EP1794475A2

EP1794475A2 - Friction ring-type transmission comprising two roller bodies which are arranged at a distance from each other about a gap

Info

Publication number: EP1794475A2
Application number: EP05774441A
Authority: EP
Inventors: Christoph DRÄGER; Werner Brandwitte
Original assignee: Individual
Current assignee: Individual
Priority date: 2004-08-06
Filing date: 2005-08-05
Publication date: 2007-06-13
Also published as: US20140087915A1; EP2687754A3; ES2611087T3; US20090118073A1; WO2006012892A2; US9638295B2; WO2006012892A8; EP3181947A1; WO2006012892A3; EP2687754B1; US9316293B2; EP2682645A2; CN101111696A; EP2687754A2; EP2682645A3; CN101111696B; DE112005001882A5; EP2687753A3; EP2687753A2

Abstract

The aim of the invention is to further develop a friction ring-type transmission. According to the invention, a friction ring-type transmission comprises two roller bodies which are arranged at a distance from each other about a gap, which correspond to each other via the friction ring and which rotate on axial roller body axes. According to the invention, the friction ring is arranged in an adjusting bridge in such a manner that it can be axially displaced about an adjusting path along the gap.

Description

Friction-ring transmission with two rolling elements spaced from each other by a gap

[01] The invention relates to a friction-ring transmission with two roller bodies spaced apart from each other by a gap, which correspond to each other on axial rolling-element axes via a friction ring, in which the friction ring is displaceable axially in an axially displaceable adjusting bridge about an adjustment path along the gap , The invention also relates to a friction-ring transmission with two rolling bodies spaced apart from each other by a gap, which correspond to each other on axial rolling-element axes via a friction ring in which the friction ring can be displaced axially along the gap in an adjustment bridge guided axially freely in a cage by an adjustment path is arranged.

[02] Such adjustment bridges are known from the prior art, as described, for example, in EP 0 878 641 A1 and EP 0 980 993 A2, and can be held in a cage and articulated via this cage. However, there is the risk that the adjusting bridge between the guide rods of the respective cage is tilted. However, this danger exists not only with regard to a cage but generally when the adjustment bridge is mounted on guide rods.

It is an object of the present invention to further develop known friction ring gear and thus to eliminate the disadvantages described.

[04] The object of the invention is achieved, on the one hand, by a friction ring transmission with two roller bodies spaced apart from each other by a gap, which correspond to each other on axial rolling body axes via a friction ring in which the friction ring is axially displaceable in an axially freely displaceable adjusting bridge is arranged displaceable along the gap, and the Verstellbrü¬ bridge is supported by a single axial guide means.

[05] 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. be rerable, so that the adjustment bridge in particular a conditional in another way displacement of the friction ring, as this example, when the friction ring is tilted, can follow. [06] Since the adjusting bridge is advantageously mounted by means of only a single axial guide device, in the present case there is only one guide region between the adjusting bridge and the axial guide device, in which the adjusting bridge is in contact with the axial guide device. As a result, tilting of the adjustment bridge with respect to a plurality of guide devices is advantageously prevented. In addition, such an arrangement can build extremely small.

[07] The term "rolling elements" describes devices which are suitable for transmitting torque from an input side to an output side or vice versa, for example, these rolling elements are conically or cylindrically shaped structures which are in contact with each other by means of a friction ring Each rolling body is, for example, about an axial rolling body axis, wherein each axial rolling body axis of a first rolling body is spaced from an axial rolling body axis of a further rolling body By suitable spacing of the two axial rolling body axes, a gap is created between the two rolling bodies corresponding to one another which a friction ring is arranged such that the friction ring surrounds one of the rolling elements and rotates about this.

[08] For the purposes of the present invention, the term "friction ring" means a device by means of which a contact is made between the two rolling elements, so that forces, in particular torques, can be transmitted from one rolling element to the other rolling elements A preferred embodiment of the friction ring provides that the friction ring, as already indicated above, travels back and forth between the two rolling elements in a gap and is in contact with both rolling elements, the friction ring encompassing one of the two rolling elements arranged inside the ring.

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

The term "axial guide means" means any device which is adapted to support the Verstellbrücke in the friction ring gear such that the Verstellbrücke in the region of an adjustment axially along the axial Wälzkörperachsen and thus also axially along the gap verla¬ The axial guide device is configured in such a way that, moreover, only one rotation about the adjustment path in this plane is possible be sufficient if the adjusting bridge is sufficiently fixed with respect to the rotation or with respect to a shift in this plane, for example by the friction ring itself. [1 l] The object of the invention is also independent of the other features vorlie¬ gender invention of a friction gear with two spaced from each other by a gap Wälz¬ body solved, the corresonding on axial Wälzkörperachsen circumferentially via a friction ring with each other, at in which the friction ring is arranged to be displaceable axially in an axially freely displaceable adjusting bridge about an adjustment path along the gap, and the adjustment bridge is mounted axially only on one side with respect to a surface predetermined by the rolling body axes.

The term "surface predetermined by the rolling body axes" is understood essentially to mean a plane which is spanned by the two rolling body axes and which at least fictitiously divides the friction-ring transmission into a first and a second side.

Due to the fact that the adjusting bridge is mounted axially only on one side with respect to a surface predetermined by the roller body axis, the overall arrangement can be substantially smaller and thus considerable space can be saved.

[14] In connection with the adjustment bridge arranged on one side with respect to the predetermined surface, it is likewise advantageous if the adjustment bridge is mounted by means of a single axial guide device. It is understood that the adjustment bridge can also be mounted on a plurality of axial guide means, but in this case the risk of tilting the Verstellbrücke is increased in a guide by more than one axial guide means in connection with the unilaterally provided axial guide means. Thus, a single axial guide device is also advantageous in connexion with an adjustment bridge which is mounted axially only on one side with respect to a surface predetermined by the rolling body axes.

[15] In addition, the object of the invention is also achieved without the other features of the present invention by a friction ring gear having two rolling bodies spaced apart from each other by a gap and corresponding to axial rolling body axes circumferentially via a friction ring, in which the friction ring is in one axially freely displaceable adjusting is arranged displaceable axially displaceable by an adjustment axially along the gap, and which is characterized in that a rotation axis of a cage is arranged on one side with respect to a predetermined by the Wälzkörperachsen surface.

Previously, the axis of rotation of a cage was arranged in a plane spanned by the Wälzkörperachsen plane. However, in order to be able to interpret and tune application-related forces that occur during the change in the angle of incidence of the friction rim on the axis of rotation, it is advantageous if the axis of rotation of the cage deviates from this on one side of that predetermined by the rolling body axes Surface or plane is arranged. In this solution, the cage rotation axis is se then arranged laterally of a plane extending substantially perpendicular to the friction ring plane. In particular, such adjustability of the axis of rotation makes it possible to specify the adjustability of the angle of attack depending on the application, coarser or more finely.

An alternative to this provides that a rotation axis of a cage is arranged outside the adjustment of the adjustment bridge. In particular, an arrangement of the axis of rotation outside the Verstellbe¬ rich guaranteed almost arbitrarily selectable lever lengths.

It is understood that the cage rotation axis but also both the side of the plane defined by the Wälzkörperachsen plane and outside the adjustment can be provided.

[19] By means of the above-described different positions of the axis of rotation can be realized independently of the other features of the friction ring, in a small space as large as possible paths for the driving drives, whereby the control is effective and errors are minimized.

The object of the invention is also independent of the other features of the present invention of a friction ring gear with two spaced from each other by a gap rolling elements solved, which correspond to axial Wälzkörperachsen circumferentially via a friction ring with each other, wherein the friction ring in a cage in a axially freely guided Verstellbrücke is arranged displaceable axially about an adjustment along the gap, and the adjustment is mounted on the cage by means of a single axial guide means.

[21] Advantageously, the adjustment bridge is thus movably arranged in a cage provided for this purpose, so that the adjustment bridge can only move axially back and forth along the axial guide device, depending on how the cage is set against the axial rolling body axes.

[22] In the present case, the term "cage" designates an assembly which carries the adjustment bridge, and the assembly additionally allows the adjustment bridge to follow the movement of the friction ring along the rolling body surface, in particular, the cage thus structurally needs a cage in the strict sense For example, depending on the design, a simple axial guide axis, on which the adjusting bridge is mounted, can constitute a cage in the sense of the invention.

[23] As explained above, the axial guide device causes an axial guidance of the adjusting bridge. Such an axial guidance can be realized structurally particularly simply by mounting the displacement bridge only via a guide rod. Thus, for the adjustment bridge, a grading certainly realized. The guide rod also forms a particularly simple constructed axial Füh¬ tion axis.

[24] In connection with a cage in which a Verstellbrücke is performed, the object of the invention is also achieved independently of the other features of the invention of a friction ring gear with two spaced from each other by a gap rolling elements, on the axial Wälzkörperachsen encircling a friction ring correspond to each other, in which the friction ring in a cage axially axially guided Verstellbrücke axially displaceable ange¬ arranged by an adjustment axially along the gap, and the adjusting is mounted axially only on one side with respect to a predetermined by the Wälzkörperach¬ sen surface.

[25] With regard to this specific solution, as already explained above, it is also advantageous if the adjusting bridge is mounted on a single axial guide device.

[26] In order to limit the displacement of the axial guide means, it is advantageous if the Reib¬ ring gear has an axial guide means which has means for limiting the axial Ver¬ adjustment path.

Structurally particularly simple such limiting means are formed when the limiting means are directed approximately transversely to the axially extending displacement component groups, such as cross-struts of a cage.

[28] In order to prevent the adjusting bridge from carrying out a rotational movement about the axial guide device or about the guide rod of the axial guide device, it is advantageous if the friction-ring gear has an anti-rotation device which rotates the adjusting bridge around a guide axis of an axial guide device in derogation.

[29] This rotation lock can be ensured by a separate guide device or by profiling the guide rod of Axialführung.

[30] Especially with the latter, it is advantageous if an axial guide device has an internal anti-rotation device.

[3 I] However, in order to be able to take up especially very high occurring moments particularly favorably on the adjustment bridge, it is advantageous if a rotation lock is arranged at a distance from a guide device. In particular, the anti-rotation device on the other side of the surface or plane, which is spanned by the Wälzkörperachsen than that on which the axial Führungsseinrich- tion is provided, be arranged. There, the anti-rotation takes no space required for an axial guide device space or at least less space than an axial guide device and yet can withstand high torques. In this respect, such an arrangement is particularly small and, since the risk of tilting is minimized, particularly safe to operate. Accordingly, the separate arrangement of axial guide and rotation lock on each side of the plane spanned by the Wälzkör¬ peraxals also independent of the other features of the present invention is advantageous.

[32] It is also advantageous for receiving particularly high forces, in particular moments, when the anti-rotation device is arranged on a housing of the friction-ring transmission.

[33] A variant embodiment provides that the anti-rotation device has a holding rail for holding the displacement bridge. By means of the retaining rail, the adjusting bridge finds an additional hold on the transmission housing independently of the guide device.

[34] If the retaining rail is free of axial limiting means, the adjustment bridge is particularly easy to install. Because the anti-rotation device is only intended to prevent the adjustment bridge from rotating about the axial guide device, axial limiting means are superfluous. Derarti¬ ge limiting means generally has the axial guide device itself.

[35] On the other hand, the axial limiting means can also be provided exclusively in the area of the rotational locking, in order to be able to apply large torques or restoring moments or opposing forces as a result of the distance to the axial guide device.

[36] An alternative embodiment variant provides that the holding rail and the guide axis of the guide device are identical. As a result, the axially guided adjustment bridge is structurally particularly simple.

It is understood that the structural separation of rotation lock and axial guide, in particular on different sides of a plane spanned by the Wälzkörperachsen plane is also independent of the other features of the present invention in a friction ring transmission advantageous.

[38] Furthermore, it is proposed that a guide axle or a cage of the friction-ring transmission have an elastic bearing device in relation to a housing of the friction-bearing transmission. By means of the elastic bearing device, hysteresis-free control of the positioning bridge or of the cage can be realized advantageously. [39] Such an elastic bearing can also be realized in a small or cost-effective manner in comparison to other bearing types, in particular in comparison with the rolling bearings known from the prior art. With a suitable arrangement of the elastic elements of the elastic bearing device can be ensured that the cage is biased by the elastic elements in the direction of a safety position, so that, for example, in case of malfunction of the cage adjustment of the cage is automatically shifted to the safety position. This also applies with regard to a Verstellbrü¬ bridge, which is not additionally stored in a cage, but directly to a guide axis of a guide device.

[4O] As elastic bearing devices, rubber elements, but also steel springs, such as leaf springs, can be used to advantage. Rubber elements and steel springs have good elastic properties and are simple and inexpensive to produce.

By suitable design or arrangement of the elastic elements can be ensured in terms of undesirable degrees of freedom extremely cost sufficient stability. On the other hand, other guide elements or drive elements can be used.

[42] In this context, it is advantageous if the cage is made of a sheet metal body. A sheet metal body can be structurally designed so that it is characterized in certain areas by particularly good spring properties, so that by means of the sheet metal body advantageously an elastic Lagerein¬ direction is provided.

[43] Preferably, the sheet metal body has at least one fastening region and an elastic region, wherein the elastic region is more elastic than the fastening region and provides an elastic bearing device. The fastening area can then be designed, in particular with regard to the degree of freedom of the bearing device, in particular more stable or stiffer.

[44] An elastic bearing device operating both axially and radially with respect to the rolling body axes is constructed particularly simply if the sheet metal body is rotated in the region of the elastic bearing device about its neutral fiber, preferably rotated by 90 °.

It is understood that the elastic bearing device is also independent of the other features of the present invention for a friction ring gear in which a cage or a similar arrangement must be adjusted in its angle in order to shift the friction ring, is advantageous.

[46] Cumulatively or alternatively, as well as independently of the other features of the invention, it is advantageous if a friction-ring transmission with two rolling bodies spaced apart from each other by a gap, which correspond to one another axially on a rolling friction ring on an axial guide device, such as in a cage axially displaceable Verstellbrü¬ by an adjustment axially along the gap, wherein the axial Führungs¬ device or the Cage can be displaced via a linkage and wherein the axial guide device or the cage is mounted by means of a bearing device with a Bewegungsaus¬ equal to a housing.

[47] By means of the compensation of movement is structurally particularly simple length compensation of Lagerein¬ direction, in particular also an elastic bearing device realized, so that, for example, Dehnun¬ conditions of the components due to temperature fluctuations are compensated advantageous. This is advantageous in particular in the case of movable components, since stresses in components or in components corresponding to one another are prevented by such a length compensation or movement compensation. In addition, by such a length compensation and larger adjustment can be realized via a lever arrangement without disturbing voltages occur. Optionally, such a length compensation can also be done directly by a suitable storage.

[48] In order to provide such a length compensation, it is advantageous if the Bewegungsaus¬ equal to a bearing bush, a plate spring and / or a rubber bushing comprises.

