WO2011160621A2

WO2011160621A2 - Conical friction ring gear

Info

Publication number: WO2011160621A2
Application number: PCT/DE2011/001360
Authority: WO
Inventors: Ulrich Rohs; Christoph DRÄGER; Werner Brandwitte
Original assignee: Ulrich Rohs; Draeger Christoph; Werner Brandwitte
Priority date: 2010-06-24
Filing date: 2011-06-24
Publication date: 2011-12-29
Also published as: WO2011160621A3; JP2013529759A; CN102959278A; CN102959278B; DE112011102103A5

Abstract

In order to provide a conical friction ring gear having two friction cones which are spaced apart from each other by a gap and have a friction ring which revolves around one of the two friction cones through the gap and is arranged so as to be shiftable along the gap via an adjustment bridge, which can be freely shifted along an adjustment bridge path, wherein the adjustment bridge is mounted via an axial guide device and has a device for adjusting a friction ring angle, which conical friction ring gear has a high degree of operational reliability and reliably operates in particular in the event of failure of the means of activating the tilting movement of the guide device, the adjustment device is activated by means of a sliding rail which can be positioned in parallel.

Description

bevel friction ring gearing

[01] The invention relates to a conical friction ring transmission with two friction cones spaced apart from each other by a gap, which is arranged so as to be displaceable over a friction ring which passes through the gap around one of the two friction cones and is displaceable along the gap via an adjustment bridge freely displaceable along an adjustment bridge path wherein the adjusting bridge is supported on the one hand via an axial guide device which defines the Verstellbrückenweg and tiltable, and wherein the adjusting bridge on the other hand is mounted on an axial guide means and having means for adjusting a friction ring. [02] Such conical friction ring transmissions are known from the prior art, as described, for example, in EP 0 878 641 A1, EP 0 980 993 A2 or WO 2006/012892 A2, wherein, on the one hand, the adjustment bridge is housed in a cage or by a one-sided one Guide rod can be held as an axial guide means and articulated about this, to effect a tilting of the friction ring, and on the other hand, the Verstellbrücke in a cage, held by two parallel sides of the two friction cone arranged axes, which are connected by two connecting rods, as an axial guide device and is axially displaceable along these axes and has an adjusting device, via which an adjustment angle of the friction ring can be influenced.

In the present context, the term "adjustment bridge" designates an arrangement that can be displaced with the friction ring, but does not rotate with the friction ring that the adjustment bridge can in particular be followed by a displacement of the friction ring caused by other means, such as occurs when the friction ring is adjusted in its angle. [04] For the purposes of the present invention, the term "friction ring" is understood to mean a device by means of which a contact is made between the two friction cones, so that forces, in particular torques, can be transmitted from one friction cone to the other friction cone. The corresponding friction cone are arranged axially parallel to each other in the opposite direction, so that the tip of a cone is on the side of the stump of the other cone and vice versa. In addition, both friction cones preferably have the have the same cone angle, but may have different radii, in order to be able to choose a basic ratio of the conical-friction ring gear in this way.

[05] It is understood that a friction ring in another embodiment may also be of the form in which it is arranged only in the gap between the two friction cones and none of the friction cone surrounds or in which he encompasses both friction cone, wherein in this Embodiments for the friction ring and a modified storage would have to be provided if necessary.

[06] The term "axial guide device" means any device which is suitable for supporting the adjustment bridge in the friction-ring transmission such that the adjustment bridge can be displaced axially along the axial friction-cone axes in the region of an adjustment path and thus also axially along the gap Otherwise, the above-mentioned cage acts as such an axial guide device, as a result of which the axial guide device limits the degrees of freedom of the bridge part.

[07] It is understood that the adjustment path of the adjustment bridge can also have further directional components, as long as the adjustment bridge can follow the movement of the friction ring in the gap between the two friction cones. Preferably or possibly, a part of the axial guide device is designed such that this part only allows rotation about the displacement in the plane perpendicular to the adjustment, which can be easily realized for example by a circular axis. In this case, it may be sufficient if the adjusting bridge is sufficiently fixed with respect to the rotation or with respect to a movement in this plane, for example by the friction ring itself. Likewise, here another part of the guide means, for example by a tongue and groove guide, are used, by which the rotation about the adjustment can be prevented. [08] If the friction ring is moved at an angle with respect to the gap located between the friction cones from a neutral orientation, which can be effected and controlled by the Verstellbrücke, so he moves of itself along the gap until it returns to its neutral orientation is adjusted. Here, the direction of this displacement is determined by the direction of rotation of the friction cone and by the direction of the adjustment angle, starting from the neutral orientation. The displacement speed depends accordingly on the size of the adjustment angle and the speed of the friction cone. It is understood that the adjustment does not necessarily have to be defined by a pure rotational movement, it In this case, depending on the specific embodiment, more complex movement sequences can also be provided. Preferably, however, the friction cone rotates about an axis of rotation when it is adjusted by the adjustment angle, wherein this axis of rotation does not necessarily have to lie in a plane spanned by the Reibkegelachsen plane. However, it is advantageous for the sake of a simple structural design, if the axis of rotation has at least one component which is parallel or real parallel to a plane spanned by the Reibkegel axis sen.

[09] The advantage of this embodiment is that the energy required for the displacement is provided directly from the rotation of the friction cone and that extremely high adjustment speeds can be achieved. In experiments it has been found that in a conical friction ring gear with friction cones between 2 cm and 20 cm radius and a cone height of 40 cm can easily succeed to shift the friction ring within seven revolutions from one end of the gap to the other end.

In the present context, the axial guide device is formed, inter alia, tiltable. This can be realized, for example, that it is suitably stored or provided by thin-walled areas or the like an articulated connection that allows tilting. This tilting causes a corresponding movement of the adjustment bridge, whereby then the friction ring is adjusted in its angle. In this respect, by tilting the axial guide means of the adjustment of the friction ring can be influenced accordingly, so that in this way the displacement of the friction ring and thus the transmission ratio can be defined.

[1 1] Ultimately, tilting can be caused in any suitable form. Preferably, this is done by a corresponding actuator, as well known from the above-mentioned prior art.

It is an object of the present invention to provide a generic conical friction ring, which has a high reliability and especially in case of failure of the control for the tilting movement of the guide device provides reliability.

