 1 and 2 and Fig. 3 and 4, the condition must be met that a longitudinal displacement of the wings ( 8 ) in Fig. 1 and 2 or the axles ( 7 ) held together by the wings ( 8 ) in Fig. 3 and 4, without simultaneously performing a rotary movement through the circular arc guide ( Fig. 8) remains excluded. This is made possible by the fact that in each position of the rockers ( 8 ) in FIGS. 1 and 2 or the ax crosses ( 7 ) held in FIGS. 3 and 4 by the rockers ( 8 ), at least two bolts ( 9 ) out of four per side possible, by their respective guides ( Fig. 7, Fig. 8) as tangential to each other. This means that the guides ( Fig. 7, Fig. 8) of the engaged bolts ( 9 ) are arranged at approximately 90 ° relative to each other in almost every joint position. As a result, at least sixteen bolts are always available for the axial forces that occur and for the required guidance ( FIG. 7, FIG. 8). Furthermore, the guides ( Fig. 7, Fig. 8) are designed so that a length compensation of the double cam joint is only possible if at the same time the radius gears ( 1 ) are deflected around the pitch circle (T). If there is no profile shift and no head and foot play on the radius gears ( 1 ), the pitch and pitch circles are identical. It is absolutely necessary for the deflection that the tooth flanks of the radius gears ( 1 ) are leveled in the area of the profile overlap in the extended position of the constant velocity joint, so that complete contact of one radius gear ( 1 ) with the respective centering bushing ( 2 ) of the other radius gear ( 1 ) can be done. Otherwise the mutual support of the radius gears ( 1 ) would not take place on the centering bush ( 2 ), but only on the tooth flanks of the two radius gears ( 1 ). This is possible in the area of the profile overlap in the extended position of the constant velocity joint without affecting the rolling of the radial gears ( 1 ), since there is no rolling on the tooth flanks of the radial gears ( 1 ) at small diffraction angles.

In order to obtain a greater profile overlap of the radius gears ( 1 ) in the extended position, the coaxial recess can be enlarged as shown in FIG. 6. This causes an increase in the tooth depth on the pitch circle (T '), whereby a better profile coverage in the extended position (180 °) is achieved. This gives you a new radius gear ( 1 ') with associated centering bush ( 2 ').

To FIGS. 7 and Fig. 8 in detail.

Fig. 7 is the linear guide ( Fig. 7) of the double cam joint with a total of four sections (AB, AE, CD, CE). The linear guides ( FIG. 7) shown on FIGS. 1 and 2 on the rockers ( 8 ) are arranged such that when the constant velocity joint is stretched, where the bolts ( 9 ) are at positions 5 (A) and (C), which exist in FIGS . 1 and 2 on the axis cross ( 7 ) and in FIGS . 3 and 4 on the double cam joint forks ( 6 ), depending on the angle of the constant velocity joint via the radius gears ( 1 ), to the positions (E) and (D) or (E) and (B). The bolt ( 9 ) in position (A) can only move on the route (AB) or (AE) depending on the direction of deflection. Correspondingly, the bolt ( 9 ) located in position (C) can only be moved on the line (CD) or (CE). The distances between the positions (AC) and the positions (EB) or (ED) are the same length, whereby the position (E) is located on the center of the respective deflecting parts in order to equalize both deflections from the respective bolts ( 9 ) can be used. The linear guide ( FIG. 7) is arranged in such a way that the position (E) defines the end position of the constant velocity joint that is angled to 90 °, the respective deflecting parts only pivoting by 45 °. However, since there are two linear guides attached to each other in a mirror-image manner on the respective deflecting parts, this results in a deflection of 45 ° with respect to the respective fixed parts, as a result of which an overall deflection angle of 90 ° is achieved.

