WO2011083094A1

WO2011083094A1 - Continuously variable transmission

Info

Publication number: WO2011083094A1
Application number: PCT/EP2011/000065
Authority: WO
Inventors: Peter Kobler
Original assignee: Peter Kobler
Priority date: 2010-01-11
Filing date: 2011-01-11
Publication date: 2011-07-14

Abstract

The invention relates to a continuously variable transmission (1), comprising at least one drivable shaft body (2) that can be rotated about the longitudinal axis thereof and a wobble body (16, 21) that is disposed on said shaft body and rotates with same and has at least one peripheral path, wherein the inclination of said wobble body can be adjusted with respect to the shaft body such that the shaft body does not perpendicularly extend through the main plane spanned by the peripheral path, and further comprising an even number of pick-up elements (22) for picking up substantially the axial component of the wobble motion of the wobble body at the peripheral path thereof in different phases. The pick-up elements are disposed in pairs diametrically in relation to each other, respectively, with respect to the longitudinal axis of the shaft body, and a corresponding number of rotation free-wheels (36), which can be neither displaced nor pivoted about an axis other than the respective rotational axis thereof, and which on the input side are each coupled preferably via a coupling device (26, 27) to a pick-up element, and on the output side are each coupled to a common output shaft (3); according to the invention, in each case two pick-up elements or coupling devices disposed diametrically in relation to each other are coupled on the other side of the respective rotation free-wheels to each other by a yoke such that, because of the yoke, they are forced to perform anticyclic path motions, while pick-up elements and/or coupling devices that are not disposed diametrically in relation to each other on the other side of the respective rotation free-wheels are not coupled to each other.

Description

Stepless transmission

The invention is directed to a continuously variable transmission, comprising at least one rotatable about its longitudinal axis, driven shaft body and arranged thereon and rotating with this tumbling body with at least one revolving path, which is adjustable relative to the shaft body in its inclination that of its circulating Track spanned main plane of the shaft body is not vertically interspersed, and an even number of Abgreifelementen for tapping substantially the axial component of the wobble of the wobble body on the circumferential path in different phases, the Abgreifelemente are arranged with respect to the longitudinal axis of the shaft body in pairs diametrically opposite each other, and a corresponding number of rotational freewheels which are neither displaceable nor pivotable about another axis than their own axis of rotation, and the input side preferably via a respective coupling device, each with one m tapping element and the output side are each coupled to a common output shaft.

Gear or couplings with a conversion of a rotational movement into a rotary motion, or vice versa, are used in particular as a variable transmission or as a pure coupling gear, both in purely mechanical form or as a mechanical-hydraulic converter, possibly also as part of an internal combustion engine. However, the proposed solutions are mainly associated with disadvantages, for example. The efficiency is often relatively unfavorable or the reaction is not smooth and even, but contains shock od. Like., Which usually suffers the achievable operating life.

If one considers only a section of the circumference of a wobble body held with respect to the rotation of the shaft, then this describes

CONFIRMATION COPY Section in an oblique position of the plane spanned by the circumference of the wobble body a vibration with a harmonic component in the longitudinal direction of the axis of rotation. Thus, such an arrangement is optimally suitable for converting a torsional vibration into an oscillating longitudinal vibration and vice versa. On the other hand, a harmonic oscillation for connected tapping generally represents a Wechselast, which loads the mechanics very much, because it is knocked out any time bearing with even the least clearance bearing over time and is exposed to relatively high wear, so that the achievable operating life is extremely limited.

From the disadvantages of the prior art described results in the invention initiating problem to develop a generic continuously variable transmission such that can achieve a favorable efficiency and also a long service life.

The solution to this problem is achieved in a generic device characterized in that two diametrically arranged each other tapping or coupling devices beyond the respective rotational freewheels are coupled together by a return that they are forced due to the inference to anti-cyclic path movements while not diametrically to each other arranged tapping elements and / or coupling devices are not coupled together beyond the respective rotational freewheels.

The wobble body is pivotable transversely or radially to the shaft body, such that the inclination of the wobble body relative to the shaft body is variable between a neutral position, which is characterized in that the normal, ie the solder, to the ground plane of the wobble body or at a same circumferential path is oriented parallel to the shaft body, to positions, which are characterized in that the normal to the ground plane of the wobble body or to a same circumferential path is not parallel to the longitudinal axis of the shaft body, but the longitudinal axis intersects at an angle α with 0 ° <α <90 °, preferably at an angle 0 ° <α <60 °, in particular at an angle 0 ° <α <45 °.

On such a pivotable swash body, in particular on its outer or peripheral circumference, a ring can be arranged there by means of a rolling bearing running around there, which is rotatable relative to the (inner) swash body, that can also be prevented from rotating while the ( inner) tumbling body rotates synchronously with the shaft body. Because thanks to the roller bearing of the ring does not follow the rotation of the shaft body, but can be held in contrast, so that it follows only the pivoting movement of the wobble body. This can be achieved, for example, by a guide which allows such a pivoting movement, but no rotation about the shaft body.

Depending on the embodiment, either a rotating wobble body itself or a ring rotatably mounted thereon can be used for picking up an axial component of the tumbling motion. Serving the tap, all-round path is arranged in the former case directly on the rotating wobble body, and the Abgreifelemente along it, while the all-round tapping path is formed in the second case by the rotatably mounted ring, on which the tapping elements can be connected directly , but in contrast mobile.

The liberated from rotation movement at the periphery of the wobble body therefore has a component in the direction of the shaft body, superimposed by a small radial movement. This oscillatory movement - either the pure longitudinal component in the direction of the shaft body, or the entire movement including the radial component, can be tapped. This can be done with pulling and / or pushing means which engage at a point or region of the wobble body or a ring mounted thereon and forward the longitudinal component of the oscillating longitudinal movement thereof to an output shaft of the transmission which, for example, be coupled to the rear hub of a bicycle could or with any other machine or device; In this case, the traction and / or pushing means may optionally be guided via deflection devices for converting the originally axial movement, relative to the longitudinal axis of the input shaft, into a tangential movement, relative to the longitudinal axis of the output shaft. There, they transmit their (now tangential) path movement to the output shaft via one freewheel and thereby drive it on. By the freewheels only one direction of movement of the traction and / or pushing means is transmitted, whereby the output shaft is driven in each case in the same direction, but alternately by different pulling and / or pushing means.

The more obliquely the wobble body is set relative to the shaft body, the greater is the amplitude of the oscillating longitudinal movements of the traction and / or pushing means, and the further and faster the output shaft rotates during one revolution of the shaft body serving as the input shaft. As a result, a variable ratio between input and output shaft is achieved, which is varied by the adjustment of the inclination of the wobble body.