[49] For example, the guide shaft can be mounted axially displaceable in the bearing bush, wherein the bearing bush corresponds to the guide axis such that between the guide shaft and the bearing bush no or only a very small radial clearance is present.

[5O] In order to enable a tilting of the guide axis relative to the bearing bush, a plate spring can cumulatively be provided on the guide axis in the region of the bearing bush. The cup spring guarantees tilting with minimal radial play between the guide axis and the bearing bush.

[51] Alternatively or cumulatively to the disc spring, other means such as a rubber bushing may be provided. By means of the rubber bush, the risk of excessive radial clearance between the guide shaft and the bearing bush is further reduced, since such a rubber bushing can also be configured radially very tight, but at the same time also tilting of the guide shaft relative to the bearing bush is possible.

[52] Such a bearing device is also advantageous independently of the other features of the present invention, since with this device a cost-effective, structurally simple and space-saving elastic suspension is possible. tion for the cage which supports an adjusting bridge, for example on a housing, in a friction ring gear mechanism. In particular, it can be ensured with a suitable arrangement of the elastic elements that the cage is biased by the elastic elements in the direction of a Sicherheitssposi¬ tion, so that automatically displaced in the event of malfunction of the cage adjustment of the cage in the safety position.

[53] While it is known from the prior art to specify the angle of incidence of the friction ring on the position of the cage, is cumulative or alternatively to the arrangements mentioned herein a Reib¬ ring gear with a friction ring and two revolving around Wälzkörperachsen, from one another Gap spaced arranged rolling elements advantageous in which the friction ring along the gap due to the rotation of the friction ring and the rolling elements in dependence on an angle bezüg¬ Lich the gap displaced and hinged in its angle of attack via an adjustment that the friction ring to at least two bearings stores and which is characterized in that at least one bearing point of the friction ring with respect to the adjustment bridge and / or with respect to a further bearing point of the friction ring is arranged displaceably. Such a bearing can be provided in particular in a conical friction ring gear with cones rotating around cone axes.

By such an adjustment, which ultimately corresponds to the friction ring of a displacement of the bearings and thus a corresponding apparent displacement of the adjustment, the friction ring can be moved in its angle without a movable cage must be provided. In this respect, a cage fixed with respect to a housing can be provided, as a result of which it can be made substantially more cost-effective and reliably builds the overall arrangement.

It is understood that the displaceable bearing point can be realized constructively in different ways. One embodiment variant provides for an articulated adjusting bridge, in which two bearing points of the friction ring are arranged so as to be displaceable relative to one another on the adjusting bridge by a hinge.

[56] Should the adjustment bridge not be designed to be articulated, in particular by means of a joint between two bearing points, a preferred embodiment provides that a bearing point is displaceably guided on a linkage arrangement. Preferably, in this embodiment, the link arrangement is arranged on the adjusting bridge so that the linkage arrangement of the adjusting bridge can easily follow. [57] It is advantageous if the link arrangement has both a first group of components consisting of a link with slide grooves and a link plate and a second component group of sliding blocks. By such a link arrangement, the movable bearing is guided safely and easily.

[58] In a preferred embodiment, the linkage arrangement is at least partially a constituent part of the adjustment bridge. Preferably, the slide grooves are ummittelbar recessed in the adjustment, whereby the slide assembly is particularly compact and easily builds by the slide grooves as Materi¬ alaussparungen. Within the gate grooves then the sliding blocks are placed, the sliding blocks on the one hand by means of suitable facilities, the rollers, which correspond to both sides of the friction ring hold. On the other hand, the sliding blocks are connected to the guide plate, to which in turn a ring follower can be attached. Due to the selected link arrangement, the ring follower is guided via the link plate and the sliding blocks in or on the slide grooves and at the same time mounted axially displaceably on the adjusting bridge. As a result, the ring follower can be moved to an axial along the axial guide axis. On the other hand, the ring follower is additionally guided transversely to the guide axis in the guide grooves.

[59] Since, in particular, a displaceable bearing point of the friction ring in a friction-ring gearbox is structurally simple, in particular by means of the present link arrangement, all features which are related to the linkage arrangement are also advantageous independently of the other features of the invention.

[60] But even the displaceable bearing point, which does not require the described link arrangement on which the friction ring is mounted, stores alone for a friction ring advantageous to a Ver¬ bridge and is therefore also without the other features of the invention advantageous.

[61] In addition, independently of the other features of the present invention, the invention is also achieved by a friction-ring transmission with two rolling elements spaced apart from each other by a gap, which correspond to each other on axial rolling-element axes via a friction ring, in which the friction ring is in one axially displaceable adjusting bridge is arranged displaceable axially displaceable by an adjustment along the gap, wherein means for deflecting a displaceable bearing point with which the displaceable bearing point is deflected by a zero axis from a zero position.

By the deflection means for the movable bearing point, it is possible to an operating state of the

To select the friction-ring transmission, so that the friction ring of the friction-ring transmission, including the adjustment bridge, follows the deflection of the deflection means until the displaceable bearing point has again reached a zero position on the zero-axis. Thus, the friction ring does not follow a positively driven adjustment bridge, but the adjusting bridge follows the friction ring. As a result, a self-adjusting adjustment system is created, which autonomously moves into an emergency running position, in particular in the case of a fault. Thus, emergency running properties of the friction-ring transmission are advantageously predetermined, so that the reliability of the friction-transmission is further increased.

[63] In order to be able to deflect a displaceable bearing point from a zero axis from a zero position, it is advantageous if the sliding blocks are arranged displaceably in guide grooves approximately transversely to the zero axis. Through the sliding blocks in the slide grooves ensures that the movable bearing is fixed but at the same time also deflectable arranged on the adjustment bridge. It is understood that the displaceable bearing point can also be attached to the adjustment bridge with other devices such that the displaceable bearing point can be deflected from a zero axis from a zero position.

[64] In this context, it is advantageous if the means for deflecting have an actuating lever. The adjusting lever is preferably of the shape that with it the ring follower can be brought into different positions, which lie next to the zero axis. For this purpose, the ring follower relative to the actuating lever is relatively displaceable.

[65] In order to bring about a deflection of the ring follower from a zero position of the zero axis by means of the adjusting lever, it is advantageous if the adjusting lever is mounted eccentrically to the zero axis. By means of the eccentrically mounted actuating lever, the displaceable bearing point can be particularly easily deflected on a zero axis.

[66] In connection with the use of a control lever, it is advantageous if a zero position is located at an intersection of the zero axis and a longitudinal axis of the control lever.

[67] The friction ring or the adjusting bridge can communicate with the deflection means in a structurally simple manner if the deflection means have a receptacle for a ring follower. The ring follower is in the present sense a component of the displaceable bearing point and preferably fastened to a link plate, so that a deflection of a deflection means, such as a control lever, can be transmitted directly to the ring follower.

[68] It is advantageous if the ring follower receptacle has a guide groove. The ring follower can easily move back and forth in the guide groove. The ring follower is thus arranged relative to the deflection means relatively movable. [69] One embodiment provides that the guide groove is configured in a straight line. But also curved or otherwise shaped guide grooves can be used.

[70] If the displaceable bearing point in connection with a link arrangement, it is advantageous if the ring follower is arranged on the link plate. The ring follower is in this case able, together with the link plate and the sliding blocks in the slide grooves, to be displaced transversely to the zero axis.

[71] Advantageously, the deflection means are mounted on a housing of the friction ring gear and thus fixed in place.

[72] In order for the friction-ring transmission to be relatively compact overall, it is advantageous if the zero-axis extends substantially parallel to the gap of the axial guide device.

[73] The object of the invention is also achieved cumulatively or alternatively by a friction ring transmission with two rolling bodies spaced apart from each other by a gap, which correspond to each other on axial rolling body axes via a friction ring, in which the friction ring is axially free displaceable adjusting bridge is disposed axially displaceable about an adjustment axially along the gap, wherein means for deflecting a displaceable bearing point are provided, with which the displaceable bearing point, which was deflected from a zero axis from a first zero position, in a further zero Position of a zero axis is deflected.

[74] Advantageously, a friction ring moves automatically by deflection of the displaceable bearing point in a zero position and thus in a rest position of the friction ring when a corresponding desired position is reached.

In the sense of the invention, the term "rest position" of the friction ring is understood to mean a position in which the friction ring can rotate about its axis of rotation, but does not perform a translational movement approximately in the direction of an axial guide axis.

[76] In this case, the term "zero axis" is understood to mean an axis along which a displaceable bearing point can move approximately translationally, but the displaceable bearing point only moves along the zero axis when, as described above, the bearing axis moves Ring follower is deflected from a zero position of the zero axis, and only until the ring follower has returned to a zero position of the zero axis. [77] A preferred embodiment variant provides that the deflection means of the displaceable bearing point have the friction ring. In this selected embodiment, the friction ring is the Einlenkmittel the movable bearing. Forms the friction ring itself the Einlenkmittel, builds the friction ring gear very compact, since further means for realizing the Einlenkmittel are not needed. Advantageously, the susceptibility of the present friction-bearing transmission is further reduced in such a variant, since it is possible to dispense with additional components in which a fault could occur. Due to the mentioned advantages, such Einlenkmittel are also independent of the other features of the present invention advantageous.

[78] Also independent of the other features, the object of the invention of a friction ring gear with two spaced from each other by a gap rolling elements, which correspond to axial Wälzkör¬ peraxially around a friction ring with each other, solved, in which the friction ring in an axial freely displaceable adjusting bridge is disposed displaceably axially displaceable by an adjustment along the gap, wherein the friction ring along the gap due to the rotation of the friction ring and the rolling elements in dependence on a setting angle with respect to the gap is displaced and which is characterized in that the Adjusting bridge, optionally via a cage, by means of a linear drive with at least one solenoid for setting the angle of attack can be controlled.

By means of the solenoids as a linear drive, the number of Ge¬ required for driving Ge drive elements, taking into account a sufficient translation between a Verstellbrückenan¬ drive and the adjustment bridge minimize, which increases the accuracy of the control by reducing the possible game. In addition, the use of lifting magnet has the advantage that they work extremely low loss and in itself with little play.

For a particularly exact setting of the cage, a further embodiment provides that the friction ring gear has a linear drive with an adjustment axis, which parallel to the axial Füh¬ tion device and / or to a surface which is formed by two Wälzkörperachsen, runs.

[81] In order for the adjusting bridge drive based on lifting magnets to be particularly simple, it is advantageous if the friction-ring gearbox has a linear drive with an adjusting axis which is parallel to the axial guiding device and / or to a surface which is formed by two rolling-element axes , runs.

[82] The operational reliability of the friction ring gear is further increased if the linear drive has more than one linear drive motor. With more than one linear drive motor is a particularly safe Provided drive so that the angle of the friction ring can still be reliably adjusted even if a linear drive motor fails.

In the present case, preferably two oppositely operating lifting magnets are used, so that it is ensured that all conceivable and necessary cage positions can also be selectively controlled.

[84] In order to be able to make advantageous in particular smallest changes in the angle of attack, it is proposed that the linear drive has a pulse-pause control. The length of the pulses or the pulse-pause control as well as the frequency make it possible to implement a desired deflection or friction ring adjustment in a particularly simple manner.

In particular, inertial effects and counterforces by springs or other magnets or drives can additionally be used accordingly in order to be able to realize a desired deflection of the friction ring.

[86] Cumulatively or alternatively for solving the object of the present invention, regardless of the other features, a friction ring transmission with two Wälzkör- pern spaced apart from each other by a gap, which correspond in the axial Wälzkörperachsen circumferentially via a friction ring with each other, vor¬ beaten, in which the friction ring in an axially freely displaceable adjusting bridge about a Verstell¬ path axially along the gap is arranged to be displaceable, wherein at least one end of the Verstell¬ path is a Verstellwegbegrenzung for the axially freely displaceable Verstellbrücke is arranged.

[87] By means of the proposed Verstellwegbegrenzung a possibility is created, the axially freely displaceable Verstellbrücke in terms of your adjustment so narrow that they even in a

Malfunction is adjusted non-destructively in a predetermined position. It is understood that such Verstellwegbegrenzung can be realized in many ways. It is possible, for example, to electronically realize the adjustment travel limit, in which sensors determine or determine the position of the axially freely displaceable adjustment bridge, and the adjustment bridge is correspondingly displaced on the basis of the data obtained.

[88] A preferred embodiment variant provides for a mechanically acting displacement limitation, since with regard to the present invention, this can be designed to be less susceptible to interference.

[89] In particular, the Verstellwegbegrenzung respect to different directions of rotation of the

To adjust friction ring, it is advantageous if the Verstellwegbegrenzung has an adjustable end stop. Depending on the direction of rotation of the friction ring, the adjustable end stop can be in one be brought favorable position. Otherwise, the position of the friction rings in the narrow limits of an adjustable stop can be adjusted by the adjustable end stop so that, for example, starting operations for the engine can be facilitated, even if the transmission itself has failed.

[90] In order to move as few masses in terms of the adjustable end stop, it is advantageous if the adjustable end stop has a displaceable Endanschlagsbolzen, which then only needs to be moved.

[9I] Depending on the embodiment, it is advantageous if the displaceable end stop bolt is arranged axially movable in relation to the axial guide device. Due to this axial displaceability with respect to the axial guide device, it is also possible to shorten or extend the adjustment path, depending on which setting is required.

In particular, when the adjustable end stop has a direction-dependent freewheel, which displaces the Endanschlagsbolzen depending on the direction of rotation of the friction ring, it is advantageous if the displaceable Endanschlagsbolzen is arranged axially movable to the axial guide means on the adjustable end stop.

[93] Should it be provided that the adjustable end stop does not have such a freewheel, the adjustment of the end stop or the displacement of the end stop pin is constructively achieved simply by the displaceable end stop having a rotary magnet. In the present case, the rotary magnet can be connected to the displaceable end stop bolt in such a way that the displaceable end stop bolt is arranged to be axially movable relative to the axial guide device.

An axial mobility of the displaceable Endanschlagsbolzens is structurally particularly ge ge guaranteed if between the displaceable Endanschlagsbolzen and a rotary magnet An¬ adjusting disc for adjusting the displaceable Endanschlagsbolzens is arranged. For example, to adjust the displaceable Endanschlagsbolzens the positioning in the contact area to verlagerba- ren end stop bolt with different thickness with respect to their circumference, so that are positioned at a rotation of the adjusting depending on the position of the adjusting in this contact area of different thickness Berei¬ surface of the adjusting. The adjusting disk thus has a first thickness in a first setting position, so that the displaceable end stop bolt is brought into a first position with respect to the adjusting path. In contrast, the adjusting disc, turned into a further setting position, has, in the area of contact with the end stop bolt, a second thickness different from the first thickness, so that the end stop pin is set in a second position relative to the adjusting path. The object is also independent of the other features of the invention of a Reibring¬ with two spaced apart from each other by a gap rolling elements, the axes on axial Wälzkörper¬ circumferentially by a friction ring with each other, solved, in which a Anpressein¬ direction for Setting a contact force between the rolling elements comprises a pressure regulating device with static and dynamic pressure regulating means, wherein the dynamic Druckreguliermit¬ tel are mounted relative to the static pressure regulating means displaceable on one of the rolling elements.