As a solution, a conical-friction ring transmission is proposed with two friction cones spaced apart from each other by a gap, which is arranged so as to be displaceable over a friction ring that passes through the gap around one of the two friction cones and is displaceable along the gap via an adjustment bridge that is freely displaceable along an adjustment bridge path. wherein the adjustment bridge is mounted via an axial guide device and wherein the conical friction ring gear characterized in that an arranged on the adjusting Verj ei device is controlled by means of a parallel positionable slide rail.

The control by means of the parallel positionable slide advantageously allows exact control of the adjusting device, wherein the term "parallel" expresses that the slide interacts substantially translationally, ie without rotational component, movable with the adjusting device and on a housing or Frame of the transmission is arranged.

In this case, in particular, the direction of movement of the slide rail at a right angle to a direction of displacement of the verse part bridge, the Verstellbrückenweg be aligned, whereby the exact driving of the adjusting device is made particularly advantageous. However, it is sufficient if the direction of movement of the slide in an angle, that is not parallel, extends to the displacement direction of the adjusting bridge in order to be able to control the adjustment arranged on the adjustment in a suitable manner on the slide. The duller this angle is, the more accurate such an actuation can be, so that this angle should be at least 45 °.

[16] Due to its parallel positionability, the slide rail can also be guided, for example, on at least one straight-line rail guide, in particular on two parallel rail guides.

[17] Furthermore, in the present context, the adjusting device is arranged on the adjusting bridge and accordingly shifts together with the friction ring. In that regard, the adjustment angle and the neutral orientation of the friction ring are determined by the displacing with the friction ring adjusting device. It is understood that the adjusting device can also be controlled via subassemblies which are not associated with it, for example via tiltable slide rails, which are already known from the prior art, or else via the slide rails which can be positioned in parallel. The latter cause, as already explained above, in deviation from the tiltable slides an extremely precise control, which can be done in particular regardless of the position of the friction ring with the same precession.

Preferably, the parallel positionable slide is driven by a spindle drive, whereby an extremely precise drive and thus a precise control of the adjusting device is made possible. However, this advantage also results if, instead of a parallel positionable slide rail, a tiltable slide rail via a spindle drive is driven. In this respect, such a drive has proven to be advantageous regardless of the other features of the present invention.

Accordingly, in order to achieve the object of the invention as an alternative or cumulative to the above features, a conical friction ring transmission is proposed with two mutually spaced by a gap friction cones, which rotates about a friction ring which passes through the gap to one of the two friction cone and along the gap via a freely displaceable along a Verstellbrückenweges adjustable bridge is arranged to be displaceable, wherein the Verstellbrücke is mounted on an axial guide means and wherein the conical friction ring is characterized in that an adjusting device arranged on the Verstellbrücke is driven by a spindle drive.

[20] In addition to the above-described embodiment for the exact control of the adjusting device, the spindle drive advantageously offers the possibility of driving the adjusting device more precisely or of positioning the friction ring more precisely in the conical-friction-ring transmission via the adjusting device. In particular, it is possible in this case for the spindle drive to be designed either directly on the adjusting device or directly on the slide rail explained above.

While for most requirements a simple helical gear can be used as a spindle drive, it is also possible that the spindle drive comprises a ball screw or a roller screw, which advantageously a very high accuracy for the control or for the drive of the adjusting device can be achieved can.

In this respect, ensures a stationary drive shaft which drives the adjusting device arranged on the adjustment, a reliable and precise drive, and this also independent of the other features of the present invention,

Accordingly, alternatively or cumulatively to the above features a conical friction ring transmission is proposed with two friction cones spaced apart from each other by a gap, which rotates about one of the two friction cones through a friction ring which passes through the gap and along the gap over a free axis Verstellbrückenweges displaceable Verstellbrücke is arranged displaceably, wherein the Verstellbrücke is mounted on an axial guide means and wherein the conical friction ring is characterized in that an adjusting arranged on the adjusting Verstelleinrichtung is driven by a stationary drive shaft which interacts with a corresponding with the adjusting device output on the Verstellbrücke , For the design of a drive shaft, it is also advantageous if the drive shaft is a profiled shaft or a rail, whereby the drive shaft can be brought into positive engagement with the hereby interacting subsequent components of the output and this form-fitting naturally, in particular against friction, the Operational safety increased. For example, the drive shaft deviating from a round cross section also have a rectangular or a polygonal cross section.

[25] The term "stationary" is hereby used synonymously with the term "housing-fixed", wherein the drive shaft along the Verstellbrückenweges is not arranged to be displaced. A "stationary" component thus does not shift its position relative to a housing of the conical-friction ring transmission, although expressly a rotational degree of freedom of the component "stationary" is to be retained. A rotatably mounted in the housing of Kegelreibringgetriebes spindle but also in the housing of Kegelreibringgetriebes friction cone of Kegelreibringgetriebes are therefore "stationary", this definition does not apply to the displaceable friction ring and the corresponding following Verstellbrücke and carried by this adjusting device.

The parallel positionable slides are excellent because of their immutability in terms of the angle to the Verstellbrückenweg, as this also represent the above-described spindle drive or the above-described drive shaft, so that here also controls the arranged on the Verstellbrücke adjustment regardless of the axial position of the adjustment can be done on their Verstellbrückenweg. In this respect, the above-mentioned solutions based on the common inventive basic idea to control the drive arranged on the adjusting Verstelleinrichtung by a respect to the Verstellbrückenweg independent mechanical drive or driven, which is independent by an angle to the Verstellbrückenweg mechanical transmission part for the drive or for the Control of the adjusting device can be achieved.

Such independence can also be realized by a motor which is arranged on the adjusting device, which surprisingly leads to a similarly reliable implementation. Accordingly, alternatively or cumulatively to the above-mentioned features and to the solution of the input standing task, a conical friction ring transmission with two mutually spaced by a gap friction cones proposed by a friction ring, which passes through the gap to one of the two Frictional cone rotates and along the gap over a freely along a Verstellbrücken away displaceable Verstellbrücke is arranged displaceably, wherein the Verstellbrücke is mounted on an axial guide means and wherein the conical friction ring characterized in that an arranged on the Verstellbrücke adjustment means of a motor on the adjusting device is arranged, is driven. As a result, since only very few assemblies are used and thus a very low susceptibility to failure against, a highly reliable conical friction ring gear can be provided.

[28] In the present context, the term refers to any energy-converting device with which mechanical energy can be provided as a drive for the adjusting device. As motors, in particular electric motors, but also hydraulic or pneumatic motors, as well as linear drives, or electromagnets or piezoelectric drives in question, in particular, the number of mechanical assemblies in the use of linear motors can be reduced to a minimum. Also, the electric motors can be designed as stepper motors.