By each two diametrically arranged tapping elements are coupled together either directly or via attached coupling devices by a conclusion, they are joined together in terms of movement. This has a number of consequences: On the one hand, this improves the management of the elements or traction and / or thrust elements coupled to one another in this way; on the other hand, by a kind of "inverting feedback" Only anti-cyclical orbital movements are permitted, whereby their disadvantages can be reduced or even avoided by superimposing two countercyclical alternating loads. The invention is characterized by at least one parallel to the shaft body and / or coaxial output shaft. This results in a for installation in a machine, a vehicle od. Like. Favorable geometry; For example, the transmission can be installed directly in a drive train instead of a shaft.

It has proven to be favorable that the rotational freewheels are stationary relative to the transmission chassis or housing. As a result, their output-side movements can be superimposed in a simple manner with a stationary summing device to a common, continuously progressive (rotational) movement.

It is within the scope of the invention that the rotational freewheels have two concentric rotational bodies, in particular two concentric rings. By influencing the coupling state between these two rings, the freewheel can switch between torque transmission and freewheeling state.

Preferably, the rotation freewheels are designed as sprag freewheels. These are distinguished by clamping bodies between the two rings of the rotary freewheel, which are received, for example, in cavities with a wedge-shaped cross section and depending on the relative direction of rotation or direction of the torque to be transmitted to the tapered end of the cavity reach (friction or torque transmission ) or to its extended end (decoupling or freewheeling state). Other types of freewheels are conceivable, for example. Pawl freewheels, wherein pawls get caught in ratchet teeth depending on the direction of the torque to be transmitted (Positive locking or torque transmission) or can slide over them (decoupling or freewheeling state).

Further advantages result from the fact that the axes of rotation of all rotational freewheels are parallel to each other. As a result, a summing can be realized with little effort, for example. By the output side freewheel rings or rotatably coupled therewith rotary body, for example. Waves, wheels, pinion, each with an all-round one (outer) teeth are provided. These teeth of all freewheels can be coupled together by an element with a row of teeth, for example a toothed sun or ring gear, a chain or the like, which meshes the above teeth of all freewheels in the manner of planetary gears.

The invention allows a development to the effect that the axes of rotation of all rotational freewheels are aligned. This allows a development to the effect that several or preferably all rotational freewheels are arranged directly on the output or output shaft, in particular with one of its terminals are non-rotatably connected. In this case, the output shaft itself forms quasi the summing device, and is driven by the progressive movement of the output side in each case the fastest rotating freewheel in always the same direction of rotation. It therefore makes sense to speak of an output-side progression body, in particular of a progression wave, in the output wave, since the angle of rotation of this progression wave always proceeds in a single direction of rotation.

The invention recommends that all coupling elements of a coupling device between the swash body and the relevant freewheel are each loaded simultaneously on train or on pressure. Here are elements that are not behind the wobble body, but at the same level or before the same, the tapping and are therefore not covered by this feature. A preferred embodiment of the invention is characterized in that all coupling elements of a coupling device between the swash body and the respective freewheel are always loaded on train or always on pressure. Thus, alternating loads are avoided, which has a particularly advantageous effect on the achievable operating life. Again, elements that are not behind the wobble body, but at the same level or before the same, the gripper and are therefore not covered by this feature.

In the context of the invention, a pulling and / or pushing means coupled to a ring or ring segment of the wobble body is connected to one or more freewheels in each case. In pursuit of the inventive concept is further provided that the coupling device comprises a traction means, in particular a chain, the chain links are always loaded on train.

As traction means, the use of a chain with a plurality of mutually movable or movably coupled chain links is recommended.

At least one per the chain deflecting means, for example. One or more pulleys. Such a chain deflection means divides the respective chain into two strands, one of which extends within a plane (s) approximately radial to the longitudinal direction of the shaft body up to the swash body and is connected to a ring there, while the other strand is within one of the longitudinal direction the shaft body about vertically interspersed level to a freewheel or a coupled (chain) wheel od. Like. Coupling extends and is engaged. These pulleys can be mounted stationary and immovable in the transmission housing or on the transmission chassis, so that only a rotation of the pulleys about their axes of rotation is possible. However, in order to tolerate lateral movements of a chain, the storage of a deflection roller on the transmission housing or chassis can also be designed to be movable, in particular pivotable.

For this purpose, a deflection roller may be mounted on a pivoting device, for example, one with a straight sleeve, which surrounds at least one run of the chain. Such a sleeve may extend beyond the respective deflection roller. So that the chain can leave this sleeve in the region of the deflection roller, this has a lateral slot of sufficient size. Adjacent to this slot can / can one or two flags be recognized, for example. Welded, soldered or glued, on or between which the guide roller is mounted. Preferably, these two flags extend beyond the circumference of the deflection roller in the direction of the second run. Such a sleeve may be mounted on the housing or chassis of the transmission, preferably in two radial bearings, which allow both rotation of the sleeve about its longitudinal axis and a displacement thereof in the direction of its longitudinal axis, but the radial orientation of the sleeve with respect to to ensure the appropriate strand. A tension of the chain would be possible via a third bearing on the housing or chassis. For this purpose, the peripheral end of the sleeve could be rotationally coupled via a thrust bearing, so that rotation or oscillation of the sleeve about its longitudinal axis does not transfer to the second bearing part of this thrust bearing. This thus dreenktkoppelte bearing part could then be attached directly to the housing or chassis of the transmission; However, this is preferably done via a spring which tends to pull the sleeve against the first strand until the chain is sufficiently tensioned. By created by the pivot bearing of the sleeve, additional degree of freedom Movement such a pendulum deflection pulley can track the tumbling movement of the traction means-articulation points on the common ring, so that no unacceptable transverse deflections are imposed on the drive strand of a chain coupled to the torsionally coupled ring.

The invention further provides that in at least one run of the chain, preferably in the second, a freewheel facing Trum a universal joint is arranged. For a traction means in the form of a chain is preferably guided over a deflection roller, which is located next to the output or progression wave. The traction means can run from this pulley to one of several freewheels on the output or Progressionswelle and is there connected to a peripheral housing portion of the respective freewheel and / or coupled. Depending on the rotational position of the housing section, the chain in question moves along its path. In an area of the chain, which never comes into contact with the freewheel, there is an inventive crossing point, where the alignment of the chain links is offset by about 90 °. On the other hand, the distance of such a chain universal joint to the connection point on the ring or ring segment should be greater than the maximum axial stroke of the wobble body.

A realization of the engagement between traction means and freewheel can consist in that a row of teeth is arranged on the freewheel or a wheel coupled thereto, with which the chain meshes. On the other hand, a fixed coupling is possible by, for example, a chain link is firmly connected to the relevant part of the freewheel, for example. Welded to the outer surface, screwed od. Like. By thus one end of the chain with the freewheel or a wheel coupled thereto is connected, it can be ensured that the interlocking parts can not come apart. If a chain is biased by a clamping means, it remains independent of the inclination position of the wobble body in a stretched state.

When using chains as coupling devices, the invention inference can be achieved by the union of two chain-coupling devices, in particular by using only a single chain.

Another embodiment of the invention is characterized in that the coupling device has a guide track for juxtaposed mechanical pressure body, which are always loaded on pressure. In this embodiment, the guide track for mechanical pressure bodies of a coupling device can experience at least one deflection.