Fig. 8 is the circular arc ( Fig. 8) of the double cam joint with a total of four sections (ZY, ZV, XW, XV). The circular arc guides ( Fig. 8) shown in Figs. 1 and 2 on the axles ( 7 ) are arranged so that when the constant velocity joint is extended, where the bolts ( 9 ) are at positions (Z) and (X), which are fixed in FIGS. 1 and 2 on the rocker arm (8) and in Figs. 3 and 4 to the axis crosses (7) depending on the angulation of the constant velocity joint on the radii of gears (1) to the position (V) and ( W) or (V) and (Y). The bolt ( 9 ) in position (Z) can only be moved on the route (ZY) or (ZV) depending on the direction of deflection. Accordingly, the bolt ( 9 ) located at position (X) can only be displaced on the line (XW) or (XV). The distances between the positions (ZX) and the positions (VY) or (VW) are the same length, whereby the position (V) is located in the middle of the respective fixed parts, in order to equally for both deflections from the respective bolts ( 9 ) can be used. The circular arc guide ( Fig. 8) is arranged so that the position (V) makes the end position of the constant velocity joint angled to 90 °, the fixed part only allowing deflection of the deflecting parts up to 45 °. However, since there is a circular arc guide ( FIG. 8) arranged in mirror image to one another on each of the respectively fixed parts, this results in a deflection of 45 ° for the respective deflecting parts, as a result of which a diffraction angle of 90 ° is achieved overall.

With this double cam joint as the inner joint, you can smallest space two 90 ° constant velocity joints in a row can be connected, for example in a U arrangement To achieve a total change in direction of 360 °.

To ensure adequate lubrication of the 90 ° constant velocity joint, a bellows containing oil or grease must be attached. Thus, it has a Axialwellendichtring be mounted between the centering sleeve (2) and the axial grooved ball bearing (3) to allow trapped in the bellows oil or grease can not escape through the gap between centering bush (2) and double-curved joint fork (6) is not provided to the A corresponding oil-filled container is attached to the ends facing away from the constant velocity joint, which encloses the disc springs ( 5 ), the axial groove ball bearing ( 3 ) and the hole nut ( 4 ) and lubricates the axial groove ball bearing ( 3 ) from the outside through the oil filling (not shown).

Reference list

Double cam joint with internal length adjustment for 90 ° constant velocity joints with radius gears

A position on the linear guide
B Position on the linear guide
C position on the linear guide
D position on the linear guide
E position on the linear guide
Z position on the circular arc guide
Y position on the circular arc guide
X position on the circular arc guide
W position on the circular arc guide
V position on the circular arc guide
T pitch circle of the radius gear
1 radius gear
2 centering bushes
3 axial deep groove ball bearings
4 hole nut
5 disc spring
6 double cam joint fork
7 axis cross
8 swingarm
9 bolts
10 grub screw
T 'pitch circle of the radius gear with increased profile overlap
1 ′ radius gear with increased profile coverage
2 ′ centering bush of the radius gear with increased profile overlap.

Claims (9)