[96] Friction-ring transmissions, in which a pressing device sets the contact pressure between rolling elements or between rolling elements and a friction ring, in particular by means of a hydraulically operating pressure regulating device, are already known from the prior art. For example, WO 2004/06 1336 A1 describes a hydraulic pressing device for clamping two friction cones, which interact with one another via an adjustable friction ring. In one of these friction cone, the output cone, the pressing device is arranged, which is actuated by means of a hydraulic pressure via a hydraulic line. Depending on how much pressure is applied to the pressing device, a corresponding contact force between the friction cones or between the friction cones and the friction ring. By means of a pressing device positioned and acting in this way, different friction conditions between the friction cones and the friction ring can be set structurally simple and thus advantageous.

[97] By means of the present pressing device with a pressure regulating device, in which dynamic pressure regulating means are arranged within a rolling element, that is to say within a friction cone, it is possible to constructively optimize known pressure regulating devices and pressing devices known therefrom constructively. In particular, due to the fact that the dynamic Druckregulier¬ medium of the pressure regulating device is mounted displaceably in one of the rolling elements, the Anpress¬ device is particularly compact.

[98] In this context, the term "dynamic pressure regulating" refers to assemblies that are moved to build up pressure accordingly, while the term "static Druckregu¬ liermittel" called assemblies that are stationary and against which the dynamic Druckregulier¬ medium support to build up the pressure.

[99] A preferred embodiment provides that the dynamic pressure regulating means are mounted on a supplementary shaft of a rolling element, which is at least partially disposed within the rolling body. Often, in such a supplementary shaft, an oil pressure line for controlling an oil pressure in the pressing device is incorporated or incorporated, so that the dynamic pressure regulating means via this oil pressure line the oil pressure of the pressing device directly on or in the oil can adjust the pressure line. Thus, it is possible to dispense with an external pressure regulating device, which takes up additional space on a friction ring transmission. By means of the inventive pressure regulator, a friction-ring transmission is also advantageously further formed independently of the other features of the invention.

[100] In contrast to the above-described storage of the dynamic pressure regulating, it is advantageous if the static pressure regulating means are arranged on a further, the rolling elements foreign component of the friction ring gear. For example, the static pressure regulating means are fixedly secured to the friction-ring gearbox so that the static pressure-regulating means are fixed in the friction-ring gear fixed to the housing and the dynamic pressure-regulating means can shift relative to the static pressure-regulating means.

Structurally particularly simple, the dynamic pressure regulating means can be displaceably arranged in one of the rolling bodies or in a supplementary shaft of one of the rolling bodies, if the dynamic pressure regulating means comprise a piston rotating with a rolling body, which can be excited by the static pressure regulating means.

[102] A preferred embodiment variant provides that the static pressure regulating means comprise a lifting magnet. By means of the solenoid, it is possible in the smallest space to move the rotating piston with the rolling elements very easy and build up a pressure.

Particularly advantageous and reliable, such a rotating piston can be excited by the Hubmag¬ neten when the rotating piston has a magnetic pin which is disposed within the solenoid. In this case, the pin preferably passes without contact within the lifting magnet and is moved by corresponding electromagnetic pulses within the solenoid, so that can be set by means of the rotating piston different pressure conditions with respect to the pressing device. The circulating piston is moved axially, for example, along a Wälzkör¬ perachse, around which the Wälzköper having the pressing device rotates.

Further features, which also solve the problem of a friction ring gear independently of the other features of the present invention, a friction ring with two voneinan¬ spaced by a gap rolling elements which correspond to each other on axial Wälzkörperachsen circumferentially via a friction ring, at which the friction ring is arranged to be displaceable axially in an axially freely displaceable adjusting bridge about an adjustment path along the gap, and the friction ring has a split running surface. [105] The fact that the running surface of the friction ring is divided, the stability of the friction ring with respect to tilting moments with respect to the gap between the two rolling elements can be improved, since the split tread with the same surface pressure larger levers can be realized. It is understood that the tread may additionally have grooves regardless of the gap, which serve a better fluid distribution and an adjustment of the surface pressure.

It is also advantageous if the divided running surface has a gap which divides the running surface into a first running surface half and into a further running surface half with a gap width which is at least 10% of the width of the friction ring, preferably at least 10% Width of the effective Laufflä¬ che, is.

[107] In the present case, the term "gap" is not to be equated with the term "groove" or "creases", since the running surface in the region of the creases has a sufficiently large surface pressure against Wälzkör¬ pern to correspondingly high torques between the friction ring and the However, this is not possible for a region of the tread that comprises a gap, since the gap has such a geometry that no torque can be transmitted between the running surface of the friction ring and a rolling element in the region of the gap is therefore, depending on the traction fluids used, generally wider or deeper than a groove or groove.

In the context of the invention, the term "effective running surface" describes that running surface of the friction ring with which the friction ring is actually in contact or transmits torques to one of the rolling elements the width of the friction ring minus the gap width and chamfers according to the invention at the peripheral edge of the friction ring.

[109] The object of the invention is also achieved by a friction ring gear with two voneinan¬ spaced by a gap rolling elements, which correspond to axial Wälzkörperachsen circumferentially via a friction ring with each other, solved, in which the friction ring in an axially freely displaceable Verstellbrücke to an adjustment is arranged axially displaceable along the gap, and rolling elements are arranged Hauptkrafteinleitungsfrei in a friction-ring gear housing.

It has been found that it is advantageous if the rolling bodies are arranged in a friction ring gear housing in such a way that essentially primary forces which occur axially or radially between the rolling body axles when two rolling bodies are braced against one another are avoided if possible in the friction ring gear housing of the rolling body present friction gear, but previously be recorded. If the introduction of such primary forces into the friction ring housing is prevented, the rolling elements are loaded in the friction ring transmission housing in the direction of the invention, while the main forces can be absorbed, for example, by a separate frame.

[111] In such a case, the friction-ring gear housing only needs to absorb secondary forces, so that it can be built much more filigree and therefore also lighter. Secondary forces would be, for example, forces that can occur due to load change torques during operation.

[112] A preferred embodiment variant in this respect provides for at least one side of the rolling elements to be clamped to one another in a friction-roller bearing housing which is self-supporting by a friction-ring gearbox housing.

[113] In the context of the invention, the term "self-contained rolling element bearing device" is understood to mean any bearing device with which rolling elements can be clamped together and fixed relative to one another, at least when the transmission is at a standstill, independently of a friction-ring transmission housing.

It has been found that it is particularly advantageous if the roller bearing device has a steel frame. In particular by means of a steel frame, primary forces can be absorbed particularly well, since steel has a high strength. Steel frames can be inexpensively manufactured in particular as a sheet-metal construction in such a way that the rolling-element bearing device not only has high strength but also high rigidity.

[115] A preferred embodiment provides that the rolling elements are mounted on both sides with one another in self-sufficient rolling element bearing devices. If rolling elements are clamped together on both sides in autonomous rolling element bearing devices, such as steel frames, for example, the relief potential with regard to forces that would otherwise be introduced into the friction-ring gear housing is particularly great.

For further stiffening of Wälzkörperlagereinrichtungen it is advantageous if the self-contained Wälzkörperlagereinrichtungen, in particular by means of a steel frame, are interconnected. As a result, the actual housing can be further relieved. Of course, materials other than steel are also suitable for realizing such a frame.

[117] In order to be able to arrange the rolling elements in a stationary manner with respect to further gear elements of the friction-ring transmission, it is advantageous if the self-sufficient rolling-element bearing devices are arranged in the friction-ring transmission housing. By such an arrangement, in particular, the housing can be much easier and more filigree in its geometry, so that in this respect the space can be minimized. Nevertheless, sufficient stability and a high contact pressure between the rolling assemblies can be ensured by the roller bearing device.

[1 19] A further advantageous embodiment provides a friction-ring transmission with a differential gear, which is connected to the friction-ring transmission and also mounted in the rolling-element bearing device. Similar to two rolling elements, which can be very rigidly connected to each other by means of a self-contained Wälzkörperlagerein¬ direction, it is possible to additionally store a differential gear or gear members thereof against rolling elements in a Wälzkörperlagereinrichtung, such as the above-mentioned steel frame ,

[120] The gear members are then particularly particularly advantageous in terms of temperature fluctuations, since the steel frame has much more favorable expansion coefficients than, for example, a housing made of cast aluminum. In particular, overall the properties of the rolling element bearing device can be suitably adapted to the properties of the gear elements to be supported, without having to consider the housing, which can then be formed particularly easily and with a complex shape.

[121] Since the storage of rolling elements in autonomous Wälzkörperlagereinrichtungen, such as in a steel frame, further develop a friction ring gear, the features in terms of autarkic Wälzkörperlagereinrichtung are also independent of the other features of the present invention advantageous.

Moreover, it is advantageous if the rolling bodies of the friction-ring transmission, in particular the friction cones, the friction ring and / or provided rolling-element shafts, such as additional shafts of a friction cone, are made of steel or of the same material as the rolling-element bearing device. The material steel has the advantage that it has a very high strength and rigidity. Components or transmission components of the friction-ring transmission made of this are then particularly durable and resistant, as a result of which the operational reliability of the friction-ring transmission is further increased. Therefore, the features with respect to the steel-made components or gear members are also inde pendent of the other features of the invention advantageous.

In order for a torque which interacts with the friction-ring transmission not to be transmitted via stationary number wheels, as is the case in prior-art arrangements, a friction-ring transmission with two is also independent of the other features of the present invention from each other by a gap spaced rolling elements, which correspond to axial rolling elements circumferentially via a friction ring with each other, advantageous in which the friction ring in an axial freely verla¬ gerbaren Verstellbrücke axially displaceable by an adjustment along the gap, wherein at the friction ring a double planetary gear is arranged.

In addition, with the dual planetary gear, a reverse gear in the case of the present friction ring gear is realized in a structurally simple manner. The reverse gear can be realized in a small space and a minimum number of Gerherr members in interaction with the Vorgebe¬ by the friction ring gear nen directions of rotation.

[125] Also independent of the other features of the invention is a friction ring gear with two spaced from each other by a gap rolling elements, which correspond to axial Wälzkörperachsen umlau¬ fend via a friction ring with each other, advantageous in which the friction ring in an axially freely displaceable Verstellbrücke to a An adjustment of the adjusting bridge or a guide cage of the adjusting bridge on the one hand with a drive, such as with an eccentric motor, operatively connected and on the other hand at a neman pivot point of the adjusting bridge or the guide cage is mounted, and the Anlenker has an overload protection.

[126] In this way, the drive can be separated from the adjusting bridge or from the guide cage, in particular in the case of a malfunction, such as an overload, on the link, so that the adjusting bridge or the guide cage can follow a movement predetermined otherwise. In addition, a overload overload separate overload protection with appropriate Ausges¬ tion in case of need immediately after solving the problem quickly and uncomplicated again geschas¬ tet when the overload protection is located on the link.

[127] The overload protection is particularly well protected against external influences if the overload protection is arranged within the armature.

A structurally particularly simple embodiment in this context provides that the link has a tube in which the overload protection is arranged. It is understood that such an overload protection on the other hand can be realized constructively diverse.

[129] For example, a preferred embodiment provides that the overload safety device has destruction-free overload protection means. This has the advantage that, at least in the case of a slight overload, the overload protection is not destroyed directly, but the overload protection is at least minimized. ge overload compensated independently, so that after the overload operation of the transmission with respect to the axially displaceable adjusting bridge can be continued unaffected.

[130] In order to provide non-destructive overload protection means, it is advantageous if the overload protection comprises at least one pressure element and / or at least one tension element.

[131] As the term "pressure element" already indicates, the pressure element of the overload protection is intended to compensate for pressure peaks which act on the adjustment bridge, and thus also on the link, at least in a noncritical region.

[132] Accordingly, the "tension element" compensates uncritical tensile forces which occur between the displacement bridge and the drive.

[133] The overload protection is realized in a space-saving manner when the pressure element and the tension element are arranged displaceable relative to one another. Preferably, the pressure element and the tension element are at least partially interleaved and thereby displaced relative to each other, so that the Über¬ load protection is very compact.

To compensate for pressure or tensile forces, it is also advantageous, both the pressure element and the tension element relative to the armature are mounted displaceably.

[135] An advantageous bias receives the overload protection when the pressure element and / or the tension element are each biased with a fault element. By means of the bias, it is possible that neither the pressure element nor the tension element bear against a rigid stop, but that they can be displaced essentially along an armature axis in both directions.

[136] In the context of the present invention, the pressure element and / or the tension element are dynamically acting overload protection means. The overload protection means act dynamically because they are implemented by non-destructive overload protection means of the overload protection, whereby at least small, uncritical overload peaks can be compensated non-destructively.

[137] A structurally small construction variant provides that the tension element is mounted on a drive of the adjustment bridge or the guide cage of the adjustment bridge. Due to the fact that the tension element of the overload safety device is mounted directly on the drive, the need for further components for connecting the overload safety device to the adjustment bridge or the cage is eliminated. [138] Cumulatively or alternatively, it is proposed that the pressure element is mounted on the Verstellbrü¬ bridge or on the guide cage of the adjustment. By arranging the pressure element directly on the adjusting bridge or on the guide cage, additional additional components are also superfluous in this regard, so that the overload protection is realized with as few components as possible and is as compact as possible.

[139] It is understood that in a further embodiment, the tension element can be fastened directly to the adjustment bridge and the pressure element can be fastened directly to the drive of the adjustment bridge. As a result, the functional safety and the mode of operation of the overload protection remain unaffected.

[140] If very high overloads occur, it may be advantageous, independently of the other features of the present invention, if the overload protection has destructible overload protection means as a predetermined breaking point. This is advantageous in particular when the overload forces reach a critical area in such a way that they can no longer be compensated by the dynamically acting overload protection means.

[141] In contrast to the dynamically acting overload protection means, the predetermined breaking point in the sense of the invention is a statically acting overload protection means. This is destroyed after a trip, so it must be replaced before the overload protection is functional again.

[142] Furthermore, the object of the present invention, independently of the other features described here, is solved by a friction-ring transmission with two rolling elements spaced apart from each other by a gap, which correspond to each other on axial rolling-element axes via a friction ring, in which the friction ring axially displaceable axially along the gap in an axially freely displaceable adjusting bridge, and which is provided by means of a failover device with means for adjusting the adjusting bridge or a guide cage of the adjusting bridge in an emergency running position independent of a primary drive of the adjusting bridge or of the guide cage distinguished.

By fail-safe, it is possible to operate the present friction gear even if the prime mover of the adjusting bridge or the guide cage fails or works only disturbed. Thus, a fail-safe having Reibringsgetriebe is particularly reliable compared to conventional friction ring gears from the prior art. [144] It is particularly advantageous if the fail-safe mechanism represents a secondary drive for the adjusting bridge or for the guide cage. Due to the fail-safe as a secondary drive the adjusting bridge or the guide cage of the adjustment receives a redundant drive, wo¬ is further increased by the reliability of the friction ring gear.