In such a case, the invention recommends that the conclusion is formed by the union of two tracks for mechanical pressure body.

In the context of a first embodiment it can be provided that a ring rotating around the wobble body is driven in the longitudinal direction of the shaft axis in the form of an oscillating longitudinal movement. In this case, the shaft body serves as an output shaft or is coupled to an output shaft. However, an embodiment is preferred, wherein the shaft body is driven to rotate about its longitudinal axis. In this case, the drive could, for example. Via a motor, in particular via an electric or hydraulic motor, but possibly, for example. Also a steam engine or other drive means. According to the concept of the invention, the movement of a ring surrounding the wobble body (approximately) within one or more planes, which are approximately radial to the longitudinal direction of the shaft body, is tapped and coupled to the output. The input and / or output could include, inter alia, one or (each) comprise a plurality of hydraulic cylinders, whereby a hydraulic fluid is set or held in flux, or (depending) a chain or other rotary, pushing and / or pulling means, which can transfer the available power to another machine or plant component.

The invention further provides that at least one rotatably mounted on a wobble body ring or bearing ring segment is guided non-rotatably by means of a guide, so that the rotational movement of the rotatably driven wobble body from the movement of at least one bearing ring or ring segment is filtered out.

Furthermore, it is the teaching of the invention that the ring guide is located within a plane parallel to the longitudinal axis of the shaft body, within which two connection points of the ring in question. As a result, the tapped at these two connection points movements are free of any harmonics in the direction of rotation of the drive shaft.

Preferably, two pushing and / or pulling means are each connected to diametrically opposite regions of a ring or ring segment rotatably arranged on the wobble body.

According to the invention, a plurality of pairs of thrust and / or traction means, each coupled diametrically to one another to a ring or to a ring segment, are provided whose points of application in the area of the wobble body are displaced relative to one another by less than 180 °. The invention is further characterized by two pairs of mutually diametrically arranged pushing and / or pulling means, which pairs are offset by an angle of 90 ° to each other, or by three pairs of diametrically opposed pushing and / or traction means, which pairs to an angle of 60 ° are offset from each other. By superimposing several phases, a continuous, seamless torque transmission can be realized.

It is within the scope of the invention that different thrust and / or traction means pairs are arranged on different, mutually rotatable rings or ring segments of the wobble body. Each of these rings may be guided in the plane of the stripper pair in question, so that the resulting movement of the tap points always remains in the plane defined by the relevant guide.

The invention undergoes further optimization in that a pulling and / or pushing means is connected via a two-dimensionally acting joint to a ring or ring segment in order to isolate the longitudinal movement of the pulling and / or pushing means from the tumbling motion of the wobble body.

For this purpose, a gripping device may have an approximately triangular shape, in particular in the form of an isosceles triangle, wherein a secant-like strut is rotatably mounted about its longitudinal axis between its two side limbs. This carries in its center a perpendicular thereto extending second axis of rotation; it is therefore a double joint in the manner of a cardan joint. In this case, this second axis of rotation may be mounted on a torsionally coupled ring of the wobble body, for example. Between two arranged there, for example. Welded tabs or bearing blocks, while the traction means may be articulated at the top of the Gleischschenkligen triangle between the two same legs, for example there eye. In pursuit of this inventive concept, it is provided that the joint between a pulling and / or pushing means and a ring or ring segment via a pressure-loaded part.

Since the wobble body wobbles during operation, the Zugmittelanbindung must be movable in any direction, and this at very high forces to be transmitted. To meet this requirement, a sphere is inserted between two hollow spherical surfaces. One of the two spherical surface is located in the torsionally coupled ring and faces away from the output shaft; the other hollow-spherical surface is located on a plate on the inside of a U- or O-shaped bracket, which surrounds the ball on its first hollow-spherical surface opposite area, for example. In the manner of a stirrup, which engages around a foot , The side legs of this bracket pass through two with respect to the first spherical surface diametrically opposed holes in the rotating coupled ring. Beyond this ring the connection to the traction means takes place.

The pressure-loaded part - for example the ball described above - can be movable relative to the traction means and / or relative to the ring or ring segment. As a result, the connecting line between the rolling points between the ball on the one hand and the hollow spherical surfaces lying on the other hand in each position of the wobble body exactly align in the pulling direction of the traction device and then passes exactly through the center of the ball. Since the plate aligns with the center of the ball, there is no sliding friction, at most an extremely low rolling bearing friction.

It has proved to be favorable that a wobble body is limited by curved surfaces, in particular by concave or convex curved surfaces. The tumbling body itself need not be even or circular. It is sufficient that a circumferential, flat and circular path is provided. Alternative tumble body cross sections with a shape corresponding to a double concave curved lens are conceivable, for example; or with a shape corresponding to a double convexed lens. A wobble body may also have a spherical surface for greater stability. A tumbling body can either be solid or hollow, for example to save weight.

In the context of a first embodiment of the invention, the pivot point of the wobble body could lie on the longitudinal axis of the shaft body. In this case, the pivoting guide can be made exclusively on the local pivot axis, or by means of lateral bracket on the shaft body, which surround the actual pivot axis arcuately, for example. On the type of tines of a fork. To increase their stability deratige arcuate bracket may be connected together at their peripheral ends.

Another embodiment of the invention is characterized in that the pivot point of the wobble body is displaced eccentrically to the axis of rotation of the shaft body. This has compared to an arrangement, wherein the pivot point of the wobble body passes exactly through the center, control engineering advantages. In particular, in a central pivot point, a self-regulating system by means of spring element and damper, the transmission ratio is to be controlled, for example, based on the actual torque value to a set torque setpoint, would not work because the required controlled system is not present (among other things, a pivoting leads the wobble body beyond the neutral position not to a different gear ratio than a pivoting of the wobble body this side of the neutral position; a reversal of the direction of rotation on the output shaft can not be realized in this way). This does not apply to an actuated system. In a preferred embodiment of the invention, the pivot point of the wobble body at a distance from the axis of rotation of the shaft body, which corresponds approximately to the radius of a circumferential ring. Such a displacement of the pivot point from the center point into the peripheral region of the wobble body ensures that the necessary controlled system is generated for such a self-regulating spring damper system.

The pivot axis may be located at the free end of a laterally projecting from the driven shaft body approximately in the radial direction extension.

On the other hand, an example. Spherical wobble body to be fixed to this one of the pole axis passing rod which is pivotally mounted with one of its ends on an eye of a leg of an approximately semicircular fork, which in turn is rotatably connected to the driven shaft body, while the other End of the pole rod is guided on a second leg of the fork and can serve as a control terminal, in contrast to the first end of the pole rod, which serves as a pivoting connection.

An eccentric pivot point may cause the wobble body at a larger pivot angle away from the center or the rotation axis of the shaft body. The error deviation is relatively low, but could still lead to imbalances. To compensate for the error, it is possible to guide the wobble body at its center or center of gravity concentric to the drive axle or to the shaft body. A corresponding storage should be designed in this way be that with simultaneous tilting of the wobble body, a length compensation of the pushing and / or pulling means is made possible.