By means of a motor arranged in this way, the complexity but also the installation space of the conical-friction ring transmission is advantageously reduced, since particularly few assemblies are required for driving or for driving the adjusting device. This advantage results from the possibility of directly controlling the adjusting device and consequently reduces the susceptibility to error of the entire assembly.

[30] For the axial guide device of the conical-friction ring transmission, it is advantageous if it is arranged stationarily with respect to the cone axes. The stationarily arranged guide means thus provides high reliability, but can also contribute to an increase in the stability or rigidity and thus for an accurate positioning of the adjustment. It is possible, as in the guide for the slide also that the guide device has at least one or at least two parallel guided sliding guides. In this context, the term "stationary" also refers to a housing-fixed coordinate system when the cone axes are arranged fixed to the housing.

An advantageous operationally reliable angle adjustment can also be achieved in a conical friction gear in an advantageous embodiment in that the adjusting bridge has at least two guide points for the friction ring and at least one of the two guide points on the adjusting device is adjustable. The two guide points In this case, for example, in each case two guide wheels revolving on both sides of the friction ring, for example a guide wheel arranged in the ring plane, which surrounds the friction ring with two flanks, or for example one or two corresponding scenes or two corresponding guide surfaces. If both guide points are adjustable depending on the specific configuration of the conical-friction ring transmission, an opposite adjustment of both guide points offers further advantages, since in this case stresses can be avoided.

It is understood that in the specific embodiment of a guide point, which mathematically has no longitudinal extent, a real training contact surface between the friction ring and a guide wheel or a guide surface is understood.

[33] In order to increase the reliability of the conical-friction ring transmission, it can also be provided that the conical-friction-ring transmission has a mechanical feedback between the axial position of the friction ring and the adjusting device. This mechanical feedback, which may consist of, for example, a lever mechanism, in particular, provides reliability in the event of failure of an electrical control of the conical-friction ring transmission. Advantageously, the friction ring is moved via the mechanical feedback position-controlled in the preselected before the failure of the electrical position. In this respect, in addition to the operational reliability, the control of the friction ring is simplified, since only a desired position of the friction ring and not the actual position of the friction ring needs to be adjusted, since the friction ring is positioned accordingly by the feedback itself.

[34] However, such a mechanical feedback can also increase in terms of a conical-friction ring transmission, in which the adjusting bridge is mounted via an axial guide device which defines the Verstellbrückenweg and tiltable, and which was therefore omitted the advantage of a stationary axial guide means lead to operational safety, especially since in case of failure of control units, the position of the friction ring nachwievor remains controlled.

In order to solve the input standing task alternatively or cumulatively to the above features, thus a conical friction ring gear is proposed with two spaced apart from each other by a gap friction cones over a friction ring, which passes through the gap to one of the two friction cone revolves and along the gap over a freely along an adjustment path displaceable adjusting bridge is arranged displaceably, wherein the adjusting bridge is mounted on an axial guide means and wherein the conical friction ring transmission is characterized by a mechanical feedback between the position of the friction ring and the position of the Führungsseimichtung which defines the Verstellbrückenweg and tilted.

The advantageous embodiment of a conical-friction ring transmission with a mechanical feedback provides a mechanical, fixed position adjustment such that the desired ring setting needs to be specified only by a corresponding control of the conditional by the feedback control loops. Specifically, this means that only a desired position of the friction ring needs to be preset and the regulation of the final position of the friction ring is oriented at the previously set value until the position of the friction ring corresponds to the desired value.

As can be seen immediately, the fact is also advantageous that the energy for the actual adjustment of the friction ring by the proper motion and thus can be removed from the drive of the conical friction ring, since the kinematics of the friction ring from the contact of the friction ring with the results in two cones. The friction ring is moved out of its stable and stationary position by forces which arise and act on the frictional contact, if these forces acting on the frictional contact are no longer in equilibrium. This is the case when the friction ring is rotated by the guide means by a pivot angle, wherein the pivot angle is proportional to the total force acting on the ring and thus proportional to the adjustment speed of the friction ring. Consequently, the presetting of the desired friction ring position requires only a minimum of energy, since only at the beginning of the wandering of the friction ring the angle of rotation needs to be adjusted.

[38] As can be seen immediately, the feedback has the further advantageous effect on the conical friction ring transmission that in case of failure of an actuator for controlling the adjusting device, the angle of the friction ring initially in its predetermined by the actuator at the time of failure position remains and that thereby sudden changes omit the transmission behavior.

[39] The control of the feedback sets in the above-described advantageous embodiment in connection with the above-described kinematics of the friction ring, preferably the desired ring position, which then assumes the friction ring automatically due to the feedback. The feedback is then capable of the preset twist angle, which is a measure of the adjustment speed, during approach to reduce the desired ring position. It is immediately apparent that upon reaching the desired position, the angle of rotation approaches zero or reaches a value of a stable and force-free friction-ring movement.

[40] By means of this mechanical feedback, therefore, a previously set transmission ratio remains, even if the drive fails. Optionally, it is also possible to bypass the failed control by a failure of control, for example, only mechanically, so that even in case of failure of the drive ratio can still be changed. This also applies, for example, when a motor vehicle or a motorcycle with a corresponding conical friction ring gear is turned off and thus an electrical control is no longer possible. In these cases, or when the vehicle is still rolling and the transmission or the drive sträng still engaged with the engine, it may be necessary to continue to drive the conical friction ring gear, which is possible by the mechanical failure control.

[41] It is also advantageous for a conical-friction-ring transmission with mechanical feedback if the conical-friction-ring transmission has means for reversing the direction of action of the feedback between the position of the friction ring and the position of the guide device. This embodiment is advantageous for the case that in Kegelreibringgetriebe a reversal of direction takes place and the ring drive or feedback of the shape is formed so that it leads only in one direction of rotation to a stable position of the friction ring. Thus, a stable further operation can be ensured, since then the angle of rotation is withdrawn again as soon as the friction ring approaches the preset position, as explained above. If the direction of rotation is reversed, the feedback otherwise leads, depending on the specific embodiment of the feedback or the control of the angle of rotation for the friction ring to an increase in the twist angle instead of a reduction, when the friction ring approaches the preset position. In this respect, then an effective direction reversal of the feedback is advantageous for a stable control loop.