[145] Structurally particularly simple and space-saving, the fail-safe mechanism in the friction-ring mechanism is realized if the fail-safe mechanism is arranged between the adjustment bridge and a primary drive of the adjustment bridge.

[146] In order for a primary drive which is not working properly to be decoupled from the adjustment bridge or the guide cage and the adjustment bridge or guide cage to be adjusted elsewhere, it is advantageous if the fail-safe device comprises a blocking / unlocking device for a force flow between the two Has Verstellbrücke and the prime mover.

It is understood that corresponding adjustment means of the adjustment bridge or of the guide cage, which serve for the above-described, other adjustment, can be implemented in a variety of ways. A particularly simple embodiment provides that the adjusting means have a cam disc and a cam follower rolling on it. Here, the cam follower is pressed by a spring element against the cam. By means of the cam follower, the cam disk can be "locked in" into an emergency running position by appropriate measures can then be realized without further notice that this locking takes place only in an emergency, for example by the cam sequences in the normal operating state is prevented from locking.

[148] Advantageously, when locking the cam follower, for example, in an emergency position between two cams of the cam disc is arranged. There, the cam follower remains so long and thereby blocks a rotation of the cam until the function of the prime mover is again made immaculate.

In order to be able to interrupt the power flow between a drive of the adjustment bridge and the adjustment bridge or the guide cage of the adjustment bridge, it is advantageous if the blocking / unlocking device for blocking a force flow is a release device, such as an electrically driven piston, and to unblock the power flow, an indenter, such as a spring element, has. In addition, the cam follower can be released by the releaser so that it can engage in the cam. For example, the releaser releases a first clutch disk an emergency clutch from the cam disk, which is a second clutch disk of the emergency clutch, so that the two clutch disks are separated from each other. The releaser displaces the first of the clutch discs away from the cam disc in such a way that it no longer blocks the cam follower, so that the cam disc rotates freely until the roller follower, which rolls on it, locks between two cams of the cam disc and fixes them in the emergency position.

[151] Once the primary drive has been restored, the releaser can be moved back to its original position and the first clutch disc can be displaced again in the direction of the cam disc by means of the spring element of the engagement member until the cam disc, ie the second clutch disc, interacts properly again with the first clutch disc.

[152] Further advantages, objects and features of the present invention will be described with reference to the following attached drawing in which friction-ring gears and component groups thereof are shown by way of example.

[153] It shows

FIG. 1 shows schematically a plan view of a cage with a leaf spring as an elastic bearing device of a friction-ring transmission,

FIG. 2 schematically shows a cross section of the cage from FIG. 1,

Figure 3 schematically shows a plan view of another cage with a rubber element as elastic

Bearing device of a friction gear,

FIG. 4 schematically shows a cross section of the further cage from FIG. 3,

FIG. 5 is a schematic plan view of a cage with an adjusting motor as an alternative elastic bearing device of a friction-ring transmission;

FIG. 6 schematically shows a cross section of the cage from FIG. 5,

FIG. 7 schematically shows a view of the connection between the adjusting motor and an axial guide axis of the cage from FIGS. 5 and 6,

8 shows schematically a perspective view of the embodiment according to the figures

5 to 7 alternative cage of a friction gear; Figure 9 is a schematic plan view of the cage and the adjustment bridge of Figure 8;

Figure 10 shows an alternative to the cage of Figure 9;

Figure 11 shows an alternative to the cages of Figures 9 and 10;

FIG. 12 shows a further alternative to the cages according to FIGS. 9 to 11;

FIG. 13 schematically shows a cross-section of a friction-ring transmission, in which one of the cages described above can be arranged, with regard to the sectional surface "I-1" from FIG. 14;

FIG. 14 schematically shows a plan view of the friction-ring transmission according to FIG. 13;

FIG. 15 schematically shows a longitudinal section through a vehicle drive for a front-wheel drive with a friction-ring transmission;

FIG. 16 schematically shows a representation of an adjustment bridge with regard to the sectional area "IV -

IV "of the friction-ring transmission of FIG. 15;

FIG. 17 schematically shows a detail of the adjusting bridge from FIG. 16 with regard to the sectional area "V - V";

Figure 18 schematically shows a longitudinal section through a rear wheel drive for a vehicle with a

friction-ring;

19 is a schematic plan view of a cage with a linkage arrangement of a friction ring drive;

FIG. 20 schematically shows a longitudinal section through the cage with the slide arrangement according to FIG. 19;

21 shows schematically a view of a concrete embodiment of a cage with a

Slotted arrangement according to Figures 19 and 20 in conjunction with friction cones from a first perspective;

FIG. 22 schematically shows a view of the concrete exemplary embodiment according to FIG. 21 without a friction cone from the first perspective; Figure 23 schematically shows a view of the concrete exemplary embodiment with friction rule according to the

Figures 21 and 22 from a further perspective;

FIG. 24 schematically shows a view of the concrete exemplary embodiment according to FIG. 22 without

Cone from the wider perspective;

FIG. 25 schematically shows a top view of the specific exemplary embodiment according to FIGS. 21 to

24 with friction cone from another perspective;

FIG. 26 schematically shows a plan view of the concrete exemplary embodiment according to FIG. 25

Cone from the wider perspective;

Figure 27 schematically shows a plan view of the concrete exemplary embodiment of Figures 21 to 26 with friction cone from a further perspective;

FIG. 28 schematically shows a plan view of the concrete exemplary embodiment according to FIG. 27 without

Cone from the wider perspective;

FIG. 29 schematically shows a view of the concrete exemplary embodiment according to FIGS. 21 to

28 with friction cone from another perspective;

FIG. 30 schematically shows the concrete exemplary embodiment from FIG. 29 without a friction cone,

FIG. 31 schematically shows a plan view of the concrete exemplary embodiment according to FIGS. 21 to

3027 without friction cone from a wider perspective;

FIG. 32 schematically shows the concrete exemplary embodiment from FIG. 31 friction cone from the further perspective;

FIG. 33 is a schematic plan view of a cage with a linear drive and a cage pivot axis arranged centrally with respect to the cage;

FIG. 34 schematically shows a plan view of a cage with a linear drive with respect to FIG

Cage outside the guide axis of the cage arranged axis of rotation;

FIG. 35 schematically shows a plan view of a further cage with a linear motor and a cage rotation axis arranged outside the cage basic body; FIG. 36 schematically shows a perspective view of a drive of an adjustable end stop;

FIG. 37 schematically shows a longitudinal section through the drive of the adjustable end stop of FIG. 36 in a first position;

Figure 38 schematically shows a longitudinal section through the drive of the adjustable end stop of the

Figure 36 in a second position;

FIG. 39 schematically shows a longitudinal section through an arrangement of two friction cones corresponding to each other;

FIG. 40 schematically shows a cross section of a two-sided friction ring between two friction cones;

Figure 41 schematically shows a friction ring gear with a friction ring gear housing made of aluminum and autarkic Reibkegellagereinrichtungen;

FIG. 42 schematically shows a perspective view of the friction-ring transmission housing from FIG. 41 in a first exploded view;

FIG. 43 schematically shows a perspective view of the friction-ring transmission housing from FIGS. 41 and 42 in a further exploded view;

FIG. 44 schematically shows a view of a friction-ring transmission with a double planetary gear arranged on the input side;

FIG. 45 schematically shows a view of a friction-ring transmission with a double planetary gear arranged on the output side;

FIG. 46 schematically shows a view of a guide cage for an adjustment bridge with an overload protection;

FIG. 47 schematically shows a view of the guide cage from FIG. 46 in a first sectional view;

FIG. 48 schematically shows a view of the guide cage from FIGS. 46 and 47 in a further sectional view; FIG. 49 schematically shows a longitudinal section through an alternative overload protection in a trailer;

FIG. 50 schematically shows a view of a deactivated failsafe with closed power flow;

FIG. 51 schematically shows the view of the deactivated fail-safe mechanism from FIG. 50 in cross-section;

FIG. 52 schematically shows a view of an activated failsafe with interrupted power flow and FIG

FIG. 53 schematically shows the view of the deactivated fail-safe mechanism from FIG. 52 in cross-section.

The arrangement 1 of the friction-ring transmission shown in FIG. 1 comprises, in particular, a cage 2, which is designed substantially as a sheet-metal body 3. Due to the construction of this sheet metal body 3, the cage 2 has a first elastic bearing device 4, a second elastic bearing device 5 and a third elastic bearing device 6. Holes 4A, 5A and 6A (numbered here only by way of example) are provided on each of its elastic bearing devices 4, 5 and 6 so that the cage 2 is screwed to a friction-ring transmission housing 8 via screw connections 7 (shown only by way of example with respect to FIG can be. In the present case, at least the first elastic bearing device 4 has a cross-sectional taper 9, so that the cage 2 can be pivoted about an axis of rotation 11 by means of a setting lever 10 in the plane of the paper of FIG. For this purpose, the adjusting lever 10 is articulated to the cage 2 by means of a Anstellhebelaufnahmeblechs 12. The adjusting lever 10 is moved in this embodiment for pivoting the cage 2 according to the double arrow 13 translationally back and forth.

[155] In addition, the arrangement 1 has an axial guide device 14, which is arranged in a U-shaped bent portion 15 of the cage 2 between a first leg 16 of the sheet metal body 3 and a second leg 17 of the sheet metal body 3. In the present case, the axial guide device 14 comprises a cylindrical guide axis 18, on which an adjusting bridge 19 can be moved freely in accordance with the directions of the double arrow 20. The axial guide device 14 is present in a structurally particularly simple manner, a one-sided axial guidance of the Verstellbrücke 19 within the cage 2. With the adjusting bridge 19, a friction ring 21, which establishes a connection between two rolling elements not shown here in a conventional manner, rotatably supported by means of a first roller holder 22 and a second roller holder 23. Accordingly, the second roller holder 23 constitutes a second bearing point in the sense of the invention. In the illustration according to FIG. 2, a first rolling body axis 24 of a first of the two rolling elements is shown schematically.

[157] In order to prevent the adjustment bridge 19 from rotating about the cylindrical guide axis 18, the adjustment bridge 19 has an anti-rotation device 25. The rotation lock 25 consists in this example of embodiment of an anti-rotation pin 26, which is a part of the Verstellbrücke 19. In addition, the rotation lock 25 has a running rail 27, in which the anti-rotation pin 26 can slide back and forth in accordance with the directions of the double arrow 20. The running rail 27 of the rotation lock 25 is fastened to the friction gear housing 8, so that larger forces can easily be absorbed by the rotation lock 25 and conducted into the friction-ring gear housing 8.

[158] In this exemplary embodiment, the rotation lock 25 is provided opposite the axial guide device 14, the axial guide device 14 being in the region of a first surface side

28 of a plane defined by the two Wälzkörperachsen surface 29 is disposed, while the Dreh¬ fuse 25 is disposed on a second surface side 30 of the surface 29. The adjusting bridge 19 is thus mounted axially only on a single surface side 28 with respect to the area 29 predetermined by the rolling body axes (here only the first rolling body axis 24 of the first rolling body).

The surface 29 is formed by means of and along the two Wälzkörperachsen, represented by the first Wälzkörperachse 24 of the first rolling element. The underlying surface here

29 and thus also the plane described by the surface 29 extends according to the representations of Figsu ren 1 and 2 at right angles to the paper plane. The surface 29 may also intersect the first surface 29 at an acute angle.

[160] Due to the one-sided mounting of the adjustment bridge 19, the risk is reduced that the Verstell¬ bridge 19 jammed in terms of two axial guide means and the proper function Funk¬ tion of the friction gear is no longer guaranteed or at least limited. Thus, by the single axial guide means 14 of the adjustment 19, the adjustment of the friction ring 21 hin¬ visibly an adjustment (not shown here for clarity) between the first leg 16 of the sheet metal body 3 and the second leg 17 of the sheet metal body 3 designed very reliable. The arrangement 101 of a friction-ring transmission shown in FIGS. 3 and 4 substantially comprises a cage 102 in which an adjustment bridge 119 is mounted by means of an axial guide device 114. With the adjustment bridge 119, a friction ring 121 is guided by means of a first roller holder 122 and a second roller holder 123. In order to prevent the adjustment bridge 119 from rotating relative to a guide axis 118 of the axial guide device 114, the adjustment bridge 119 has a rotation lock 125 which, with regard to the adjustment bridge 119, comprises an anti-rotation pin 126. The anti-rotation pin 126 corresponds to a running rail 127, which is attached to a friction-ring gear housing 108. In addition to the running rail 127, the cage 102 is also fastened in the friction-ring transmission housing 108. By contrast, the adjusting bridge 119 is mounted on the cage 102 only by means of the axial guide device 114. Thus, the adjustment bridge 119 is supported only by a single bearing on the cage 102. As a result, the risk of tilting the Verstellbrücke 119 with respect to the axial guide means 114 is almost completely excluded, so that the adjustment of the Reib¬ ring 121 against the mutually corresponding rolling elements (for clarity, not shown here) is designed particularly reliable.

[162] Also in this embodiment, the axial guide device 114 is only on a first surface side 128 with respect to a surface 129. The rotation lock 125, however, is located on a second surface side 130 of the surface 129. The surface 129 extends through and along the two Wälzkörperachsen the rolling elements not shown here, which can interact with each other by means of the friction ring 121. The surface 129 extends according to the illustrations of Figures 3 and 4 perpendicular to the plane of the paper. The surface 129 may also intersect the first surface 129 at an acute angle.

[163] The essential difference between the arrangement 1 according to FIGS. 1 and 2 and the arrangement 101 according to FIGS. 3 and 4 lies in the structure of the cages 2 and 102, in particular in the different elastic supports 4, 5, 6 or 104 of the two cages 2 and 102. The elastic bearing device 104 in the arrangement 101 is realized from a rubber element 140 with a fixed fastening core 141, via which the cage 102 corresponds to the friction-ring gear housing 108. By means of the rubber element 140 of the elastic bearing device 104, it is possible to adjust the cage 102 about an axis of rotation 111, so that the cage 102 can be adjusted along the axial guide device 114 by a different angle of attack.

[164] In order to be able to transmit required adjusting forces to the cage 102, a Anstellhebelaufhahmeblech 1 12 is provided on the cage 102, to which a Anstellhebel 1 10 is hinged. The hinged attachment lever 110 can be moved back and forth in accordance with the double arrow 113, as a result of which the cage 102 is rotated about the axis of rotation 111.

[165] The stability or degree of stability of the bearing of the cage 102 within the friction ring drive depends not only on the choice of material but also on the selected length 142 of the rubber element 140. If the length ratios of the rubber element 140 are suitably selected, the cage 102 will be found despite the elastic bearing device 104 sufficient support within the friction ring gear, so that a safe adjustment of the Verstellbrücke 119 and thus the friction ring 121 against rolling elements (the sake of clarity sake not explicitly shown here) and a sufficiently stable storage is guaranteed perpendicular to the degree of freedom required for this purpose.