In this case, in addition to the control function, a control connection can also assume an additional guiding function, namely in each case in the radial direction, relative to the axis of rotation of the input shaft body, while at the same time the swivel connection has clearance in the radial direction. This can be effected in a pivotal connection, that in the wobble body, a slot or slot is provided in the ground plane of the wobble body path, wherein a pin or an axis of a laterally projecting from the shaft body extension engages.

On the other hand, in the pivot connection, an additional, approximately parallel to the shaft body intermediate lever between the wobble body and the laterally projecting from the shaft body extension could be inserted, which also allows a radial clearance,

In one or both embodiments, at least one leg may be provided in the region of the control connection to the shaft body with a slot extending approximately in the axial direction, wherein a lateral pin or other extension of the wobble body engages the guide. The two lateral extensions of the shaft body should be balanced. This can be done, for example, by the fact that both are formed symmetrically to each other, on the type of fork already described above.

So that such a guidance of the center or center of gravity of the wobble body concentric with the drive axis or with the shaft body does not lead to overdetermination and thus to jamming of the mechanism, the pivot point of the wobble body can be movably supported or guided. In particular, the pivot point of the tumbling body could a movable linkage or at least be arranged on a rod, which in turn is movable relative to the shaft body.

In order for such a linkage or such a rod itself does not produce an imbalance, the invention further provides that a structurally identical linkage or a structurally identical rod for adjusting or controlling the pivot angle of the wobble body is used, which (s) - point-symmetrical with respect to the center or Center of gravity of the tumbling body to the pivot point acts on the wobble body, so together with this and rotates with the pivot point and the shaft body, but compensates due to its opposite eccentric position, the imbalance of the pivot bearing. An axial offset between the two rods or rods - ie between the pivot terminal on the one hand and the control terminal on the other - leads at most to a bending stress of the shaft body, but the same causes no appreciable oscillations in a sufficiently stable execution thereof.

Preferably, the radial distance of a tapping device to the axis of rotation of the shaft body is smaller than the radial distance of a pivoting and / or control connection. As a result, the force introduced by each pick-up device into the swash body is always distributed to both connections-swivel and control connection-and there is no alternating load even in the region of these connections of the swash body. This condition can, for example, be achieved in that the wobble body or a torsionally coupled ring on its outer periphery has an all-round slot, wherein the tapping means are guided radially inwardly and finally in a radially inner track with the wobble body or ring in contact to step. In order to guide the wobble body precisely while avoiding a tilting of the wobble body about the axis spanned by the pivoting and control terminal, can be attached to the wobble body in addition to the Pivoting and the control terminal to be provided at least two further guide connections. Preferably, these two guide connections are symmetrical to the axis spanned by the pivoting and control connection. On the other hand, the wobble body 5 may also be mounted by means of radially projecting pins on a sleeve which is guided linearly displaceably on the input or output shaft.

Further features, details, advantages and effects on the basis of the invention will become apparent from the following description of some preferred i o embodiments of the invention and from the drawing. Hereby shows:

Figure 1 is an inventive, continuously variable transmission without housing in a perspective view, partially blown.

FIG. 2 shows the rotating parts of the transmission from FIG. 1, likewise in a perspective, partially exploded view; FIG.

3 shows a longitudinal section through the Fig. 2.

FIG. 4 shows a schematic longitudinal section through the wobble body and two tapping devices together with coupling devices connected thereto of another embodiment of the invention; FIG. such as

25 Fig. 5 the wobble body and two tapping devices together with attached coupling devices of a again modified embodiment of the invention in a Fig. 4 corresponding representation.

The transmission embodiment 1 of FIGS. 1 to 3 has a tubular input shaft 2 and a likewise tubular output shaft 3, wherein the outer diameter of the input shaft 2 is smaller than that Inner diameter of the output shaft 3, so that the input shaft 2 and the output shaft 3 can be arranged coaxially with each other, as can be seen most clearly from Fig. 3. The housing removed in the illustration surrounds the entire transmission 1 and is penetrated by the input shaft 2 and / or the output shaft 3 - or by drive and / or output shafts coupled thereto in a rotationally fixed manner. The housing may be provided with fastening means, for example with a flange threaded through by fastening bores.

In the illustrated embodiment, the input shaft 2 engages in the output shaft 3 in some areas. Between the two parts and coaxial with these is a control sleeve 4. The control sleeve 4 is in the axial direction relative to the input and output shafts 2, 3 slidably. This has an approximately annular central region 6 with a large central recess which is penetrated by the control sleeve 4, as well as two approximately diametrically arranged thereon, from the ring approximately radially one of these arms 7 may be mounted on the housing or chassis of the transmission 1, for example, about a pivot axis, not shown, which is approximately perpendicular to the longitudinal axis of the respective arm 7, within a plane which is penetrated by the longitudinal axis of the control sleeve 4 approximately vertically. The other, this support arm 7 approximately diametrically opposite arm 8 is preferably longer than the support arm 7 and preferably engages through the housing of the transmission 1. By adjusting this externally accessible actuating arm 8, the transmission ratio of the transmission 1 can be changed continuously.

For this purpose, a rod 9 is hinged to the annular central region 6 of the control bracket 5, which is hingedly connected to a further ring 10. This is in contact with another, parallel to this and rotatable relative to this ring 11, which in turn abuts against a circular collar 12 of the control sleeve 4 or is connected thereto. As a result, the control sleeve 4 undergoes axial adjustment movements in accordance with the movements of the actuating arm 7.

The collar 12 is located at or in the vicinity of the transmission input end facing (s) of the control sleeve 4. Before that there is a to the collar 12 on the control sleeve 4 approximately the same collar 13, which surrounds the tubular input shaft 2 and rotatably with this connected is.

In the circumference of the two collars 12, 13 there are two or more, (in each case) pairs diametrically opposed incisions or notches 14. At least on one side of a collar 12, 13 these are each one approximately tangential to the respective waistband circumference extending pin, wire od. Like. Interspersed, on each of which an elongated connecting element 15 is anchored with eyes in the region of its two ends articulated. In this case, the respective other ends of these elongated connecting elements in approximately axial directions toward each other and are hinged to a ring 16 which engages around the input shaft 2 at a radial distance. In this case, the points of articulation of the various connecting elements 15 on the ring 16 are diametrically opposite each other. This has the consequence that the ring 16 in an axial displacement of the control sleeve 4 by actuating the actuating arm 8, although in an inclined position, but still receives no static imbalance. Contributes to this, inter alia, that the two connecting elements 15 are identical to each other, and also that the two collars 12, 13 are each symmetrical in itself, ie the notches 14 for receiving a connecting element 15 each arranged a blind notch 14 without function opposite is. The ring 16 rotates synchronously with the input shaft 2. For this purpose, the input shaft 2 is provided with two radial projections 17 which, for example, can be formed by a pin 18 passing through the input shaft. On the input shaft is seated a sleeve 19 which has two diametrically opposed longitudinal slots, in each of which a radial extension 17 of the input shaft 2 engages to take the sleeve 19 drehbewegungsmäßig, regardless of the exact axial position of the sleeve 19. To the two, By halves of the sleeve 19 separated from one another by more or less long or possibly even longitudinal slots, the sleeve halves can be connected to one another by an internal web 20. In order not to obstruct the sliding of the sleeve 19 in the longitudinal direction, two elongated holes are provided in the input shaft 2 for such a web 20. The web 20 is extended in its two directions in each case beyond the sleeve 19 and rotatably received in recesses provided in the ring 16, so that the ring 16 can pivot about the web axis, but in terms of its axial position alone according to the interaction of two connecting elements 15 - in particular the axial distance of their articulation points - can set.