[42] As can be seen immediately stabilizes the effective direction reversal of the feedback, if necessary, the friction ring for both possible directions of rotation of the conical-friction ring transmission. This gains not only in a motor vehicle in importance when the motor vehicle is driven backwards, but especially in light motorcycles, which are pushed backwards for shunting. In this case, the conical friction ring gear can be stably maintained in a Anfahrübersetzungsverhältnis, whereby a start after shunting can be done safely. Otherwise, while shunting the Friction ring position and thus the transmission ratio of the conical friction ring gear due to the unstable feedback or control are changed, to undefined and unpredictable gear ratios, which may result in an increased accident risk or an increased risk of operating errors. [43] Preferably, the feedback is mechanically implemented, whereby a high reliability can be achieved even in the event of a power failure. However, the feedback can also be done electronically, for example by an electronic position sensor, which in turn acts on the setting mechanism via an actuator.

To solve the input standing task is alternatively or cumulatively to the above features further proposed a conical friction ring with two spaced apart from each other by a gap friction cones, which rotates about a friction ring which passes through the gap to one of the two friction cone and along the The adjusting bridge is mounted via an axial guide means which defines the Verstellbrücken- and tilted via an actuator, wherein the actuating drive is operatively connected to the axial guide means via a control gear and wherein Means are provided for determining the position of the friction ring, which act mechanically on the control behavior of the adjusting gear. As a result, feedback does not necessarily have to take place, which, however, with a suitable embodiment of the action of the determination means on the actuating drive, a feedback can be realized.

By the mechanical action on the control behavior, a reliable operation of the guide device can be structurally easily implemented even in the event of a power failure.

[46] In this case, the setting behavior can be, for example, the adjustment speed, whereby depending on the difference between the actual position of the friction ring and the desired position of the friction ring, a different setting speed can be set automatically. Likewise, in particular, a local specification for the actuating gear can be made by the determination means and thus directly to be reached a position of the adjustment bridge can be specified. [47] In particular, the determination means for determining the position of the friction ring can also be designed mechanically, whereby advantageously additional control algorithms, in particular electronic assemblies, can be dispensed with. [48] Thus, it is also possible that the action of the determination means on the control behavior of the adjusting gear via a planetary gear. A planetary gear, but also another conceivable transmission is both compact and precise executable and combined with little constructive effort with an electric motor drive or an electric actuator. As can be seen immediately, an electrical control is thus further complemen- tary readily implementable.

[49] In order to realize a particularly efficient, ie low-loss, embodiment of a conical-friction ring transmission, it is also possible that the action of the determination center] on the setting behavior of the adjusting mechanism takes place via a toggle mechanism. The same advantages also arise when the determination means comprise a lever arm. Thus, the use of a lever mechanism promotes both reliable and low-wear position determination of the friction ring. It is understood that a simple lever arm in the context of the invention can be used as a lever mechanism.

[50] The lever arm may have a slot, whereby in particular translational and rotational movements, as they occur in a multi-layered form in a conical friction ring gear, for example in a displacement of the adjustment bridge, an axial guide means or the angle of the friction ring, are coupled easily and reliable.

[5 1] Also, the lever arm can represent an arm of a toggle lever, so that the corresponding advantages can be implemented even in a toggle mechanism, which contributes accordingly to operational safety.

[52] For a structure that is structurally adaptable to changing conditions, the determination means may comprise a toothed belt. As a result, for example, external requirements, which are provided by third parties, such as OEMs or engine manufacturers to the transmission, can be implemented more easily. Toothed belts can, but need not, be used permanently without any lubricant, which, for example, compared to chains, have a much lower noise emission and at the same time can reduce the total mass of the conical-type transmission over other applications.

[53] If required, the conical friction ring gear can have means for reversing the direction of action of the determining means in their action on the setting behavior of the adjusting gear, wherein such reversal of the direction of effect is advantageous for the reasons mentioned above, if the positioning of the friction ring is stable only in one direction of rotation. The effective direction reversing means may comprise a brake-adjustable planetary gear. As already indicated above, a planetary gear is particularly space-saving and reliable applied to a conical friction ring gear, with these benefits also affect the effective direction reversing, [55] include the effective direction reversal a lever assembly with a dead center, where two directions of movement of the levers to each other are possible, and An actuator for selectively setting the direction of movement, also a very simple direction of direction can be realized, which also builds very reliable. It is, as immediately apparent, also conceivable that the adjuster can be controlled mechanically or electrically. For example, the adjuster may be a spring arrangement that biases a lever in the dead center in one direction so that it leaves the dead center in one direction. If the actuator acts in a different direction, the lever leaves the dead center in a different direction.

[56] It is understood that the features of the solutions described above or in the claims can optionally also be combined in order to be able to implement the advantages in a cumulative manner.

[57] Further advantages, objects and features of the present invention will be explained with reference to the following description of exemplary embodiments, which are also illustrated in particular in the appended drawing. In the drawing show:

1 shows a device for adjusting a friction ring angle with a parallel positionable slide rail;

Figure 2 shows a further embodiment of a device for adjusting a friction ring angle with an electro-motor actuator on the adjustment bridge;

3 shows a further embodiment of a device for adjusting a friction ring angle with a mechanical actuator;

Figure 4 is a detail view of the arrangement of Figure 3;

Figure 5 is a schematic diagram of an adjusting device and a control for a

Adjustment device with mechanical feedback in a schematic plan view with a schematic partial view of the side of a setting gear;

Figure 6 shows the adjusting device and control with mechanical feedback of Figure 5 in a perspective view;

FIG. 7 shows a further adjusting device and control for the adjusting device with mechanical feedback in the position of an average transmission ratio; FIG. 8 shows the adjusting device and the control according to FIG. 7 in the position of a large transmission ratio;

FIG. 9 shows the adjusting device and the control according to FIGS. 7 and 8 in FIG

Position of a small gear ratio;

FIG. 10 shows an adjusting device and control for the adjusting device with mechanical feedback and with a switching unit for reversing the direction of action in a schematic front view;

Figure 11 shows the adjusting device and control with mechanical feedback of Figure 10 in a schematic plan view;

FIG. 12 shows a further adjustment device and control for the adjusting device with mechanical feedback and with a switching unit for reversing the direction of action in a schematic front view;

13 shows the adjusting device and control with mechanical feedback of Figure 12 in a schematic plan view;

14 shows a further adjusting device and control for the adjusting device with mechanical feedback and with a switching unit for reversing the direction of action in a schematic front view;

Figure 15 shows the adjusting device and control with mechanical feedback of Figure 14 in a schematic plan view;

16 shows a further adjusting device and control for the adjusting device with mechanical feedback and with a switching unit for reversing the direction of action in a schematic front view;

17 shows the adjusting device and control with mechanical feedback of Figure 16 in a schematic plan view; and

FIG. 18 shows a further adjusting device and control for the adjusting device with mechanical feedback and with a switching unit for reversing the direction of action in the front view.