The alternative arrangement 201 shown in FIGS. 5 to 7 in the region of a cage 202 of a friction ring gear has an adjusting motor 245 for realizing an elastic bearing device 204 for the cage 202, which has a gear arrangement 246 with a cylindrical guide axis 218 of an axial guide device 214 is coupled. In the present exemplary embodiment, the cylindrical guide axis 218 represents the actual cage 202 of the arrangement 201. The cylindrical guide axis 218 is reciprocated by means of the variable speed servomotor 245 and the gear arrangement 246, so that an adjustment bridge 219 is inserted relative to rolling elements (not shown) can be made.

[167] Also in this exemplary embodiment, the adjustment bridge 219 is mounted on one side on the axial guide device 214. As in the exemplary embodiments explained above, the adjusting bridge 219 has, in addition to the axial guide device 214, an anti-rotation device 225, which includes an anti-rotation pin 226 on the adjusting bridge side, which is slidably inserted within a running rail 227. The track rail 227 is mounted in a friction ring gear housing 208. The adjusting motor 245 and the side of the cage 202 which lies opposite the adjusting motor 245 are likewise fastened directly to the friction-ring transmission housing 208.

[168] A friction ring 221 is mounted on the adjusting bridge 219 itself, as is the case with the above-described exemplary embodiments. The friction ring 221 rotates about a rolling body axis 224. In order for the friction ring 221 to move correspondingly with respect to the adjustment bridge 219, the friction ring 221 is fastened rotatably to the adjustment bridge 219 by means of a first roller holder 222 and a second roller holder 223. As in the case of the two exemplary embodiments explained above, the adjusting bridge 219 is supported relative to the cage 202 only by means of a single axial guide device 214 within the friction gear housing 208. The one single axial guide device 214 is in this case on a first surface side 228 of the surface 229. The surface 229 is also in this embodiment essentially a plane which is spanned by two Wälzkörperachsen 224 two rolling elements. It extends according to the illustrations according to Figures 5 and 6 perpendicular to the paper plane. The surface 229 may also intersect the first surface 229 at an acute angle.

By means of such an arrangement 201, the adjustment bridge 219 is advantageously mounted axially only on one side 228 with respect to a surface 229 predetermined by the roller body axis 224. As a result, jamming of the adjusting bridge 219 on the axial guide device 214 of the cage 202 is prevented.

[170] In this exemplary embodiment, the elastic mounting 204 takes place via a leaf spring 248, which may for example also be formed integrally with the cage 202 with the guide axis 218. As can be seen immediately restoring forces can be applied by the elastic bearings of the Ausfüh¬ described above. With suitable implementation, these restoring forces can be chosen such that the cage or the adjusting bridge are brought into an emergency position by these restoring forces when the drive, for example the adjusting motor 245, fails.

[171] An alternative to the embodiment according to FIGS. 5 to 7 is shown in FIGS. 8 and 9. This corresponds essentially to the embodiment according to FIGS. 5 to 7, so that identical components are also numbered identically and are no longer explained explicitly. Here too, a friction ring 221 runs between two bevel friction wheels 252 and 253 of one of the conical friction wheels 252, 253 and is guided by an adjusting bridge 219, which in turn is mounted axially freely displaceably on a cage 202. However, the cage 202 or the guide axis 218 is not axially displaceable via a leaf spring but via a bearing bushing 248A, whereby it is ensured via a suitable bearing point that the guide axis 218 in the bearing bush 248A is radially zero or only extremely small But can tilt in the bushing 248A.

[172] With a plate spring 248B, as shown in FIG. 10, such a tilting can be implemented structurally particularly simply with minimal radial clearance. Also, instead of a tilting elastic rubber bush 248C (see Figure 11) are used.

[173] Moreover, in the arrangements according to FIGS. 8 to 11, a lever 246A mounted on the housing is provided, which can be driven by an eccentric motor, not shown in more detail, similar to the Verstellmo¬ gate 245. In addition, the guide axle 218 is mounted on the lever 246A so as to be rotatable about a bearing 249. In this respect, the lever 246A predetermines the movement and can be supported very accurately with only one rotational degree of freedom, while the bearing of the guide axis 218 can provide the corresponding compensation. This is a deviation from the Embodiment of Figures 5 to 7, in which the compensation is carried out essentially by a game between the guide shaft 218, the lever or the gear assembly 246 and the adjusting motor 245.

[174] The exemplary embodiment according to FIG. 12 also essentially corresponds to the aforementioned exemplary embodiment. However, in this embodiment, the bearing point for the guide shaft 218 is laid in the direction of the center of the cone. In this respect, in this arrangement, the pivot point for the Führungs¬ rod 218 and thus also for the cage 202 in a plane defined by the guide rod 218 and arranged parallel to the shaft axes level, resulting in extremely small deflections of the Führungsstan¬ 218 and the cage 202nd leads, whereby this arrangement consumes very little space. Preferably, the storage takes place within the guide axis 218, which is particularly space-saving. In the present embodiment, this is realized by a bearing head 248D, which is fastened to a rod 248E and rests in a bearing cup 248F, which in turn is arranged in the guide axis 218.

[175] The arrangements 1, 101 and 201 described above are also particularly suitable for being arranged on or in friction-ring gears according to FIGS. 13 to 18.

[176] The friction-ring gears illustrated in FIGS. 13 to 18 essentially consist of two conical-friction wheels 352 and 353 arranged on parallel rolling-element axles 350 and 351 at a radial distance, which are arranged in opposite directions and have the same cone angle β. Between the conical friction wheels 352 and 353, a friction ring bridging the radial distance 321 is arranged, which surrounds the first conical friction wheel 352 and is held in a cage 302. By the distance between the two conical friction wheels 352 and 353 so a gap 321 A is present.

[177] The cage 302 consists of a frame formed by two crossheads 354 and 355 and two parallel guide shafts 356 and 357 received therein. These guide shafts 356, 357 are arranged parallel to the conical friction wheel shafts 350 and 351 and at the same time to the generators of the conical friction wheels 352 and 353 inclined at the angle β and carry an adjusting bridge 319 with two cones 358 facing each other (numbered here only by way of example) which a first Rollen¬ holder 322 and a second roller holder 323 sit. The roller holders 322 and 323 engage on both sides of the friction ring 321 and give this the necessary axial guidance.

[178] The center of the crosshead 354 forms a vertical axis of rotation 311 about which the entire cage 302 is pivotable. For this purpose, the lower crosshead 355 is connected to a transverse drive 359 acting on it and not shown in detail, and to an adjusting motor 345. In this embodiment, the axis of rotation 311 lies in the area 329 defined by the bevel friction wheel shafts 350 and 351 of the conical friction wheels 352 and 353, which represents a plane. The surface 329 may also lie in a plane parallel thereto or intersect the first surface 329 at an acute angle.

[180] If the cage 302 is pivoted by a few angular degrees, the friction drive becomes an axial adjustment of the adjustment bridge 319 and thus a change in the transmission ratio of the conical friction wheels 352 and 353. For this purpose, a minute expenditure of energy is sufficient.

[181] The front wheel drive for a vehicle shown in FIG. 15 has a conical friction ring gear 360. The front-wheel drive consists essentially of a hydraulic converter or a fluid coupling 360, a downstream switching unit 361, the conical-friction-ring transmission 362 and an output 363.

[182] The drive member of the fluid coupling 360 is seated on a shaft 364, on which a brake disc 365 is disposed, which cooperates with the Kegelreibringgehäuse 308 held brake shoes 366 and is electronically controlled. Immediately behind the brake disk 365 sits a freewheeling gear 367, which is in engagement with a countershaft 368 only partially shown and can cause the reverse gear in the output 363. The gear 367 has on one side a Kronenver¬ toothing, with which it can be brought into engagement with a held on the shaft 364 and axially displaceable, an inner axial toothing aufeisenden sliding sleeve 369 and activated.

[183] If a reversal of the direction of rotation is desired, first the brake consisting of brake disk 365 and brake shoes 366 is actuated, so that the following transmission is not affected by the torque impulse. The shift sleeve 369 in FIG. 15 is then moved to the right from its neutral position shown there and engages with a pinion 370, which is fixedly connected to the drive shaft 371 of the bevel friction wheel 353 of the conical friction ring transmission 362.

The conical friction ring transmission 362, as also described with reference to FIGS. 13 and 14, consists of two conical friction wheels 352 and 353 with the same cone angle and parallel axes arranged opposite one another and at a radial distance from each other. Furthermore, the first conical friction wheel 352 (here the upper conical friction wheel) is enclosed by the friction ring 321, which is in frictional engagement with the second conical friction wheel 353 with its inner circumferential surface and with the first conical friction wheel 352 with its outer circumferential surface. [185] The two bevel friction wheels 352, 353 can, as shown, have different diameters, as a result of which, if necessary, a gear ratio is saved in the subsequent drive 363. For weight reasons, the conical friction wheels 352 and 353 may also be hollow, since it only arrives on its lateral surface.

The friction ring 321, as also shown in FIGS. 16 and 17, is held in a cage 302, which is pivotally mounted at the point 372 (FIG. 10) in the friction-ring transmission housing 308 about an axis of rotation 31 1 which is defined by the bevel friction-wheel axes 350 and 351 of the conical friction wheels 352 and 353 certain level. To avoid large pivoting paths, it lies approximately in the middle of the axial length of the conical friction wheels 352, 353. The axis of rotation 311 may, as mentioned above, also lie in a plane parallel thereto and intersect the first-mentioned plane at an acute angle.

In the cage 302, two parallel guide shafts 356 and 357 are held, the pitch angle ß to the horizontal equal to the cone angle ß of the conical friction wheels 352 and 353. An adjusting bridge 319 is guided on these guide axes 356 and 357 and has projections 373 and 374, respectively, on which roller holders 322 and roller holders 323 are mounted. These have, as shown in FIG. 12, a circumferential groove 357 and surround with their flanges 376 the friction ring 321.

The friction ring 321 can be arranged with its axis parallel to the conical friction wheel shafts 350, 351 of the conical friction wheels 352 and 353. However, it can also be held in the cage 302 such that its axis lies parallel to the generatrix of the conical friction wheels 352, 353 facing one another and is perpendicular to the lateral surface of the conical friction wheels 352, 353.

[189] For adjusting the cage 302, an adjusting spindle 377 mounted in the housing 308 is provided, which is connected to an adjusting motor or magnet, not shown, and engages the cage 302.

[190] Upon slight rotation of the cage 302, the friction ring 321 is rotated about the axis 311, thereby changing the relative position to the conical friction wheels 352 and 353, so that the friction ring 321 automatically moves its position and changes the gear ratio of the conical friction ring transmission 362.

The output shaft 378 of the conical friction wheel 353 is received in a pressing device 379, which in turn is mounted in the housing 308, and carries output pinions 380, 381.

[192] The pressing device 379 consists of an extension shaft which extends over the output shaft 378 and has a flange 382 with a radial toothing which faces the bevel friction wheel 353 and which has a radial toothing cooperates with a corresponding radial toothing on the conical friction wheel 353. The radial toothing causes an axial pressure on the conical friction wheel 353.

[193] Advantageously, the friction-ring transmission housing 308 between the drive and output 360, 361, 363 on the one hand and the conical-friction-ring transmission 362 on the other hand divided by a partition 385. This makes it possible, in the housing part for the friction ring gear 362, a coolant without lubrication properties, for example, silicone oil, shrink, so that the coefficient of friction is not affected. As cooling liquid for the friction ring transmission 362, traction fluids or oils with ceramic powder or other solid particles are also suitable.

[194] Advantageously, the friction surfaces of at least one gear part of the friction ring gear 362, for example the conical friction wheels 352, 353 or the friction ring 321, are made of a hard metal or ceramic coating, for example titanium nitride, titanium carbonitride, titanium aluminum nitride or the like.

The application of the friction-ring transmission 362 shown in FIG. 18 is associated with a rear-wheel drive of a vehicle and substantially corresponds to the arrangement according to FIGS. 15 to 17, so that components of identical action are also numbered identically. In front of the friction-ring transmission 362 is a fluid coupling or a hydraulic converter 360 and behind the friction-ring transmission 362 is a planetary gear 386.

[196] The output shaft of the fluid coupling 360 also forms the shaft 387 of the upper first bevel friction wheel 352, which drives the second conical friction wheel 353 via the friction ring 321, on the Ab¬ drive shaft 388 a pinion 389 sits, with a freely rotatable on a transmission output shaft 390th sitting gear 391 meshes. The transmission output shaft 390 is aligned with the shaft 387 and is freely rotatably received in this. A pinion 392 integrally connected to the gear 391 forms the sun gear of the planetary gear 386. This meshes with planet gears 393 which are held in a planet carrier 394 which is capable of running around the transmission output shaft 390. The planet carrier 394 has a cylindrical projection 395, which includes a ring gear 396, which meshes with the planet gears 393 and is fixedly connected to the transmission output shaft 390 via a spline 397. In planetary gear 386, a multi-plate clutch 398 is further provided, which can connect the transmission output shaft 390 with the ring gear 396. Finally, a brake is assigned to the cylindrical projection 395 of the planet carrier 392.

[197] The forward gear is switched on by actuating the multi-plate clutch. If the brake is actuated, the planet carrier is held in place and there is a change in the direction of rotation of the transmission output shaft 390, that is to say a reverse drive. As can be seen immediately, in the embodiments according to FIGS. 13 to 18, the axis of rotation for the cage is arranged in each case in the region of the cones or the cone axes. This is different in the exemplary embodiments according to FIGS. 1 to 12. Here, the axis of rotation lies outside the space occupied by the cones and cones axes, when the arrangement of upper, is considered in the plane spanned by the cone axes plane. Although the adjustment paths become longer as a result of the latter arrangement, the latter arrangement permits a more sensitive adjustment and application of greater forces.

The conical-friction-ring transmission shown in FIGS. 19 and 20 has a friction ring 421 and two conical friction wheels 452, 453 (here only conical friction wheel 452 shown), in which the friction ring 421 is articulated via an adjustment bridge 419 which connects the friction ring 421 to a first Bearing 422 and stored at a zwei¬ ten bearing 423. The friction ring rotates when adjusting about the axis of rotation 411.

In this exemplary embodiment, the second bearing point 423 is an adjustable bearing point, with the result that the adjustable bearing point 423 is adjustable relative to the first bearing point 422 on the one hand and to the adjusting bridge 419 on the other hand. To adjust the adjustment bridge 419 in this exemplary embodiment by means of a link assembly 1100 to a cage 402 having an axial Führungs¬ device 414 consisting of a first cylindrical guide axis 1101 and a second zy¬-cylindrical guide axis 1102, out. Both the first cylindrical guide axis 1101 and the second cylindrical guide axis 1102 of the cage 402 are mounted in a friction-ring transmission housing 408.