The ring 16 therefore behaves like a wobble body, but is displaceable in its longitudinal direction relative to the input shaft 2. This allows a development of the invention, not shown in the drawing, wherein the tubular input shaft 2 is not fixed in the axial direction within the gear housing, but slidably mounted and beyond even with the control sleeve 4 is movably coupled such that these two bodies 2, 4th perform countercyclical axial control movements of equal amplitude. This can be achieved, for example, by a corresponding coupling at one end of the two bodies, for example in the region of the output shaft 3. The output shaft 3 can end for this purpose within the gear housing and with a gear for Be provided output, while beyond its end a coupling device for the two bodies 2, 4 place.

The purpose of such an arrangement is that for the gear adjustment, an adjustment of the swash body ring 16 from a first end position, wherein the ring plane is penetrated perpendicularly from the axis of the input shaft 2, to a second end position with maximum inclination of the swash body ring 16th is sufficient. These two end positions can be defined by a respective stop element. As a result, for example, a controller can act on the actuating arm 8, for example a speed-dependent control element.

As can also be seen from FIG. 3, the ring 16 has a C-shaped cross-section, which is interrupted on its end side facing the output side. A second ring 21, which is rotationally decoupled relative to the first ring 16 by bearing means (not shown), in particular roller bearings, is incorporated therein.

By a non-illustrated positive engagement between the second ring 21 and the housing or chassis of the transmission 1, the second ring 21 is prevented from following the rotation of the first ring 16, while due to the bearing means between the two rings 16, 21, the wobbling movement of the first ring 16 is taken over. The positive engagement can be effected, for example, by an extension of the second ring 21 protruding through the opening of the cross-sectionally C-shaped slot 16, which engages in a (curved) guide track of the transmission housing or chassis and is guided therein.

The second ring 21 need not be encompassed by the first ring 16; However, a storage, especially Qälzlagerung between the two is essential to allow a smooth relative rotation. The second ring 21 thus performs with a corresponding adjustment of the actuating arm 8 a pure wobbling motion, which is largely free of rotational movements. This tumbling movement corresponds to oscillatory movements of individual regions or points of the ring 21 about the center thereof, the main component of these oscillatory movements being an axial direction, ie a direction parallel to the input shaft 2. This axial movement is primarily for the transmission function of interest and is therefore tapped at different points of the ring 21.

The Abgreifeleinrichtungen 22 provided for this purpose are constructed in the illustrated embodiment in the manner of joints. They each include an approximately spherical head 23, which engages in a respective recess 24 of the ring 21.

The recesses 24 and tapping points are present in an even number, and always two recesses 24 are each pairwise associated with each other and straight offset by 180 ° to each other, so arranged diametrically to each other. In the example shown there are a total of six recesses 24, which are each offset by 60 ° from each other; these can be grouped into three mutually offset by 60 ° pairs of diametrically opposed recesses 24. The recesses 24 may be formed in the manner of the pans of ball joints, so hollow spherical. They each have an opening in the region of the circumferential slot in the cross-sectionally C-shaped ring 16, so that about bolt-shaped projections 25 on the ball heads 23 through the slot in the ring 16 of the rotational movement can freely escape to the outside, in one of the Input shaft 2 approximately parallel direction. In the illustrated embodiment, one end 26 of a chain 27 is articulated to each picking device 22 in each case. These chains 27 are deflected by various rollers 28, 29 in the output-side region of the transmission 1 5. In this case, each chain end 26 in the illustrated embodiment, two deflection rollers 28, 29 assigned. These are each mounted between two mutually parallel, approximately in the direction of the output shaft 3 extending rods 30 of a chassis 31; These rods are eg. At its two ends by a respective ring 32, 33 of the chassis 31 connected to each other io. For installation in the transmission housing, this chassis 31 may, for example, be provided with one or more fastening plates 34, possibly with fastening bores 35.

The chassis 31 surrounds along the output shaft 3, in the case illustrated in FIG. 15, up to the adjusting device 6-8. As can be seen further in FIG. 3, a total of six rotationally symmetrical annular rotary freewheels 36 are seated on the output shaft 3. Clamping body freewheels can be provided, wherein clamping bodies 39 are provided between two concentric rings 37, 38 each after the rotational or force direction to be transmitted between the rings or not and thereby selectively allow a rotation transmission or the two rings 37, 38 of the freewheel 36 decouple from each other. All six freewheels 36 are fixed in the same direction of rotation on the output shaft 3, so that all allow a power transmission in a direction of rotation 5 of the output shaft 3, but not in the opposite direction of rotation.

While the respective inner ring 37 is non-rotatably connected to the output shaft 3, the respective outer ring 38 of a freewheel 36 has a shape 0 with a U-shaped cross section, wherein at both end faces of an approximately cylindrical middle portion 40 depending a flat disc 41 with annular base is located; the parts 40, 41 are integral be connected to each other, for example, be generated from a common rotational body by machining. The clear distance between the two annular discs 41 of a freewheel 36 is equal to or preferably slightly larger than the maximum width of a chain 27, so that the chain links find space between the annular discs 41 of a freewheel 36. For the rotationally fixed coupling of one or more chain links with the outer ring 38 of a freewheel 36 whose annular disks 41 are provided with recesses, in particular holes 42. Since in each case a bore 42 in an annular disc 41 of a freewheel 36 is aligned with a bore 42 in the other annular disc 41, axially parallel pins can pass and anchor therein. These pins can also pass through aligned holes in the chain links of the chain 27 and therefore provide a positive and non-positive connection between a chain 27 and the outer ring 38 of a freewheel 36th

Each freewheel is assigned a tapping device 22 via a chain end 26. The chain 27 extends between these elements in the illustrated embodiment via two pulleys 28, 29. Of these each sit a pulley 28 in the region of the front chassis ring 32, while the other pulley 29 is further shifted to the output side and approximately on the Height of the associated freewheel 36 is located. Preferably, the chain 27 rotates around the first guide roller 28 at its radially inner side, the second guide roller 29 at its radially outer side, and from there finally approximately tangential to the relevant freewheel 36, where it is anchored. In order to allow the tangential course, the rods 30 of the chassis 31 can extend obliquely to the output shaft 3.