[58] In a first embodiment, as shown in particular in Figure 1, has an adjusting device 2 of a conical-friction ring 1 - not shown in Figure 1, wherein in the present case similarly effective components of the various embodiments are numbered identically - via a friction ring 6, which a friction ring 5 for determining a friction ring position leads, which interacts with friction cones 3 of the conical friction ring 1 in a conventional manner. For this purpose, the adjusting device 2 has an adjusting bridge 8 which carries the friction ring guide 6 and, within the adjustment 2 by means of two axial guide devices or two Verstellbrücken- guides 9 translationally substantially in the direction of a rotation axis (not shown) of a gap between the friction cones 3 in a conventional manner.

To adjust the transmission ratio of the conical-friction ring gear, which takes place via the position of the friction ring 5 along two friction cones 3, not shown, of the conical-friction ring transmission 1, a slide rail 1 1 is arranged in the adjustment device 2. This slide rail 11 in turn is arranged to be displaceable parallel to two sliding guides 12, wherein both slide guides are substantially perpendicular to the axis of rotation and thus parallel to a rotation axis containing rotation plane, which in turn is pierced perpendicularly through the axis of rotation of the friction ring 5. Also used for adjusting the slide 1 1 spindle drive 13 is aligned parallel to the two sliding guides 12 in this embodiment, but this is not necessary for adjusting the slide 1 1 necessary. In this respect, it is also possible to arrange the spindle drive 13 askew to the two sliding guides 12. Likewise, the two sliding guides 12 may be at an angle to the plane of rotation.

The slide 1 1 is coupled to the friction ring 5 via a steering slide 10 which controls an adjustable, in this embodiment, two guide wheels friction ring guide 7, which in the slide rail 1 1 substantially along an adjustment path of the friction ring 5 in a first Displacement direction is arranged displaceable. A second displacement direction of the steering slide 10 is set at the adjusting bridge 8, whereby the steering slide 10, when the slide 1 1 is guided parallel to the plane of rotation of the friction ring 5, is displaced within the adjustment bridge 8 relative to the friction ring 5. This displacement of the steering slide 10 has the consequence that the friction ring 5, since the displacement path of the steering slide 10 within the adjustment 8 is not parallel to the plane of rotation of the friction ring 5, tilted.

[61] The friction ring 5, which, if it is in a stationary orbit begins to wander at a tilt along the friction cone 3, since now unsteady forces act on contact surfaces between the friction ring 5 and the cones 3. The arrangement of the two displacement directions is selected such that when displacing the friction ring 5 and consequently with displacement of the adjusting bridge 8 of the steering slide 10 is gradually moved to its initial position within the adjustment bridge 8, that is vertical. This is due to the slightly employed arrangement of the slide rail 1 1. Reaches the steering slide 10 now during the adjustment of the friction ring 5 its original position, the tilting of the friction ring 5 is equally withdrawn and the friction ring 5 goes to the newly approached position along the friction cone 3 in a stationary position.

Significant for the embodiment of Figure I is the fact that the slide 1 1 due to the parallel guide along the sliding guides 12 now for each gear ratio of the conical friction ring 1 has the same tolerance, since the leadership of the steering slide 10 along a precisely manufactured Groove takes place and possible tolerance fluctuations of the spindle drive 13 in the entire Verstel Ibereich the slide 1 1 and the steering slide 10 have identical effects and not amplified by leverage, which can occur on a rotatably mounted slide 1 1. [63] An alternative embodiment may instead of a perpendicular to the rotation plane of the friction ring 5 spindle drive 13 also have a parallel to the adjustment away the adjusting device 2 extending profile shaft 15 or a directly acting electric motor 14 as an actuator 14, as shown in Figures 2 to 4. The electric motor 14 or the professional! In this case, shaft 15 acts on a switching shaft 16 (numbered exemplarily in FIGS. 3 and 4), which is operatively connected to an adjustable friction-ring guide 7 and is capable of adjusting this friction-ring guide 7 parallel to the axis of rotation of friction-ring 5.

[64] The adjustable friction ring guide 7 provided on the adjusting bridge 8 causes, as in the embodiment explained above, tilting of the friction ring 5, whereby the friction ring 5 is automatically displaced. With the displacement of the friction ring 5 takes place, as can be seen immediately on the friction ring 6 but also on the adjustable friction ring 7, a displacement of the entire adjustment bridge 8 along the two Verstellbrückenführungen. 9

Both embodiments explained above each have constructive advantages, on the one hand the electric motor 14 due to the arrangement on the adjustment bridge 8 can be used very easily and with little space and on the other hand, the control of the profile shaft 15 by means of a stationary or fixed to the housing drive takes place and thus the drive is decoupled from the movement of the adjusting bridge 8.

A further embodiment of a conical-friction ring transmission 1 with an adjusting device 2 is explained with reference to FIGS. 5 and 6, wherein the adjusting device 2 has a mechanical feedback of the position of the friction ring 5 or the adjusting bridge 8 by means of a feedback transmission 30. For feedback of the friction ring position, the adjustment bridge guide 9 is rotatably arranged about a Verstellbrückenachse 18 in this embodiment. The adjustment of the adjustment bridge guide 9 about the Verstellbrückenachse 18, wherein on an adjusting coupling rod 22 an adjusting force 72 acts on the adjusting bridge 9 acts against a torque 60 on the adjusting bridge 8 and thus causes a rotation of the friction ring 5, whereby this changes its position along a cone axis 4 of the cone 3. In addition to the adjusting coupling rod 22, which acts indirectly on the adjusting bridge 8, a feedback coupling rod 33 is arranged on the adjusting bridge 8 or on a displaceable feedback axis 36, which returns the current position of the adjusting bridge 8 to the feedback gear 30. This feedback of the feedback coupling rod 33 in this case takes place via a feedback lever 31, which is operatively connected to the feedback coupling rod 33 by means of a feedback knee 35.