The gate assembly 1100 consists essentially of a gate 1103, which has a first cam groove 1 104 and a second cam groove 1105, from a cam plate 1106 with a first sliding block 1 107 and a second sliding block 1108 and a ring follower 1109th

[202] In order to guide the ring follower 1 109 of the linkage arrangement 1100, an adjusting lever 1110 is rotatably mounted on the friction ring housing 408 by means of a guide pin 1111 so that the entire ring follower receptacle 1 110 pivots about the guide pin 1111 according to the double arrow 1112 is. The ring follower receptacle 1110 has a Ringfolgerführungsnut 1113, in which the Ringfol¬ eng 1109 along a longitudinal axis 1114 of the actuating lever 1110 can be moved.

[203] In the normal operating state, the ring follower 1109 is arranged centrically on a zero axis 1115. When the adjusting lever 1110 is moved in one of the two directions of the double arrow 1112 about the guide pin 1111, the ring follower 1109 is deflected from the zero axis 1115 to the left or to the right of the zero axis 1115. This requires a shift of the adjustable bearing 423, and thus a tilting of the friction ring, which thus begins to wander and the ring follower 1109 wie¬ moves back to the zero axis 1 1 15. Thus, since the ring follower 1109 always endeavors to dwell centrally on the zero axis 1115, the ring follower 1109 wanders along the longitudinal axis 11 14 within the guide groove 1113 of the actuating lever 1110 as long as the ring follower 1109 again centric, that is on a zero Position 1116 on the zero axis 11 15 arrived.

The respective zero position 1116 is defined by the intersection of the central longitudinal axis 1114 of the control lever 1110 and the zero axis 1115.

As a result of the fact that the ring follower 1109 moves automatically along the central longitudinal axis 1114 of the setting lever 1110 as a function of the position of the adjusting lever 1110, a particularly reliable, simple and fast reaction of the friction ring 422 to the conical friction wheels 452, 453 is possible. The present zero axis 1 115 preferably runs substantially parallel to the gap between the two conical friction wheels 452, 453.

In the present arrangement, the friction ring 421 provides a means for deflecting the displaceable bearing 423. The Einlenkmittel, so the friction ring, deflects the ring follower 1109 and thus also the movable bearing 423 in total again in a zero position 1109 on the zero axis 1115 a. It is understood that along the zero axis 1115 several different zero positions exist depending on the position of the control lever 1110.

[207] A first roller 1117 and a second roller 1118 for guiding the friction ring 421 are fastened to the sliding blocks 1107 and 1108 by suitable means.

[208] In FIGS. 21 to 32, a concrete exemplary embodiment of the embodiment according to FIGS. 19 and 20 is shown in different perspectives. Here, in each case the pair of figures 21 and 22, 23 and 24, 25 and 26, 27 and 28, 29 and 30 and 31 and 32, the embodiment once with Kegel¬ friction wheels 552, 553 and once without the Kegelreibräder 552, 553. Between the Kegelreibrädern a gap 52 IA is provided which is bridged by a friction ring 521. The friction ring 521 is guided in first bearing points 522 fixed relative to the adjustment bridge 519 (numbered here only by way of example) and bearing point 523 which can be displaced in relation to the adjustment bridge 519. As can be seen immediately, the bearing 523 is adjustable not only the adjusting bridge but also with respect to the other two bearing points 522. The other two bearing points 522 are preferably centrally, that is, in the axis of rotation of the friction ring 521, which remains as a degree of freedom through the gap 521 A between the two bevel friction wheels 552, 553 and allows the respective angle of attack for wandering the friction ring 521, ange¬ arranged. One of the two bearing points 522 is located in the gap 52 IA hiss the two conical friction 552 and 553. As a result, the adjusting bridge 519 can be axially displaced with respect to the exact ring position and follow the friction ring 521 axially exactly. A corresponding central bearing point can also be provided in the gap 52 IA, wherein the bearing points can also be provided at a different circumferential position on the friction ring 521.

In this exemplary embodiment, the adjustable bearing point 523 is mounted on the adjusting bridge 519 via sliding blocks (not visible here), which displace the displaceable bearing point 523 axially relative to the friction ring path along the gap 52 IA and a displacement perpendicular to the displacement path enable the adjustment bridge 519. As a result, an axial displacement of the adjustable bearing 523 can be caused by an adjusting lever 1210. If the adjusting lever 1210 is mounted eccentrically with respect to the path of the entire vertical bridge 519, then its position can be used as a measure of the position of the friction ring 521. If the adjusting lever 1210 is set in a specific position, this causes an adjustment of the displaceable bearing point 523 and the friction ring 521 moves in the direction of the position predetermined by the position of the adjusting lever 1210. The more he approaches this position, the more the ring follower 1211, which is guided in a guide groove 1213 of the actuating lever 1210, approximated for the backdrop of his rest or neutral position, which he reaches exactly in the desired position of the friction ring 521, so that the latter comes to rest.

[210] In this respect, an arrangement is provided by way of example in which the setting angle of the friction ring 521 can be adjusted by means of an adjusting device, the adjusting device, for example the adjusting lever 1210, being in relation to a zero setting position of the friction ring 521 in FIG. rather, the friction ring 521 each retains its axial position with respect to its travel, is in each case made unter¬ different. Thus, if the adjusting device is adjusted when the friction ring 521 is in a An¬ zero angle set, the friction ring 521 is adjusted by a corresponding angle. He then moves as long as his employment, until he again reaches a Anstellwinkelnullposition or zero position on the zero axis, namely at another axial position, namely at the axial position, which corresponds to the set position of the actuating device.

The cage 602 of a further exemplary embodiment shown in FIG. 33 is mounted so that it can be adjusted by means of a linear drive 1220 about a rotation axis 611 in a friction-ring transmission housing 608. The cage 602 has two guide shafts 618, on which an adjusting bridge 619 between a first end stop 1221 and a second end stop 1222 is displaceable about an adjustment path 1223. At the adjusting bridge 619, a friction ring 621 is provided which is mounted on the adjusting bridge 619 by means of a first roller holder 622 and by means of a second roller holder 623. [212] In this embodiment, the axis of rotation 611 of the cage 602 lies, on the one hand, within the range of the displacement path 1223 and, secondly, in the plane formed by a surface 629 formed by the rolling body axes 624.

[213] The linear drive 1220 has a first lifting magnet 1224 and a second lifting magnet 1225. The two solenoids 1224 and 1225 have the same structure in this embodiment. Therefore, the structure and function of the lift magnets 1224 and 1225 will be explained only on the first lift solenoid 1224. Both solenoids 1224, 1225 are attached to the friction-ring transmission housing 608 and are located on an adjustment axis 1226 in such a way that in each case a Verstellkol¬ ben 1227 of the first solenoid 1224 and the second solenoid 1225 with a bearing device 604 of the cage 602 corresponds. In order to verla¬ the adjusting piston 1227 along the adjustment axis 1226, each of the lifting magnets 1224, 1225 at one end of the adjusting 1227 a metal core 1228, which is surrounded by a magnetic coil 1229, which is housed in a 1221 Hubmagnetgehäuse unter¬. To move the adjusting piston 1227, the magnetic coil 1229 is activated in a pulse-pause mode, as a result of which the cage 602 can be set or controlled particularly accurately. The lifting magnets 1224 and 1225 each have a spring element 1231, which permanently presses the adjusting piston 1227 of a lifting magnet 1224 in the direction of the bearing device 604. Since the two solenoids 1224, 1225 are located on a common adjustment axis 1226, the spring forces of the spring elements 1231 of the individual solenoids 1224, 1225 cancel each other, whereby the bearing means 604 of the cage 602 is maintained in balance with respect to a central position 1232.

The provision of two solenoids 1224, 1225 has the advantage that there is redundancy with regard to the linear drive 1220 used, so that the operational safety of the linear drive 1220 is ensured even if one of the solenoids 1224, 1225 should fail.

[215] The exemplary embodiments according to FIGS. 34 and 35 have substantially the same construction as the exemplary embodiment from FIG. 33, so that identical and / or identically acting component groups have an identical numbering. The exemplary embodiments according to FIGS. 34 and 35 differ only in the construction of the respective cage 702 or 802.

[216] However, in the cage 702 according to FIG. 34, the axis of rotation 71 1 of the cage 702 lies outside the range of the adjustment path 1223 of the displacement bridge 619 within the plane which is determined by the surface 629. Thus, in the exemplary embodiments according to FIGS. 33 and 34, the axes of rotation likewise each lie in a region covered by the cones and the conical shafts, as was already explained in the case of the exemplary embodiments according to FIGS. 13 to 32. Characterized in that in the exemplary embodiment according to Figure 34, the position of the rotation axis 711 relative to the position of the axis of rotation 611 is arranged outside the adjustment path 1223, other lever dimensions result between the rotation axis 711 and the adjustment axis 1226 in the case of the cage 702 than between the rotation axis 611 and the adjustment axis 1226 in the case of the cage 602.

[217] The same applies with regard to the cage 802 from FIG. 35, since the axis of rotation 811 of the cage 802 is arranged between the first end stop 1221 and the second end stop 1222, thus in the region of the adjustment path 1223. However, the axis of rotation 811 is offset from the plane of the surface 629 and outside a region occupied by the cones and the conical shafts so that different lever dimensions result between the axis of rotation 811 and the adjustment axis 1226, thereby increasing the sensitivity of adjustability of the Friction ring 621 is chosen differently again.

[218] The adjustment bridge may start against the limit stops 1221 and 1222 if the drive for the cage fails. These stops ensure that the adjustment bridge is tilted to a neutral position and does not move further. In this way, a complete destruction of the transmission counteracted in these cases and a motor vehicle with this gear still be moved.

[219] The adjustable end stop 1240 shown in FIGS. 36 to 38 has a displaceable end stop pin 1241 and forms a preferred adjustment travel limit for a friction ring transmission with alternating direction of rotation. The adjustable end stop 1240 further consists essentially of a rotary magnet 1242 and an adjusting mechanism 1243. The rotary magnet 1242 is supplied with electricity via two electric cables 1244 and 1245 and can thus drive the adjusting mechanism 1243.

[220] The adjustable end stop 1240 is flanged by means of screw connections 1246 (here only exemplarily numbered) to a friction-ring transmission housing 908. For this purpose, the adjusting mechanism 1243 has a corresponding adjusting mechanism housing 1247 with corresponding threaded bushes 1248. In this embodiment, the Verstellmechanikgehäuse 1247 comprises a total of three threaded bushes 1248 (here only exemplified).

The rotary magnet 1242 is connected via a rotary magnetic shaft 1249 to a setting disk 1250 of the adjusting mechanism 1243. The rotary magnetic shaft 1249 and the adjusting disc 1250 form a shaft-hub connection in this embodiment. Between the adjusting disk 1250 and the Endanschlagsbolzen 1241 a bearing ball 1251 is provided. Forces between the end stop pin 1241 and the adjusting disk 1250 are easily transmitted via this bearing ball 1251 and, secondly, the adjusting disk 1250 is structurally mounted so as to be relatively displaceable relative to the end stop pin 1241. So that the Endanschlags pin 1241 on the bearing ball 1251 always on the pressure plate 1250 is pressed and thereby clearly positioned opposite the adjusting disk 1250, a compression spring 1252 engages around the end stop bolt 1241. In order for the pressure spring 1252 to apply a sufficiently large pressure force, the pressure spring 1252 is between a shoulder 1253 of the end stop bolt 1241 and a Housing stop 1254 clamped.

[222] In order to transmit the forces acting on the end stop bolt 1241 or the adjusting disk 1250 to the adjusting mechanism housing 1247, a bearing disk 1255 is provided between the adjusting disk 1250 and the adjusting mechanism housing 1247, which has a sliding bearing 1256 between the adjusting disk 1250 and the adjusting mechanism housing 1247 causes.

[223] The adjusting disk 1250 has different thicknesses in the region of its outer radius, so that the displaceable end stop bolt 1241 of the adjustable end stop 1240 according to the double arrow direction 1257 can be displaced structurally in a particularly simple manner. Thus, in a first position, the setting disk 1250 provides an initial thickness 1258 (see FIG. 37) in the region of the displaceable end stop pin 1241, while in another position it provides an end thickness 1259 (see FIG. 38) in the region of the displaceable end stop pin 1241.

[224] The present adjustable stop 1240 can be provided on the one hand, in order to start up an adjustment bridge or a friction ring in an emergency or in borderline cases against it. With a suitable arrangement of the adjustable end stop 1240, this leads to a running against the end of a Verstellwegs friction ring straight and non-destructive remains in this position. However, this mode of operation depends on the direction of rotation of the friction ring, so that the adjustable end stop 1240 must be set differently depending on the direction of rotation of the friction ring. Therefore, it is advantageous if, depending on the direction of rotation of the friction ring, the rotary magnet 1242 is actuated in accordance with the required end position of the end stop pin 1241. It should again be noted that in addition to the exemplary embodiment with proposed rotary magnet 1242, a purely mechanical solution via a directional freewheel (not shown here) can be provided, the freewheel depending on the direction of rotation of the friction ring a Endanschlagsbolzen 1241 ent¬ accordingly shifted ,

[225] The arrangement shown in FIG. 39 consists essentially of an input cone 1270, an output cone 2171 and a friction ring 2021. The input cone 1270 is operatively connected to a drive shaft 1272 and firstly by means of cylindrical roller bearings 1273 and secondly by means of tapered roller bearings 1274 a friction ring gear housing 2008 stored. The taper roller bearings 1274 are particularly well suited to additionally absorb axially acting forces in addition to radially acting forces. [226] By contrast, the output cone 1271 is mounted on the friction-ring transmission housing 2008 only by means of cylindrical roller bearings 1275 or 1276. The output cone 1271 is operatively connected to an output shaft 1277. The output shaft 1277 is mounted directly on the output cone 1271 and additionally by means of tapered roller bearings 1278 on the friction-ring gearbox housing. Through the bearings 1274, 1278, 1273, 1275 and 1276, the input cone 1270 and the output cone 1271 are braced against each other in the axial direction 1279, that necessary contact forces between the input cone 1270, the friction ring 1521 and the output cone 1271 are applied so that forces, in particular torques, can be transmitted without difficulty between these components. For clamping or for generating an additional contact force, a pressing device 1280 is provided between the drive shaft 1277 and the output cone 1271. By means of the pressing device 1280, it is possible to vary a distance in the axial direction 1279 between the output cone 1271 and the tapered roller bearing 1278 on the drive shaft 1277 or, in particular in the clamped state, to produce correspondingly varying contact forces.

The variation of the contact forces between the input cone 1270, the output cone 1271 and the friction ring 1521 is advantageous, since not only the translation ratio but also forces acting on the arrangement, in particular torques and surface pressure forces, displace the friction ring 1571 to change. In order to be able to advantageously adapt the contact forces and thus also the frictional connection between the two friction cones 1270, 1271 and the friction ring 1521 to these different operating conditions, the pressing device 1280 not only acts with a constant force but can also be adjusted. For this purpose, the pressing device 1280 comprises a first adjusting disk 1281 and a second setting disk 1282, between which a ball 1283 is guided on corresponding guide tracks (not explicitly shown here) of the individual adjusting disks 1281, 1282. The guideways for the balls 1283 are configured such that an increased torque causes a rotation of the two adjusting disks 1281, 1282 relative to one another, which in turn causes the balls 1283 to shift along the guide track, as a result of which the setting disks 1281, 1282 are pressed out of one another become. In this way, the pressing device 1280 generates a starting force dependent on the output torque. Advantageously, the arrangement described here as a mechanical device has extremely short reaction times and can react very well, in particular, to impacts in the output-side drive train.