Furthermore, the axes of rotation of the rear guide rollers 29 are not parallel to the axes of rotation of the freewheels 36; the chain 27 must therefore bend on these elements 29, 36 in different directions. For this purpose, it is possible in the chain 27 between these elements 29, 36 a universal joint insert, which allows a change in the orientation of the chain links.

However, the chains 27 do not end at the freewheels 36, which are associated with their respective end 26; Rather, they nestle partially to the outer periphery of a freewheel 36 - where they are rotatably coupled via the pins, not shown, each with a freewheel 36 - and finally leave this in the tangential direction. Preferably, the six freewheels 36 are associated in consecutive order adjacent to successive tapping devices 22, that is, the tapping devices 22 and tapping points of two adjacent freewheels 36 are offset from each other by 60 °. This means that in each case two other freewheels 36 are inserted between two freewheels 36, which are associated with diametrically arranged tapping devices 22, ie offset by 180 ° from one another. Approximately on a median plane between two freewheels 36 spaced from each other by twice the width of a freewheel 36, a further deflecting roller is mounted, which is omitted in the drawing for reasons of clarity, as well as areas of the chains 27 beyond the deflecting rollers 28. The axis of rotation Such deflection roller is preferably within the relevant median plane.

Each of these two chains 27, whose ends 26 are coupled to diametrically arranged tapping devices 22, are guided beyond the associated freewheel 36 of this to a common, further pulley, enclose them partially and are connected to each other, preferably by a normal chain link. This is possible because the two interconnected chain runs their associated freewheels 36 in the same direction of rotation and therefore leave these freewheels in the same direction. Strictly speaking, therefore, the two thus interconnected ends 26 are nothing more than the two ends 26 of the same, common chain 27. In the illustrated embodiment there are therefore 5 in total only three chains 27, each with two ends 26, which are diametrically opposed to each other lying tapping devices 22 out and connected there.

A common chain 27 i o formed by connecting two chain ends 26 encloses a further deflection roller at a center angle of approximately 180 ° or approximately along half the circumference and is thereby deflected by approximately 180 °. As a result, the warp strands on both sides of the further idler roll move anticyclically along the respective warp web, i.e., as one moves toward the further idler, the other moves away from it. Due to the same direction wrapping the respective freewheels 36 and the same direction arrangement thereof will therefore be decoupled during each half cycle of the oscillating chain movement each one of the freewheels involved 36, while on the other freewheel 36, the output shaft 3 is driven, if not just 20 a chain 27th the other two phases move faster and have a driving effect.

Each two attached to each tapping 22 connected chain ends 26 chain 27 is taut around the last or further pulley

25 tensioned, so that the chain 27 is always under tension and therefore no alternating load occurs, even if the direction of movement of the chain 27 changes. This is ensured by the anticyclical movements of both chain ends 26. If necessary, an additional voltage can be generated, for example. By a deflection roller, in particular the

30 last mentioned, is provided with a clamping mechanism. This may be, for example, a very hard spring element, which endeavors to tension the rotating or bearing axis of the relevant deflection roller, in particular, in a direction opposite to the direction of this pulley chain strands 26 approximately opposite direction. In addition to such, automatic tensioning device, it is also conceivable to provide a device for manual retightening, which can be tightened at each maintenance.

The separate from the other phases inference coupling per two chain ends 26 to a common chain 27 causes each of the three chains 27 can be individually and individually under (pre-) voltage maintained. This is i.a. This is possible because a separate further deflection roller is provided for each phase. So that these phase-wise return pulleys do not obstruct each other, it can be provided that they are distributed over the circumference of the transmission 1, in particular each offset by a center angle of about 120 ° relative to the output shaft 3 against each other. Due to the phase-separated conclusions of each chain is always under optimal tension, which on the one hand maximizes the efficiency and on the other hand also increases the operating time. For the sake of completeness, it should be noted that in this as well as in any other embodiment, the number of existing phases or chains 27 or pairs of tapping devices 22 is not limited to three. For example, there could also be only two such phases or pairs of tapping devices 22 or their four or a different number.

4, a modified embodiment of a continuously variable transmission 1 'can be seen. This differs from the transmission embodiment 1 described above only with respect to the wobble body ring 16 'and the tapping means 22', but otherwise may be identical to the previously described embodiment. In particular, three pairs of tapping devices 22 'can also be present here, but a different number would also be possible. In the gear 1 'serving as a wobble body ring 16' preferably has an approximately planar shape with a rectangular ring cross-section. An additional, in contrast, rotatable ring does not exist in this embodiment; Rather, the not only tumbling, but also about the input shaft 2 rotating ring 16 'itself be used to pick up the axial movement.

For this purpose, there are on the side facing away from the output shaft 3 of the wobble body or ring 16 ', a guide means 43 for six in the example shown to the input shaft 2 parallel bolts 44. The bolts 44 are arranged at equal radial distances from the input shaft 2, respectively offset by 60 °. The guide device comprises two annular disks 45, 46 which surround the input shaft 2 and each have six axially parallel recesses 47, 48, which are likewise offset from each other by 60 °, similar to the cartridge drum of a drum revolver. The two annular discs 45, 46 are fixed to the housing or on a chassis part of the transmission 1 'and arranged such that two recesses 47, 48 of both annular discs 45, 46 are aligned with each other and are penetrated by a common pin 44.

The bolts 44 are slidably received in these recesses 47, 48; Preferably, the recesses 47, 48 therefore have approximately to the cross section of a bolt 44 congruent cross-sections, for example. Each circular or polygonal cross-sections.

The wobble body or ring 16 'facing ends 49 of the bolt 44 are rounded, in particular formed approximately dome-shaped, and are used for direct contact with the wobble body or ring 16'. Their task is to scan or tap the axial component of their tumbling motion, however, are prevented by the guide means 43 from participating in its rotational movement.

In the region between the two guide washers 45, 46, each bolt 44 each has a radially outwardly facing extension 50 with a connection for a chain end 26, in particular in the form of an eye 51 for suspending the first chain link or a suitable transition piece 52nd By the tension of the chain 27 suspended therein, the bolts 44 are pressed firmly against the wobble body or ring 16 '. Due to the wobbling motion of the wobble body or ring 16 ', the chain 27 is impressed with a harmonic oscillation movement, with its two ends 26 executing anticyclical path movements. The chain movement is transmitted to the output shaft 3 by means of two freewheels 36 as in the previous embodiment. In this case, the amplitude of the harmonic oscillation movement of the chain 27 and thus the gear ratio are varied in accordance with the inclination of the wobble body or ring 16 'set on the adjusting arm 8.