While the feedback lever 31 in turn acts on a ring gear 44 of a planetary gear 40, the Verstellkoppelstange 22 via a Verstellknie 23 and an adjusting lever 21 with a sun gear 41 of said planetary gear 40 is operatively connected. A the adjusting lever 21 and the Verstellkoppelstange 22 including adjusting 20 is coupled to the feedback gear 30 via planetary gear 43 of the planetary gear 40, wherein a planetary carrier 42, on which the planet 43 are arranged on a control shaft 51 of a servo motor 50 are adjustable and wherein Adjusting 20 in this embodiment is part of a control gear of the conical friction ring 1, which is controlled by the servo motor 50 and on which the feedback mechanism 30 acts mechanically.

[69] If the actuator 51 and thus the planet carrier 42 are actuated via the servomotor 50, initially only an adjustment of the adjustment bridge guide 9 by means of the variable transmission 20 follows, since initially the adjustment bridge 8 remains in its position and thus the ring gear 44 retains its position. If an adjustment of the Verstellbrückenführung 9 in the direction of an adjustment 75 to smaller ratios 73, reduces a Verstellbrücken away defining adjustment position 70 of the adjusting bridge 8, since the friction ring 5 begins to wander in the direction of the small ratios 73.

[70] As the friction ring 5 travels, a feedback force 63 acts on the feedback coupling rod 33, which in turn results from an axial force 61 and a transverse force 62 of the adjustment bridge 8. The feedback force 63, which moves the feedback lever 31 in the illustrated view counterclockwise, acts now, if the servo motor 50 remains in a fixed position, by means of the planet 43 on the adjusting lever 21, which is again adjusted in a clockwise direction and the Verstellbrückenführung 9 pivots back to its original position. Has the Verstellbrückenführung 9 reaches its original position, the feedback force 63 vanishes, since the friction ring 5 now rotates in a stable position around the friction cone 3 and cancel each other in the direction of the cone axis 4 acting on the friction ring 5 forces.

[71] In order to effect an adjustment of the friction ring 5 in the direction of large transmission ratios 74, the adjustment bridge guide 9 is pivoted in an adjustment direction 76. Here, as can be seen immediately, a walking of the adjusting bridge 8 in the direction of the large transmission ratio 74, wherein the feedback lever 31 is moved in the illustrated view in the clockwise direction and by means of the planetary gear 40, the adjusting lever 21 moves counterclockwise about its axis of rotation.

[72] Instead of a planetary gear 40 for mechanical feedback, the conical friction ring transmission 1 according to FIGS. 7 to 9 has a lever arrangement with an actuating drive 52, which acts on an adjusting lever 53. Here, an adjustment of the actuator 52 acts in the adjustment direction 75 to smaller ratios 73 and in the adjustment 76 to larger ratios 74 initially on the adjustment lever 21, which is operatively connected by means of Verstellknies 23 with the lever 53, on the Verstellbrückenführung 9 and on the adjustment bridge 8. The adjustment bridge 9 is here also arranged rotatably about the Verstellbrückenachse 18, It is understood that instead of the adjustment drive 52, a servomotor or other actuator may be provided.

In this embodiment, a feedback lever 32 designed as a lever arm or toggle lever is arranged on the displaceable feedback axis 36 of the adjusting bridge 8, which rotates about a housing-fixed feedback axis 37 and thereby actuates a feedback coupling rod 34 of the feedback gear 30. [74] The interaction of the feedback lever 32 with the housing-fixed feedback axis 37 causes a groove or a slot in the feedback lever 32, by means of which or by means of which the adjustment bridge 8 actuates and guides the feedback lever 32. The reaction of the feedback gear 30 on the adjusting knee 23 causes, if the actuator 52 is held, a reset of the adjusting 20, whereby the adjustment bridge 8 is in turn pivoted back to its original position.

[75] As in the previously described exemplary embodiment, the adjusting bridge 8 according to FIGS. 7 to 9 is only around the adjusting bridge axis 18 by means of the adjusting bridge guide 9 arranged displaceably. The adjustment bridge 8 is guided on the Verstellbrückenführung 9 side facing away by means of Verstellbrückenfixierung 17 slidably. In this case, the adjustment bridge 17 leaves the adjustment bridge 8 a degree of freedom of movement in a plane on which the adjustment bridge axis 18 is perpendicular. Thus, the adjustment keeps the possibility to pivot about Verstellbrückenachse 18 and the Verstellbrückenfixierung 17 is at the same time fixed to the housing, which causes a significant reduction in vibration of the adjustment.

For automatic adjustment of the position of the friction ring 5, it is necessary that the friction ring 5 pivots about an axis which on the one hand with the adjustment bridge axis 18 coincides or at least parallel to it and on the other hand extends at least with a directional component parallel to a plane which is spanned by the cone axes 4 of the two friction cone 3 shown as an example. Thus, the leadership of the friction ring 5 via the two friction ring guides 6, which are arranged outside the plane spanned by the cone axes 4 plane on the Verstellbrücke 8 and therefore give the friction ring 5 a twist angle.

[77] A further embodiment of an adjusting device 2 for a conical-friction ring transmission 1 contains, in addition to the planetary gear 40 used for feedback, an additional gearbox interposed between the adjusting gear 20 and the planetary gear 40 for reversing the direction of action of the adjusting gear 20, as implemented in the exemplary embodiments described below.

The stable position of the friction ring 5 along the adjusting position 70 of the adjusting bridge 8 depends - depending on the concrete implementation of the friction ring and / or the feedback - inter alia, on the direction of rotation of the friction cone 3, since the direction of rotation of the friction cone 3 on the friction ring 5 acting forces and torques determine. If the direction of rotation in the conical-friction ring gear 1 changes, this also results in a change in the force relationships in frictional contact between the cones 3 and the friction ring 5, as a result of which the automatically controlled adjustment direction of the adjusting bridge 8 also changes. The reversal of motion of the adjustment bridge 8 thus also results in a reversal of the feedback of these by means of the feedback gear 30 to the planetary gear 40 result.

[79] Because of the reversal of the feedback dynamics, the cone friction gear 1 according to FIGS. 10 and 11 therefore has a forwardly running bevel gear 89 and a backward-running bevel gear 90, which can be selectively driven by means of a switched via a switching unit 84 shift sleeve 85. The planetary gear 40 controlled via the servomotor 50 is coupled in the illustrated embodiment by means of the planetary carrier 42 to a driving bevel gear 88, which in turn meshes with both bevel gears 89, 90. In this embodiment, the adjusting bridge 8 is mounted on the adjusting bridge guide 9 by means of a linear guide 82, which drives the friction ring 5 in a particularly wear-resistant and low-friction manner and, in particular, with a very high accuracy.