[228] In addition to the action of the balls 1283, the adjusting disks 1281, 1282 are pushed apart by means of a spring arrangement 1284, and the spring arrangement 1284 in the present case provides a certain base load of the pressing device 1280. [229] Since the characteristic curve of the present pressing device 1280 can only be optimized to a limited extent, the pressing device 1280 has a force compensation, in particular for partial load ranges. This takes place by means of a hydraulic pressure regulating device 1285, which in this exemplary embodiment has a lifting magnet 1286 and a magnetic piston 1287 which revolves with the drive cone 1271. The solenoid 1286 is fixedly mounted in the friction-ring gear housing 1508. By contrast, the magnetic piston 1287 is movably mounted in a supplementary shaft 1288.

The additional shaft 1288 can orbit with the output cone 1271 and "take along" the magnetic piston 1287 of the hydraulic pressure regulator 1285 so that the magnetic piston 1278 rotates with the output cone 1271 about its axis of rotation 1289 1288 has a bearing bore 1290 for the magnetic piston 1287, wherein the bearing bore 1290 merges into a hydraulic oil bore 1291. The hydraulic oil bore 1291 in turn is operatively connected to an oil chamber 1292 of the output cone 1271.

[231] By means of the hydraulic oil stored in the hydraulic oil space 1292, the forces which are transmitted to the second setting disk 1282 by means of the spring arrangement 1284 and / or which are transmitted via the balls 1283 by the first setting disk 1281 can be compensated.

[232] In order to be able to carry out a corresponding pressure compensation in the hydraulic oil chamber 1292, the magnetic piston 1287 is axially displaced by means of the lifting magnet 1286 along the axis of rotation 1289 of the output shaft 1271. Depending on how the magnetic piston 1287 is excited by the solenoid 1286 and axially displaced along the axis of rotation 1288, the volume of the bearing bore 1290 increases, thereby setting different hydraulic oil pressures in this bearing bore 1290. These pressure variations are transmitted via the oil hydraulic bore 1291 to the oil chamber 1292, so that the forces acting thereon from the hydraulic oil of the hydraulic oil chamber 1292 on the second adjusting disk 1282 can be adjusted differently.

[233] The described hydraulic pressure regulator 1295 of the pressing device 1280 is particularly compact and therefore requires very little installation space. Advantageously, it can be arranged almost completely within the output cone 1271. Only the solenoid 1286 as a housing fixed and thus statically fastened component requires a bearing on a friction-ring transmission component, which is the output shaft 1271 is not directly associated. It is particularly advantageous in this connection that the magnetic piston 1287 cooperating with the lifting magnet 1286 is mounted as a dynamically moved component of the hydraulic pressure regulating device 1285 so as to be displaceable directly or indirectly on the output cone 1271. In the present exemplary embodiment, the magnetic piston 1287 is mounted particularly reliably on the additional shaft 1288 of the output cone 1271. [234] It is understood that a piston of a hydraulic arrangement does not necessarily have to be driven by the lifting magnet 1286. Rather, any other dynamic component of a pressing device, in particular a compensating-effective or motor-driven pressing device, can be driven accordingly.

According to the illustration according to FIG. 40, a split friction ring 1300 for a conical friction ring transmission with a first friction cone 1301 and with a second friction cone 1302 is proposed. The split friction ring 1300 has on its outer running surface 1303 a gap 1304 which divides the outer running surface 1303 into a first running surface half 1305 and into a further running surface half 1306. Moreover, the split friction ring 1300 has on its inner race 1307 an inner gap 1308 which divides the inner race 1307 into a first inner race half 1309 and into a second inner race half 1310.

[236] The split outer race 1303 and the split inner race 1307 improve the stability of the split friction ring 1303 against tilting moments with respect to a gap 1311 between the two friction cones 1301 and 1302 (against rotational movements in the drawing plane of FIG. 40). because by the shared running surfaces 1303, 1307 with the same surface pressure greater leverage can be realized.

It is understood that the divided treads 1303, 1307, regardless of this, can still have creases (for the sake of clarity, not explicitly shown here). By means of such grooves, a better fluid distribution and an improved adaptation of the surface pressure is achieved. It has been found that the above-mentioned effects can no longer be significantly influenced effectively with wider gaps, so that with a gap width 1312 of more than 10% of the width of the first half-surface 1305 or 1309 and the second half-surface 1306 or 1310, respectively Stabilization of the split friction ring 1300 substantially comes into play.

The divided friction ring 1300 rotates about a friction-ring rotation axis 1313, while the first friction cone 1301 rotates about a friction-cone axis 1314 and the second friction cone 1302 rotates about a friction-cone axis 1315. The divided friction ring 1300 in this case encloses the first friction cone 1301 and is at least partially disposed in the gap 1311 between the first friction cone 1301 and the second friction cone 1302. According to the outer shape of the friction cone 1301, 1302, the friction ring axis 1313 has an angle 1316 with respect to the Reibkegelrotationsachsen 1314 and 1315. However, it can also be readily extended with this gap in conical running surfaces parallel to the cone axes. [239] Thus, the areas of the columns 1304, 1308 also do not count toward the effective tread 1303 or 1307, such as chamfers attached to the split friction ring 1300 (numbered as an example only for clarity). The split friction ring 1300 has a total width 1317. It is understood that such a gap may be provided only on one of the two treads.

[240] The tapered-friction ring gearing 2363 shown in FIGS. 41 to 43 substantially corresponds in its construction to the gearboxes treated here. A significant difference is that the friction cone 2301, 2302 are mounted in this embodiment both in a first separate bearing glasses 1330 made of steel and in another separate bearing glasses 1331 made of steel. It is understood that for producing the separate bearing glasses 1330 and 1331, another, suitably suitable material can be used.

[241] In particular, due to the stable bearing glasses 1330, 1331 made of steel, it is possible that the remaining conical friction ring housing 2008 can be made on the one hand of lighter material, such as aluminum, and on the other hand particularly thin-walled. The bearing glasses 1330 and 1331 in this case preferably take on the complete main forces, such as radial and axial forces, which arise essentially as a result of the bracing of the two friction cones 2301 and 2302. Advantageously, accordingly, the conical friction ring housing 2008 only needs to absorb only secondary forces, such as torque forces, bearing rotors 1330, 1331 twisting one another, so that, as mentioned, it can be constructed much more filigree and therefore lighter. This leads to an enormous weight saving over conventional transmissions. In principle, in the present case, it may be sufficient to support the friction cones 2301, 2302 on only one of their sides in a pair of bearing glasses.

[242] Alone due to the fact that much weight is saved by the bearing glasses 1330 and 1331 with respect to a transmission housing 2008, the storage of at least one side of the two friction cone 2301, 2302 in a common bearing glasses 1330 or 1331, preferably from a formed material deviating from the rest of the transmission housing 2008, also advantageous regardless of the other features of the present invention. Accordingly, two such bearing glasses 1330, 1331 for one side of the friction cone 2301, 2302 are particularly advantageous.

[243] Preferably, a seal, in particular a shaft seal 1332 for the friction cone shaft 1333 of the friction cone 2301 mounted on the bearing bracket 1330, may be provided directly on the bearing bracket 1330. As a result, the bearing glasses 1330 can act as a fluid space separation on its own, so that it is possible to dispense with additional additional sealing assemblies of this type. This is particularly advantageous when 1330 gear members comprehensive rooms are to be separated from each other by the steel bearing glasses. [244] In the present exemplary embodiment, for example, the bearing gland 1330 separates a fluid space 1334 filled with a traction fluid, in which the friction cones 2301, 2302 rotate, from an adjacent further gear space 1335.

[245] In the area of the bearing gland 1331, a friction cone gland 1336 is provided on the friction cone housing 2008. The bearing glasses 1331 and the friction cone seal 1336 are shielded from an environment 1337 by a cover plate 1338.

[246] In order to minimize the number of fastening elements for the present bearing eyeglasses 1330, 1331 and thereby to save space, it is advantageous if at least one of the bearing eyeglasses 1330, 1331 only between a first housing half 1339 of the conical friction ring gear housing 2008 and a further housing half 1340 of the conical friction ring gear housing 2008 is clamped. This also facilitates the production, since for the bearing glasses 1330 no separate Befestigungs¬ elements, such as screw holes or the like, must be provided. On the other hand, it may be favorable to realize a seal over a housing surrounding a gear sliding chamber, which is already known per se from the prior art.

[247] In connection with the above-described bearing goggles 1331, and when, for example, gear members 2302 mounted on the bearing goggles 1331 can be found on only one side of the bearing goggles 1331, it may be advantageous for the gland bearings 1331 to be located outside a sealed space such as the fluid space 1334 to arrange. In this way, the bearing glasses 1331 is easily accessible and eliminates a complex eyeglass seal. The bearing goggles 1331 can then be covered cost-effectively with a simple cover plate 1338 on their side 1341 facing away from the gearbox 2302.

[248] In order to be able to fix the bearing glasses 1330, which are of relatively large size, to the conical-friction-ring transmission housing 2008, the conical-friction-ring transmission 2363 additionally has a bearing-wear attachment 1342. By means of the Lagerbrillenansatzes 1342 succeeds a precisely fitting connection between the bearing glasses 1330 and the first housing part 1339th

It is understood that in particular the bearing goggles 1330 can be configured so that a transmission member 1343 of a differential gear, which is part of the conical-friction ring transmission 2363, can be flanged onto it. Advantageously, the steel bearing bracket 1330 supports the gear member 1343 of the differential gear 1344 relative to the second friction cone 2302, in particular with respect to an output shaft 2277 of the second friction cone 2302, such that a distance 1345 of a driven shaft rotation axis 1346 to a differential gear rotation axis 1347 with respect to temperature. Temperature fluctuations and load fluctuations are particularly low, ideally not at all, changed. This achieves the effect that the interacting component group output shaft 2277 and gear member 1343 of the differential gear 1344 interact with each other in as little wear and noise as possible in almost all operating states.

[250] In addition, forces between the differential gear 1344 and the bevel gear 263, in particular between the gear 1343 and the output shaft 2277, can also be transmitted particularly advantageously by means of the bearing goggles 1330 without loading the conical friction ring gear housing 2008.

As is immediately apparent, it is possible to connect the two bearing glasses in a varied embodiment via a separate frame, for example via rods or via a linkage, so as to further relieve the housing.

As shown in FIGS. 44 and 45, a reverse gear R in a bevel friction ring gear 3363 (FIG. 44), 4363 (FIG. 45), preferably independently of the other features of the present invention, can also be provided by a planetary gear 3360 or a double planetary gear 4360 can be realized. In particular, with the double planetary gear 4360 can be realized in a small space and a mini¬ number of gear members in conjunction with the prescribed by a conical friction ring 4362 directions of rotation a reverse gear R, in which a torque does not have to be transmitted via stationary gears, as this in arrangements The prior art is the case.

[253] The planetary gear 3360 of the conical-friction ring transmission 3362 is arranged on the input side in front of an input cone 3270 of the conical-friction ring transmission 3362. The input cone 3270 is in operative contact via a friction ring 3021 with an output cone 3271 of the conical friction ring transmission 3362. The input cone 3270 rotates on an input cone axis 3363, while the output cone 3271 rotates on an output cone axis 3364. On the output cone 3271, an output shaft 3365 is arranged on the output side, which has an output shaft sun gear 3366.

[254] The planetary gear 3360 is operated via an input shaft sun gear 3367 of an input shaft 3368. The planetary gear 3369 rotates not only about its planetary gear 3370, but simultaneously rotates about the input shaft axis 3363 and meshes with a ring gear 3371 of the planetary gear 3360. By means of the ring gear 3367, which also On the input shaft axis 3363, rotational moments are transmitted from the input shaft 3368 to the input cone 3270. If a shift linkage 3372 of the planetary gear 3360 is in a neutral position N, the planetary gear 3369 revolves around the input bevel axis 3363 and meshes with the input shaft gear 3367 on the one hand and with the ring gear 3371 in such a way that between the input shaft 3368 and the ring gear 3371 are not transmitted sufficient driving forces to make the input cone 3270 in rotation.

If the shift linkage 3372 is displaced to the position R, a web 3373 of the planetary gear 3369 is fixed to a conical friction ring housing 3008, then the planetary gear 3369 rotates about its planetary gear 3370 and the ring gear 3367 rotates in the opposite direction to the input sun gear 3367. Thus, a reverse gear is realized.

If the shift linkage 3372 is displaced from the neutral position N in the direction of the position D, the web 3373 is fixed to the ring gear 3371, so that the planetary gear 3369 can not rotate about the input shaft axis 3363. Thus, the planetary gear 3369 is fixed relative to the ring gear 3371, so that between the ring gear 3371 and the planetary gear 3369 no relative movement is possible. Hier¬ by a rotational movement of the input shaft sun gear 3367 is transmitted via the planetary gear 3369 on the input cone 3270, whereby a forward gear is realized.

[258] In the conical friction ring gear 4362, the input shaft 4368 is directly connected to the input cone 4270 so that power is transmitted directly from the input shaft 4368 to the input cone 4270. In this embodiment, the double planetary gear 4360 is arranged on the output side between the output cone 4271 and the output shaft 4375.

The dual planetary gear 4360 has an output shaft sun gear 3380 which meshes with a first planetary gear 4369 with a first planetary gear shaft 4370. In turn, a second planetary gear 4381, which rotates about a second planetary gear axis 4382, meshes with the first planetary gear 4369. The two planet gears 4369 and 4381 are connected via a planetary gear 4383 directly to the output cone 4271.

[260] In particular, to set the second planetary gear 4381, the double planetary gear 4360 has a first shift linkage 4384, over which a reverse gear can be shifted. By means of a second shift linkage 4385, the planetary gear frame 4383 can be fixed relative to the output shaft 4365, so that a forward gear is realized.

[261] When the first shift linkage 4384 is shifted to the position R, the second planetary gear 4381 can no longer rotate about the second planetary gear axis 4382, so that the first planetary gear 4369 rotates about the second planetary gear 438 Output tapered shaft 4364 rotates. In this case, the direction of rotation of the output cone 4271 rotates, so that the output shaft 4365 rotates in the opposite direction.

[262] On the other hand, when the second shift linkage 4385 is brought into the position D so that the planetary gear frame 4383 and the output shaft are fixedly connected to each other via a second shaft sounding wheel 4386, a rotational direction of the output cone 4271 directly becomes the second output shaft sun gear 4386 via the planetary gear frame 4383 and thus transferred to the output shaft 4365. As a result, a forward gear is realized.