4, a lever could be coupled to each bolt 44 instead of an approximately radial extension 50, which is mounted on the housing or chassis of the transmission 1 ", and on the other hand also the respective chain end 26 is attached There are both the possibility of a one-armed lever, the chain end 26 is attached to the same arm as the bolt 44, as well as the possibility of a two-armed lever, the chain end 26 and the bolt 44 is coupled to different lever arms This arrangement can also be further developed such that such a lever is not coupled to a bolt 44, but has, for example, a dome-shaped element, preferably in the region of its ends, for the purpose of direct contact with the wobble body 16 ', so that the bolts 44 and guides 45, 46 could be dispensed with.

In all the embodiments described with reference to FIG. 4, a dome-shaped portion at the front or free pin or lever end need not rest directly against the wobble body 16 'or a ring rotatably coupled thereto, but may be provided, for example, with a shoe a preferably flat front surface for abutment against a revolving path of the wobble body 16 'or a rotatably coupled thereto ring and a hollow spherical recess on its back for partially receiving the dome-shaped portion of a bolt, lever od. The like. This results on the one hand a ball joint-like Function, ie a pivoting of the shoe in any direction in space, and also a large contact surface, on the one hand between the swash body 16 'or a rotatably coupled ring and the shoe, and on the other hand between the latter and the dome-shaped portion of a bolt, lever od. Like. By the big plant area, the pressure is considerably reduced and thus the wear is reduced. On the other hand, such a shoe can also be made of a special material with friction and / or wear-reducing properties.

A different embodiment of a transmission 1 "according to the invention is shown in Fig. 5. This is a further modification of the second embodiment As here, the additional ring 21 can also be dispensed with here, and the axial component of the tumbling motion can be direct However, in contrast to the second embodiment, the tapping does not take place on the side of the ring 16 facing away from the output shaft 3, as can be seen as a flat annular disc with an approximately rectangular annular cross section ', but at the output shaft 3 side facing. This transmission embodiment also uses this pin 44 "with approximately dome-shaped ends 49" to rest on the wobble body or ring 16 '. These bolts 44 "are guided in a guide device 43"; However, this has only one guide-ring disc 45 ", which may be identical to the annular disc 45 of the second example, and in the recesses 47" each one of the six bolts 44 "is guided linearly movable.

However, no chain is coupled to these bolts 44. Rather, a tube 53 adjoins each recess 47 "directly on the driven-side end face of the guide ring disk 33, preferably with approximately the same cross-section as the relevant recess 46". Instead of tubes 53 could - at least in sections - and other lines or, for example, channels in a solid or block with a corresponding - constant - serve inner diameter.

Each of these tubes 53 leads to exactly one freewheel 36 and surrounds it along a certain area and then dissolves again from this. The tubes 53 of two diametrically opposed recesses 46 "are connected to each other beyond the respective freewheels, thus forming a single, common tube 53rd

Within the tube 53 balls 54 are arranged, whose diameter corresponds approximately to the inner diameter of the tube 53 or is minimally smaller. The balls 54 are made of a pressure-resistant material, preferably metal. The balls 54 are in the tube 53 close to each other, therefore, can transmit movements by the transmission of pressure. These are, so to speak, a pendant to a chain, with the individual chain links now corresponding to the balls 54. However, while the links of a chain communicate their motion through the tension within the chain, the balls 54 do so by pressure, unlike hydraulics, however, without compression and thus without losses. To pass on the movement of the balls 54 within the tubes 53 to the freewheels 36 triggered by the wobble body or ring 16 ', the tubes 53 can each extend in the region of a freewheel 36 along their wall facing the freewheel 36 in question in the longitudinal direction of the tube Slit have. Through this slot can be made a connection of one or more balls 54 with the relevant freewheel 36, in particular with its outer jacket. For this purpose, a ball 54 selected therefor, for example, can have a through-bore, preferably through its center. It is then inserted a pin and possibly anchored, for example. Welded, which then extends through the slot in question and is also anchored to a ring of the freewheel 36, for example, also welded. If the respective ball 54 oscillates back and forth inside the tube 53, it will transmit this movement to a ring of the freewheel 36, and this will in turn select a half period from this movement depending on the direction and transmit it to the output shaft 3, if not one Freewheel 36 another phase causes a faster rotation of the output shaft 3.

In this design, it should be ensured that the tubes 53 always take on their bends a sufficiently large bending radius, so that the balls 54 can not get stuck in it. If necessary, this embodiment can be further developed by inserting one Abtandselement between each two balls 54. This could for example be limited by two hollow spherical end faces similar to a double concave lens, wherein the radius of the hollow spherical surfaces should correspond to the radius of the balls in order to increase the pressure surfaces between the balls 54. The outer diameter of such spacers may be smaller than the diameter of a ball 54, or be just as large. In this case, however, the lateral surface of such a Spacer element, for example, be designed spherical or barrel-shaped, to prevent jamming within the tube 53. In this case, even the diameter of the balls 54 could be smaller than the inner diameter of the tube 53, so that the balls 54 are guided only by the spacer elements. By filling the tube 53 with a lubricant, the friction between tube 53, balls 54 and spacers can be minimized.

Also in this embodiment can be provided between a dome-shaped portion at the front and free end of a bolt 44 "or on another, on the wobble body 16 'or on the rotatable coupled thereto coupled ring part on the one hand and the latter on the other hand, a shoe, preferably a just front to rest on a rotating path of the wobble body 16 'or a rotatably coupled thereto ring and a hollow spherical recess on its back for partially receiving the dome-shaped portion of the bolt 44' or on another, on the wobble body 16 'or on the thus rotatable coupled ring adjacent part.

***

Claims

claims

1. Continuously variable transmission (1) comprising

a) at least one rotatable around its longitudinal axis, drivable shaft body (2)

b) and arranged thereon and rotating with this tumbling body (16,21) with at least one orbiting path which is adjustable relative to the shaft body (2) in its inclination so that the plane spanned by its orbiting main plane of the shaft body (2) is not vertically interspersed,

c) and an even number of Abgreifeleinrichtungen (22) for picking up substantially the axial component of the tumbling motion of the wobble body (16,21) on the circumferential path in different phases, the tapping devices (22) with respect to the longitudinal axis of the shaft body (2) in pairs are arranged diametrically opposite one another,

d) and a corresponding number of rotational freewheels (36) which are neither displaceable nor pivotable about another axis than their own axis of rotation, and the input side preferably via a coupling device (26,27; 52,53), each with a tapping device (22) and the output side are each coupled to a common output or output shaft (3);

characterized in that in each case two, diametrically opposed tapping devices (22) or coupling devices (26,27; 52,53) beyond the respective rotational freewheels (36) are coupled together by a return that they due to the inference to anti-cyclic path movements are forced while not diametrically arranged Tapping devices (22) and / or coupling devices (26,27; 53,54) are not coupled to each other beyond the respective rotational freewheels (36).

2. Continuously variable transmission according to claim 1, characterized by at least one to the shaft body (2) parallel and / or coaxial output or output shaft (3).

3. Continuously variable transmission according to one of the preceding claims, characterized by an output or output shaft (3) on which a plurality of rotational freewheels (36) are arranged, in particular with one of its terminals are rotatably connected.