[81] The two embodiments of the adjusting device 2 according to FIGS. 12 to 15 offer another form of reversal of direction of action. In this case, the switching unit 84 includes a toothed coupling 87 which fixes a planetary carrier 92 and a ring gear 94 of the switching unit 84 designed as a planetary gear can. A predetermined by the servo motor 50 and, by the planet carrier 42 direction of rotation is thus passed unchanged when setting the planet carrier 92 and the ring gear 94 to the adjusting 20, as well as planet 93 of the switching unit 84 are fixed. [82] If a reversal of the direction of effect is desired, the toothed coupling 87 is actuated so that the planet carrier 92 is interconnected with a housing 95 and the direction of rotation of the ring gear 94 with respect to a sun gear 91 is changed via the planets 93.

[83] The embodiments according to FIGS. 12 to 15 furthermore contain a toothed belt 83. This toothed belt 83, which engages the ring gear 44 of the planetary gear 40, is coupled to the adjusting bridge 8 and in this case brings about the feedback on the adjusting bridge guide 9, which previously explained, about the Verstellbrückenachse 18 is pivotally mounted in the adjusting device 2 and the Verstellbrücke 8 by means of the linear guide 82 on one side. On the side of the adjustment bridge 8 facing away from the adjustment bridge guide 9, the adjustment bridge fixing 17 for stabilizing the adjustment bridge 8 is again provided in this embodiment.

The feedback of the adjusting bridge 8 with the planetary gear 40 is carried out in the embodiment of Figures 12 and 13, characterized in that the toothed belt 83 is connected to the adjustment bridge 8, and in the embodiment of Figures 14 and 15 via a toothed belt clutch 77 on the adjustment 8. The toothed belt clutch 77 causes a fixed connection of the toothed belt 83 with the adjusting bridge 8, whereby a movement of the adjusting bridge 8 via the toothed belt 83 to the ring gear 44 of the planetary gear 40th is transmitted. The control of the transmission ratio is thus similar to the embodiments described above.

In contrast to the embodiment according to FIGS. 12 and 13, the embodiment according to FIGS. 14 and 15 offers an adjustment possibility of the adjustment bridge 8 through a four-limb adjustment bridge guide 80. Two parallel guided guide rods 79 of this four-membered adjustment bridge guide 80 which guide the adjustment bridge 8 Guide over the linear guide 82, although performed parallel to each other for adjusting the friction ring 5, but without performing a rotation about the Verstellbrückenachse 18. Only two pivotable guide rods 78 of the four-limb Verstellbrückenführung 80 are pivoted about the Verstellbrückenachse 18 and about a not shown, however, the Verstellbrückenachse 18 parallel axis and thus set the friction ring 5 at appropriate angles. As a result, the tension of the toothed belt 83 changes only insignificantly.

As already explained above, the switching unit 84 or the ring gear 94 acts on the adjustment bridge guide 9, in this case on at least one of the two pivotable guide rods 78. The toothed belt 83, which drives the ring gear 44, is connected to the adjustment bridge 8 via a Synchronous toothed belt clutch connected.

[87] The two embodiments according to FIGS. 12 to 15 have the advantage that assemblies arranged on the side of the friction cone 3 can largely be dispensed with.

[88] The two embodiments according to FIGS. 16 to 18 also have a four-limb adjustment bridge guide 80, but this consists of a rigid frame without pivotable guide rods 78. In this case, the adjusting mechanism 20 acts directly on the adjustment bridge axis 18 which is arranged centrally on the four-membered adjustment bridge guide 80 and which in turn is operatively connected to the planetary gear 40 by means of the shake unit 84. The interconnection or feedback of the adjusting bridge 8 with the four-limbed Verstellbrückenführung 80 by means of the planetary gear 40 and the switching unit 84 is thus in accordance with the embodiments described above.

[89] The essential difference of the embodiment according to FIGS. 16 and 17, in contrast to the previously described embodiments with the four-limb adjustment bridge guide 80, is the use of the feedback gear 30 with the feedback lever 31 and the feedback rod 33 acting on the ring gear 44 of the planetary gear 40, which in turn are interconnected via the feedback knee 35. The arrangement of the force acting on the planetary gear 40 servo motor 50 is in turn fixed to the housing and thus decoupled from the movement of the adjusting bridge 8 and the four-limbed Verstellbrückenführung 80.

Furthermore, the servomotor 50 of the exemplary embodiment according to FIG. 18 is fixedly arranged on the adjusting bridge 8. Thus, the servo motor 50 with the adjusting bridge 8 is arranged displaceably. The ring gear 44 is now operatively connected by means of a rack 97 with the housing 95, whereby the movement of the adjusting bridge 8 causes the feedback to the planetary gear 40.

The switching unit 84 used for reversing the direction of action is arranged on a guide pivot axis 98 of a pivotable friction ring guide 96 which replaces the adjustment bridge axis 18 explained above. Thus, the adjustment bridge 8 is arranged by means of the linear guide 82 only translationally on the Verstellbrückenführung 9 movable and performs no own rotation more. A control of the servomotor 50 causes logical, depending on the position of the shift sleeve 85 pivoting the pivotable friction ring 96 in clockwise or counterclockwise about the guide pivot axis 98. The subsequent translational adjustment of the adjustment 8 leads, as the ring gear 44 rolls on the rack 97 , to the feedback, wherein with progressive adjustment of the adjusting bridge 8, a pivoting angle of the pivotable friction ring guide 96 is withdrawn. In this respect, this embodiment is subject to the same kinematics or regulation, as has already been explained above. [92] For better controllability of the friction ring position, it is also possible that between the actuator 51 and the ring gear 44 of the planetary gear 40, which relative to each other have an adjustable rotation angle, a sensor (not shown) is arranged. By means of this sensor, on the one hand, the adjustment speed but also, on the other hand, the friction ring position can be returned to a control unit of the conical-friction ring transmission 1, which determines or regulates the desired transmission ratio. LIST OF REFERENCE NUMBERS