1. constant velocity joint with radial gears for positive transmission of a rotary movement, held together by a spring-loaded inner joint, optionally for a diffraction angle up to 90 ° in two planes in mutual engagement, characterized in that
the spring-mounted inner joint of a resiliently mounted double cam joint, wherein the resilient mounting via plate springs (5), which are mounted on the threads of the double cam joint forks (6) between the perforated nuts (4) and Axialrillenkugellagern (3) of radii of toothed wheels (1) are included, are included to enable a length adjustment of the double cam joint at a diffraction angle of less than approx. 3 ° and to keep the radial gears ( 1 ) of the constant velocity joint in mutual engagement, and that the double cam joint consists of two centering bushes located in the radial gears ( 1 ) ( 2 ) rotatably and axially displaceably embedded double cam joint forks ( 6 ), in which two cube-shaped axles ( 7 ) pivotally mounted in guides ( Fig. 7, Fig. 8) are accommodated, which with two on opposite sides to the double cam joint forks ( 6 ) i n Guides ( Fig. 7, Fig. 8) pivotally mounted, by a detachable connection interconnected rocker ( 8 ) hold the double cam joint, without this striving to extend into the extended position of 180 ° from an angled position between approx. 3 and 90 ° back, and that the deflection of the double cam joint is carried out either with the two rockers ( 8 ) or with the axles ( 7 ) which are firmly connected by the wings ( 8 ), and that an ax ( 7 ) has four perpendicular bearing sides, each having four in guides (Fig. 7, Fig. 8) slidably located bolt (9), a linear (Fig. 7) and a circular arc guide (Fig. 8), and that
in every position of the deflecting parts, per bearing side of the axis crosses (7) at least two bolts (9) out of the four possible pin (9) by their respective guides (FIG. 7, FIG. 8) are tangential as possible to each other, and that the guides ( Fig. 7, Fig. 8) are arranged so that a length compensation of the double cam joint is only possible if the radius gears ( 1 ) are deflected around the pitch circle (T) at the same time, and that the guides ( Fig. 7, Fig. 8) on the one hand from a with four sections (AB, AE, CD, CE) linear guide ( Fig. 7), which is attached to the respective deflecting parts in the center and mirror image to each other, and on the other from one with four sections (ZY , ZV, XW, XV) circular arc guide ( Fig. 8), which is attached to the fixed parts in the center and mirror images of each other, are realized. 2. constant velocity joint according to claim 1, characterized in that the double cam joint fork ( 6 ) has at the end facing away from the constant velocity joint center a coaxially arranged thread to receive a hole nut ( 4 ) and in the further course towards the center of the joint has a coaxially arranged collar, accommodating the plate springs (5) axially displaceable, wherein, to exclude the waistband to a radial displacement of the disc springs (5) must be equal to the inner diameter of the disc springs (5) and facing the joint center side two offset from its fork-shaped recess 90 ° has mutually parallel recesses in order to allow the rockers ( 8 ), provided they represent the deflecting parts, a sufficiently large swivel range, and on the respective bearing sides to the axis crosses ( 7 ) a circular arc guide ( Fig. 8) and two fixed bolts ( 9 ) which are arranged so that they are in the linear guide ( Fig. 7) of the axles ( 7 ) in the extended position at positions (A) and (C) engage. 3. constant velocity joint according to claim 1 and 2, characterized in that the axles ( 7 ) on the respective bearing sides to the double cam joint fork ( 6 ) have a linear guide ( Fig. 7) and two fixed bolts ( 9 ) which are arranged so that they engage in the circular arc guide ( Fig. 8) of the double cam joint fork ( 6 ) in the extended position at positions (Z) and (X), and one circular arc guide ( Fig. 8) and two on the respective bearing sides to the rockers ( 8 ) have fixed bolts ( 9 ) which are arranged so that they engage in the linear guide ( Fig. 7) of the rocker ( 8 ) in the extended position at positions (A) and (C). 4. Constant velocity joint according to one of claims 1 to 3, characterized in that the rockers ( 8 ) on the respective bearing sides to the axis crosses ( 7 ) have a linear guide ( Fig. 7) and two fixed bolts ( 9 ) which are arranged so that they engage in the circular arc guide ( Fig. 8) of the crosses ( 7 ) in the extended position at the positions (Z) and (X), and the linear guides ( Fig. 7) are arranged in the center and in mirror image on the wings ( 8 ) are, and in the middle of each rocker ( 8 ) have a thread in which a threaded pin ( 10 ) is received, and the outer contour of the rocker ( 8 ) has radii or chamfers. 5. Constant velocity joint according to one of claims 1 to 4, characterized in that the radial gear ( 1 ) has two coaxial recesses in the inner contour, in which the centering bush ( 2 ) and the axial groove ball bearing ( 3 ) are received, and the radial gear ( 1 ) has two coaxial recesses on the inner contour, in which the centering bush ( 2 ) and the axial deep groove ball bearing ( 3 ) are accommodated, and on the outer contour has a collar on which a tube can be received, and the tooth flanks in the area of the profile overlap in the extended position not involute, but have a flat surface, and with an enlargement of the coaxial recess for the centering bushing ( 2 ), a greater profile overlap in the extended position. 6. constant velocity joint according to one of claims 1 to 5, characterized in that the centering bush ( 2 ) is provided on the side facing away from the center of the joint with a collar, and on the side facing the center of the joint on the outer contour has a concave recess around the radius gear ( 1 ) to support. 7. constant velocity joint according to one of claims 1 to 6, characterized in that the plate springs ( 5 ) are arranged for length compensation at a diffraction angle smaller than about 3 ° as a plate spring package. 8. constant velocity joint according to one of claims 1 to 7, characterized in that the hole nut ( 4 ) has two holes on the end face, which have the same radial distance from the central axis of the hole nut ( 4 ), and has a coaxial recess around which Take up the collar of the double cam joint fork ( 6 ), and has a coaxially arranged internal thread to receive the thread of the double cam joint fork ( 6 ). 9. constant velocity joint according to one of claims 1 to 8, characterized in that the threaded pin ( 10 ) has a right-hand thread on one side and a left-hand thread on the other side.