4. Continuously variable transmission according to one of the preceding claims, characterized in that the rotational freewheels (36) relative to the transmission chassis or housing are stationary.

5. Continuously variable transmission according to one of the preceding claims, characterized in that the axes of rotation of all rotational freewheels (36) extend parallel to each other.

6. Continuously variable transmission according to one of the preceding claims, characterized in that the axes of rotation of all rotational freewheels (36) are aligned.

7. Continuously variable transmission according to one of the preceding claims, characterized in that the rotational freewheels (36) have two mutually concentric rotation body, in particular two mutually concentric rings (37,38).

8. Continuously variable transmission according to one of the preceding claims, characterized in that the rotational freewheels (36) are designed as sprag freewheels, in particular with clamping bodies (39) between two mutually concentric rings (37,38).

Continuously variable transmission according to one of the preceding claims, characterized in that all coupling elements of a coupling device (26,27; 53,54) between the swash body (16,21) and the relevant freewheel (36) are each loaded simultaneously on train or on pressure.

Continuously variable transmission according to one of the preceding claims, characterized in that all coupling elements of a coupling device (26,27; 53,54) between the swash body (16,21) and the relevant freewheel (36) are always loaded on train or always on pressure.

Continuously variable transmission according to one of the preceding claims, characterized in that on one or more freewheels (36) in each case one with a ring (16,21) or ring segment of the wobble body coupled pulling and / or pushing means (26,27; 53,54) connected.

Continuously variable transmission according to one of the preceding claims, characterized in that a coupling device comprises a traction means, in particular a chain (27) whose chain links are always loaded to train.

13. Continuously variable transmission according to one of claims 10 to 12, characterized in that the traction means is a chain (27) having a plurality of movably coupled members.

14. Continuously variable transmission according to claim 13, characterized by at least one respective chain (27) deflecting means, in particular at least one guide roller (28,29).

15. A continuously variable transmission according to claim 14, characterized in that the chain deflecting means (28, 29) divides the relevant chain (27) into two strands, one of which is within a longitudinal direction of the shaft body (2) approximately radial plane (s). extends to the wobble body (16,21) and is connected to a local ring or ring segment, while the second strand extends to a freewheel (36) or a wheel coupled thereto and is engaged therewith.

16. Continuously variable transmission according to claim 14 or 15, characterized in that in the chain (27), preferably between two chain deflection means (28,29) is arranged a universal joint.

17. A continuously variable transmission according to claim 16, characterized in that the distance of the chain universal joint to the connection point or to the tapping point on the ring (16,21) or ring segment is greater than the maximum axial stroke of the wobble body (16,21) ,

18. Continuously variable transmission according to claim 17, characterized in that on the freewheel (36) or on a wheel coupled therewith a row of teeth is arranged, whereby a chain (27) meshes.

19. A continuously variable transmission according to any one of claims 12 to 18, characterized in that one end (26) of at least one chain (27) is connected to a freewheel (36) or a wheel coupled thereto, preferably hingedly attached to a peripheral point, in particular one or more perforated annular discs (41) of a freewheel (36) by means of the holes (42) by cross-pins is attached.

20. Continuously variable transmission according to one of claims 12 to 19, characterized in that at least one chain (27) is biased by a clamping means, in particular by a spring or a spring-damper unit.

21. Continuously variable transmission according to one of claims 12 to 20, characterized in that the inference is formed by the union of two chain-shaped coupling devices (26), in particular to a common chain (27).

22, continuously variable transmission according to one of claims 12 to 21, characterized in that at least one coupling means a guide track, in particular a guide tube (53), channel od. Like. For abutting mechanical pressure body, in particular balls (54), which always charged to pressure.

23. A continuously variable transmission according to claim 22, characterized in that the guide track, tube (53), channel od. Like. Of a coupling device for mechanical pressure body, in particular balls (54), undergoes at least one deflection.

24. Continuously variable transmission according to one of claims 22 or 23, characterized in that the return path is formed by the union of two guide tracks (53) for mechanical pressure body (54).

25. A continuously variable transmission according to one of the preceding claims, characterized by two pairs of approximately diametrically opposed pushing and / or pulling means (26,27; 53,54), which pairs are offset by an angle of about 90 ° to each other, or by three pairs of diametrically arranged shear and / or Traction means (26,27; 53,54), which pairs are offset by an angle of about 60 ° to each other.

26. Continuously variable transmission according to one of the preceding claims, characterized in that on a wobble body (16) at least one ring (21) or ring segment is arranged, which (-s) of the same relative to the wobble body (16) along a circumferential path is rotatably mounted ,

27. Continuously variable transmission according to one of the preceding claims, characterized in that the wobble body (16) is limited by curved surfaces, in particular by concave or convex surfaces.

28. Continuously variable transmission according to claim 27, characterized in that the wobble body (16) has a spherical surface.

29. Continuously variable transmission according to one of the preceding claims, characterized in that the wobble body (16) is hollow.

30. Continuously variable transmission according to one of the preceding claims, characterized in that the pivot point of the wobble body (16) is displaced eccentrically to the axis of rotation of the shaft body (2).

31. Continuously variable transmission according to one of the preceding claims, characterized in that the pivot point of the wobble body (16) has a distance from the axis of rotation of the shaft body (2), which corresponds approximately to the radius of a circumferential ring (16) or greater than that radius ,

32. Continuously variable transmission according to one of the preceding claims, characterized in that the pivot point of the wobble body (16) is movably mounted or guided.

33. Continuously variable transmission according to one of the preceding claims, characterized in that the pivot point of the wobble body (16) on a movable linkage (15) is arranged.

34. Continuously variable transmission according to one of the preceding claims, characterized in that at least one of a tumbling body

(16) rotatably mounted ring (21) is guided non-rotatably by means of a guide relative to the transmission chassis or housing.

35. Continuously variable transmission according to claim 34, characterized in that the ring guide is within one to the longitudinal axis of the

Shaft body (2) parallel plane, within the two connection points or tapping points of the ring concerned (16,21) are located.

36. Continuously variable transmission according to one of the preceding claims, characterized in that different thrust and / or traction means pairs are arranged on different, mutually rotatable rings (21) or ring segments of the wobble body (16).

37. Continuously variable transmission according to one of the preceding claims, characterized in that a pulling and / or pushing means via a two-dimensionally acting joint (23,24) is connected to a ring (21) to the longitudinal movement of the pulling and / or pushing means (16,21; 53,54) from the tumbling motion of the

Isolate wobble body (16).

38. Continuously variable transmission according to claim 37, characterized in that the two joint axes intersect or pass close to each other, in particular run through a common part.

39. Continuously variable transmission according to claim 37 or 38, characterized in that the joint between a pulling and / or pushing means (26,27; 53,54) and a ring (16,21) has a pressure-loaded part, which is preferably has a spherical or spherical segmental shape.

40. Continuously variable transmission according to claim 39, characterized in that the pressure-loaded part relative to the pulling and / or pushing means and / or relative to the ring (16,21) is movable.