1 conical friction ring gear 43 Planet

2 adjusting device 44 ring gear

3 friction cone 50 servomotor

4 cone axis 51 control shaft

5 friction ring 52 actuator

6 Friction ring guide 53 Lever

7 adjustable friction ring guide 60 Torque of the adjustment bridge

8 Verstellbrücke 61 Axial force of the adjustment bridge 9 Verstellbrückenführung 62 Transverse force of the adjustment

10 Steering slide 63 Feedback force

1 1 Slide rail 70 Adjustment position of the adjustment bridge

12 sliding guide 72 adjusting force

13 spindle drive 73 small gear ratio 14 electric motor 74 large gear ratio

15 Profile shaft 75 Adjustment direction to smaller over-

16 shift shaft 0 settlement ratios

17 Verstellbrückenfixierung 76 Adjustment direction to larger Über¬ 8 Verstellbrückenachse

20 Adjusting gear 77 Timing belt coupling

21 adjusting lever 78 pivotable guide rod

22 Adjusting coupling rod 5 79 parallel guide rod

23 adjustable knee 80 four-link adjustable bridge guide

30 Feedback gear 82 Linear guide

31 Feedback lever 83 Timing belt

32 Feedback lever 84 Shift unit

33 Feedback coupling rod 0 85 Shift sleeve

34 Feedback coupling rod 87 Gear coupling

35 back-coupling knee 88 driving bevel gear

36 displaceable feedback axis 89 forward-running bevel gear

37 housing-fixed feedback axis 90 reverse-running bevel gear

40 planetary gear 5 91 sun gear

41 sun gear 92 planet carrier

42 Planet carrier 93 Planet Ring gear 97 rack

Housing 5 98 Guide pivot axis Swiveling friction ring guide

Claims

claims:

1. conical friction ring transmission (1) with two spaced apart from each other by a gap

Friction cones (3), which is arranged so as to be displaceable by way of a friction ring (5) which passes through the gap around one of the two friction cones (3) and is displaceable along the gap via an adjustment bridge (8) freely displaceable along an adjustment bridge path, wherein the adjustment bridge (8) 8) is mounted via an axial guide device and has a device for adjusting a friction ring angle, characterized in that an adjusting device (2) arranged on the adjusting bridge (8) is controlled by means of a sliding rail (11) which can be positioned in parallel,

2. conical friction ring transmission (1) with two spaced apart from each other by a gap

Friction cones (3), which is arranged so as to be displaceable via a friction ring (5) which passes through the gap around one of the two friction cones (3) and is displaceable along the gap via an adjustment bridge (8) which is freely displaceable along an adjustment bridge path, wherein the adjustment bridge (8) 8) is mounted via an axial guide device, in particular according to claim 1, characterized in that a on the

Adjusting bridge (8) arranged adjusting device (2) by means of a spindle drive (13) is driven.

3. conical-friction ring gear (1) with two mutually spaced by a gap friction cones (3), which rotates about a friction ring (5) through the gap to one of the two friction cone (3) and along the gap over a free along a

Verstellbrückenweges displaceable adjusting bridge (8) is arranged displaceably, wherein the adjusting bridge (8) is mounted on an axial guide means, in particular according to claim 1 or 2, characterized in that on the Verstellbrücke (8) arranged adjusting device (2) by means of a stationary drive shaft, the one with the United partial device (2) corresponding

Downforce on the adjustment bridge (8) interacts, is driven.

4. conical friction ring transmission (1) according to claim 3, characterized in that the drive shaft is a profiled shaft (1) or rail.

5. conical friction ring gear (1) with two mutually spaced by a gap friction cones (3), which circulates through a friction ring (5) through the gap to one of the two friction cone (3) and along the gap over a free along a Verstellbrückenweges displaceable adjusting bridge (8) is arranged displaceably, wherein the adjusting bridge (8) mounted on an axial guide means, in particular according to one of the preceding claims, characterized in that on the Verstellbrücke (8) arranged adjusting means (2) by means of a motor, the on the adjusting device (2) is arranged, is driven.

6. conical friction ring transmission (1) according to one of the preceding claims, characterized in that the axial guide means is stationary with respect to cone axes (4) of the friction cone (3) is arranged.

7. conical friction ring transmission (1) according to one of the preceding claims, characterized in that the adjusting bridge (8) has at least two guide points for the friction ring (5) and at least one of the two guide points on the adjusting device (2) is adjustable.

8. conical friction ring transmission (1) according to any one of the preceding claims, characterized by a mechanical feedback between the axial position of the friction ring (5) and the adjusting device (2).

9. conical friction ring gear (1) with two friction cones spaced apart from each other by a gap, which is displaceable over a friction ring (5) which passes through the gap around one of the two friction cones and along the gap via an adjustment bridge (8) freely displaceable along an adjustment bridge path is arranged, wherein the adjusting bridge (8) is mounted via an axial guide means, in particular according to one of the preceding claims, characterized by a mechanical feedback between the position of the friction ring (5) and the position of the Führungseinrichtun which defines the Verstellbrücken away and tilted is.

Conical friction ring transmission (1) according to claim 9 characterized by means for reversing the direction of action of the feedback between the position of the friction ring (5) and the position of the guide means.

Bevel friction ring gear (1) with two mutually spaced by a gap friction cones (3), which circulates through a friction ring (5) through the gap to one of the two friction cone (3) and along the gap over a freely displaceable along a Verstellbrückenweges Verstellbrücke (8) is arranged to be displaceable, wherein the adjusting bridge (8) is mounted via an axial guide device, in particular according to claim 9, characterized in that the axial guide means defines the Verstellbrückenweg and via an actuator (14) is tiltable, the actuating drive (14 ) is operatively connected to the axial guide means via a control gear and means for determining the position of the friction ring (5) are provided, which act mechanically on the control behavior of the adjusting gear.

Conical friction ring transmission (1) according to claim 1 1, characterized in that the action of the determining means on the adjusting behavior of the adjusting gear via a planetary gear (40).

Conical friction ring transmission (1) according to claim 1 1 or 12, characterized in that the action of the determining means is carried out on the control behavior of the adjusting gear via a toggle mechanism.

Conical friction ring transmission (1) according to one of claims 1 to 13, characterized in that the determining means comprise a lever arm.

Conical friction ring transmission (1) according to claim 14, characterized in that the lever arm has a slot,

Conical friction ring transmission (1) according to claim 14 or 15, characterized in that the lever arm is an arm of a toggle lever.

Conical friction ring transmission (1) according to one of claims 1 to 16, characterized in that the determining means comprise a toothed belt (83).

18. conical friction ring transmission (1) according to one of claims 1 1 to 17, characterized by means for reversing the direction of the determination center! in their action on the control behavior of the adjusting gear.

19. conical friction ring transmission (1) according to claim 10 or 18, characterized in that the effective direction reversing means comprise a controllable via a brake planetary gear.

20. conical friction ring transmission (1) according to claim 10, 18 or 19, characterized in that the effective direction reversing means having a lever arrangement with a dead center, on which two directions of movement of the levers to each other, and a Ansteller for selectively setting the direction of movement.