[263] The cage 5002 shown in FIGS. 46 to 48 has an axial guide 5014 with two guide shafts 5018, one left and one right. On the guide shafts 5018 a Verstellbrücke 5019 is guided axially freely displaceable. With the adjustment bridge 5019, a friction ring 5021, which transmits forces between two friction cones (not shown), is held by means of a first roller holder 5022 and by means of a second roller holder 5023.

The cage 5002 is mounted on a friction-ring gear housing (not shown here) about an axis of rotation 5011. The adjustment of the cage 5002 about the axis of rotation 5011 is effected by means of an eccentric motor 5390, which is operatively connected to the cage 5002 by means of a link 5391. In this exemplary embodiment, the link 5091 is divided into two and consists of a link rod 5092 which is fastened to the cam motor 5390, and a cage link rod 5093 which is fastened to the cage 5002 directly via a cage link pivot 5094.

[265] By means of the Anlenkers 5091 slight Anstellbewegungen the cam motor 5390 are exactly transferred to the cage 5002, so that it rotates about the axis of rotation 5011, whereby the Reib¬ ring 5021 against the Reibkegeln (not shown here) hires and with the adjustment bridge 5019th along the guide axes 5018 moves accordingly and repositioned.

[266] In order for disturbances in the region of the eccentric motor 5390 not to block the function of the cage 5002 in such a way that the operation of the cage 5002 completely fails, an overload protection 5395 is provided for such emergency situations in the area of the cage link rod 5393. Components such as a Positionierku¬ gel 5396 and a positioning spring 5397, the overload protection 5395 are arranged on the cage 5002 or within a receptacle 5398 provided for this purpose on the cage 5002.

The cage arm rod 5393 is placed above the receptacle 5398 such that the positioning ball 5396 is pressed by the spring force of the positioning spring 5397 into a positioning ball recess 5399. As a result, the cage link rod 5393 is in the normal operating state of the cage 5002 and the cam motor 5390 defined against the cage 5002 held and fixed. In order that the cage link rod 5393 is not pushed away by the spring force of the positioning spring 5397, the overload lock 5395 comprises an overload protection cover 5400 which engages around the cage 5002 in the area of the overload protection 5395 in a C-shaped manner. In order for the overload protection cover 5400 to remain securely in its original place, it is additionally fastened to the cage 5002 by means of a safety screw 5401.

[268] Should an overload occur during operation, the cage link rod 5393 within the overload fuse 5395 can deflect according to the directions of the double arrow 5402, so that damage to the cage 5002, to the link 5391 or to the cam motor 5390 is at least slight Overloads are prevented.

[269] The overload protection 5395 is triggered as soon as the overload forces exceed the forces of the positioning spring 5397 and the frictional resistance between the cage link rod 5393 and the positioning ball 5396, the cage 5002 and the overload protection cover 5400.

[270] The overload protection 6395 shown in FIG. 49 is arranged within an armature 6391, so that the mechanics of the overload protection 6395 are particularly well protected against external influences by the armature 6391. The overload protection 6395 has a tension element 6410, which is intended to be attached directly to a guide cage (not shown here) for an adjustment bridge (not shown here) by means of a Käfiganlenkerdrehpunkts 6394. In addition, the overload protection 6395 has a pressure element 6412, which comprises a bearing ring 6411 for coupling to an eccentric disc (not shown here) of an eccentric drive (not shown here). By means of the bearing ring 6411, the link 6391 can be securely connected to the eccentric drive. Both the tension element 6410 and the pressure element 6412 are displaceably guided in a link tube 6413 to one another.

[271] The tension element 6410 is braced within the Anlenkerrohrs 6413 by means of a first compression spring 6414. The compression spring 6414 is supported in this case on the one hand on a Anlenkerrohrkragen 6415 of the Anlenkerrohrs 6413 and the other on a Anlenkerflansch 6416, which is screwed to the tension element 6410. So clamped is the first compression spring 6414 biased accordingly. By means of the first compression spring 6414, tensile forces 6417, which act on the link 6391, can be compensated by the overload protection 6395, in that the tension element 6410 moves in the direction of the tensile forces 6417 relative to the linkage tube 6413 and the pressure element 6412. [272] In order to compensate for compressive forces 6418, the overload protection 6395 has a second pressure spring 6419 between the pressure element 6412 and the tension element 6410 or the armature flange 6416. By means of the spring force of the second compression spring 6419, pressure forces 6418, which are below a critical value, can be well compensated by the overload protection 6395. For this purpose, the pressure element 6412 springs into the Anlenkerrohr 6413 or in the Anlenkerflansch 6416.

[273] In the normal operating state, the second compression spring 6419 pushes the pressure element 6412 away from the tension element 6410, so that the pressure element 6412 normally bears against a retaining ring 6420, which is arranged on the armature tube 6413. In this exemplary embodiment, the securing ring 6420 provides a predetermined breaking point of the overload protection 6395, which is destroyed in the event of an overload which exceeds a critical value.

Thus, the present overload protection 6395 has, on the one hand with the retaining ring 6420, a destructible overload protection means, which in the present case is destroyed, in particular in the case of overload pressure forces which exceed a critical value. On the other hand, the overload protection 6395 with the spring-mounted tension element 6410 or pressure element 6412 has destruction-free overload protection means with which dynamically acting overload protection means are realized which compensate overload forces which do not exceed a critical value. Here, the springs are each chosen so strong that the link 6391 is rigid in normal operation and yields only when overloaded in the desired and described above manner.

The overload protection 6395 described above is particularly compact because it is integrated within the armature 6391, the armature 6391 or the overload protection 6395 being arranged and acting directly between a drive and a related cage.

[276] Alternatively or cumulatively to the overload fuses illustrated in FIGS. 46 to 49, a fail-safe 7430 as illustrated in FIGS. 50 to 53 may be provided with respect to an adjustment bridge (not shown) or a guide cage (not shown) of an adjustment bridge. Such a fail-safe 7430 has, on the one hand, a cam disk 7431, a cam follower 7432 and a cam follower contact spring 7433. The cam disk 7431 of the fail-safe 7430 is in the proper operating state by means of first driver 7434 of the cam plate 7431 with second drivers 7435 a retaining washer 4736 in contact. The holding disk 7436 is mounted axially displaceably along a drive axis 7437 of a drive 7438 on a drive shaft 4739 in accordance with the directions of the double-file 7440. The retaining disk 7436 is pressed and fixed in the direction of the cam disk 7431 by means of a retaining disk spring 7441, so that a force flow from the drive 7438 via the drive shaft 7439 and the retaining disk 7436 with second drivers 7435 to the first catch 7434 of the cam disk 7431 and is transferred from there to the cage or on the adjustment bridge.

In order to decouple the retaining disk 7436 from the cam disk 7431, a releaser 7442 is provided, which is able to push the retaining disk 7436 away from the disk 7431 by means of a release piston 7443 until the first drivers 7434 and the first catch 7434 engage second driver 7435 lose contact with each other. For decoupling, the release piston 7434 is simply moved in the direction 7444 so that the retaining disk 7436, as shown in FIGS. 52 and 53, is completely decoupled from the cam disk. In this case, the retaining disk 7436 has shifted relative to the drive shaft 7439 and moved closer to the drive 7438, so that the retaining disk spring 7441 is accumulated together.

If the retaining disk 7436 is de-coupled from the cam disk 7431 by the release piston 7443, the retaining disk 7436 is displaced beyond the cam follower 7432, so that the cam follower 7432 moves into a depression 7446 of the disk due to the pressing force 7445 of the cam follower contact spring 7433 7431 is pressed (see in particular Figure 53).

The presented here failover 7430 ensures that in case of malfunction of the drive 7438, the free adjustment of a cage or a Verstellbrücke is guaranteed by the releaser 7442 decouples the cam 7431 of the drive 7438 while the cam follower 7432 in the sink 7446 of the cam follower 7431 is pressed. As a result, the cam disk 7431 is fixed in an emergency running position, so that the operability of a friction-bearing transmission, which has the fail-safe mechanism 7430, is ensured. The emergency running position is present when the cam disk 7431 is aligned such that the cam follower 7432 is arranged in the recess 7446 of the cam disk 7431.

[281] The spring force of the cam follower urging spring 7433 may be configured such that a friction ring of a friction ring gear is capable of rotating the cam disk 7431 to a final rest position in which the cam follower 7432 is disposed in the valley 7446 as soon as the friction ring reaches a corresponding end stop (not shown here) and starts against it. In this way, a reliable fail-safe can be readily realized, which adjusts the friction ring with a predetermined adjustment, for example, in the direction of a starting position, the friction ring is then stabilized by the end stop in this position. In the described operation of the failover 7430 is to be considered that usually a drive only small If necessary, an appropriate gear (not shown here) can be provided between the drive and the cam disk 7431. In this respect, in most application areas, a height profile 7447 of a cam curve of the cam disk 7431 is generally sufficient in order to hold the cam disk 7431 in an emergency running position.

[282] It is understood that the retaining washer 7436 can be provided with a cam, which is not arranged in the working area of a cam disc. After removing a fault, so even if a release piston of a releaser is engaged again, the retaining disk 7436 can be rotated by means of a drive until a cam of the retaining washer 7436 reaches the cam follower 7432 er¬. Then a Nockenfolderandrückfeder 7441 can be relaxed, which was previously pressed by a cam follower in a sink, so that a clutch between the two discs 7431 and 7436 can engage again. If then the entire assembly is rotated back, it is back in its normal operating position.

LIST OF REFERENCE NUMBERS

1 arrangement

2 cage

3 sheet metal construction

4 first elastic bearing device

5 second elastic bearing device

6 third elastic bearing device

7 holes

8 friction ring gear housing

9 cross-sectional rejuvenation

10 adjusting lever

11 axis of rotation

12 Anstellhebelaufhahmeblech

13 double arrow

14 axial guide device

15 U-shaped bent area

16 first leg of the sheet metal construction

17 second leg of the sheet metal construction

18 guide axis

19 adjustable bridge

20 arrow directions

21 friction ring

22 first roll holder

23 second roll holder

24 rolling element axis

25 rotation lock

26 anti-rotation pin

27 track rail

28 first surface side

29 area

30 second surface side

101 arrangement

102 cage 104 elastic bearing device

110 adjusting lever

111 axis of rotation

112 Anstellhebelaufhahmeblech

113 double arrow

114 axial guide device

118 guide axis

119 adjustable bridge

121 friction ring

122 first roll holder

123 second roll holder

124 rolling element axis

125 rotation lock

126 anti-rotation pin

127 track rail

128 first surface side

129 area

130 second surface side

140 rubber element

141 fixed fixing core

142 rubber element length

201 arrangement

202 cage

204 elastic bearing device

208 friction ring gear housing

214 axial guide device

218 guide axis

219 adjustable bridge

221 friction ring

222 first roll holder

223 second roll holder

224 rolling element axis

225 rotation lock

226 anti-rotation pin 227 Running track

228 first surface side

229 area

230 second surface side

245 variable motor

246 gear arrangement

247 opposite side

248 leaf spring

248A guide bush

248B disc spring

248C rubber element guide

248D bearing head

248E bearing rod

248F bearing cup

249 bearings for the guide rod

302 cage

308 friction ring gear housing

311 axis of rotation

319 adjustable bridge

321 friction ring

321A gap

322 first roll holder

323 second roll holder

329 area

345 variable motor

350 first bevel pinion axis

351 second conical friction wheel axis

352 first bevel gear

353 second bevel gear

354 first crosshead

355 second crosshead

356 first guide axis

357 second guide axis

358 cones 359 transverse drive

360 fluid coupling

361 switching unit

362 conical friction ring gear

363 downforce

364 wave

365 brake disc

366 brake shoes

367 freewheeling gear

368 countershaft

369 shift sleeve

370 pinion

371 drive shaft

372 place

373 approaches

374 approaches

375 circumferential groove

376 flanges

377 adjusting spindle

378 output shaft

379 Adjustment device

380 output pinion

381 output pinion

382 facing flange

383 Radial toothing

384 Radial toothing

385 partition

386 planetary gear

387 wave

388 output shaft

389 pinion

390 transmission output shaft

391 gear

392 pinion, which is integrally connected to the gear 393 planetary gears

394 planet carrier

395 cylindrical approach

396 ring gear

397 spline

398 Lammelenkupplung

399 brake

402 cage

408 friction ring gear housing

411 rotation axis

414 axial guide device

419 adjustable bridge

421 friction ring

422 first depository

423 second depository

424 rolling element axis

452 first bevel gear

519 adjustable bridge

521 friction ring

522 first depository

523 second depository

521A gap

552 first conical friction wheel

553 second bevel gear

602 cage

604 storage facility

608 friction ring gear housing

611 rotation axis

618 guide axle

619 adjustable bridge

621 friction ring

622 first roll holder

623 second roll holder

624 rolling element axis 629 area

702 cage

704 storage facility

71 1 area

802 cage

804 storage facility

811 rotation axis

908 friction ring gear housing

1100 backdrop arrangement

1101 first cylindrical guide axis

1102 second cylindrical guide axis

1103 scenery

1 104 first gate groove

1105 second gate groove

1106 link plate

1107 first sliding block

1108 second sliding block

1109 ring follower

1110 Lever

1111 guide pin

1112 double arrow

1113 guide groove

1114 middle longitudinal axis of the control lever

1115 zero axis

1116 zero position

1117 first role

11 18 second roll

1201 first cylindrical guide axis

1202 second cylindrical guide axis

1206 link plate

1210 lever

1211 guide pin

1213 guide groove

1220 linear drive 1221 first end stop

1222 second end stop

1223 adjustment path

1224 first solenoid

1225 second solenoid

1226 adjustment axis

1227 adjusting piston

1228 metal core

1229 solenoid

1230 solenoid housing

1231 spring element

1232 middle position

1240 adjustable end stop

1241 adjustable end stop bolts

1242 rotary magnet

1243 adjustment mechanism

1244 electrical cable

1245 electrical cable

1246 screw connections

1247 adjusting mechanism housing

1248 threaded bushes

1249 rotary magnetic shaft

1250 pick-up disc

1251 bearing ball

1252 compression spring

1253 End stop bolt shoulder

1254 housing stop

1255 bearing disc

1256 plain bearing

1257 double directions

1258 initial thickness

1259 final thickness

1270 entrance cone

1271 exit cone 1272 drive shaft

1273 cylindrical roller bearing of the input cone

1274 tapered roller bearing of the input cone

1275 cylindrical roller bearing of output cone 1276 cylindrical roller bearing of output cone

1277 output shaft

1278 tapered roller bearing of the output shaft

1279 axial direction

1280 Pressing device 1281 first adjusting disk

1282 second adjusting disk

1283 bullets

1284 spring arrangement

1285 hydraulic pressure regulator 1286 solenoid

1287 magnetic piston

1288 additional wave

1289 rotation axis of the output shaft

1290 bearing bore 1291 hydraulic oil hole

1292 hydraulic oil room

1300 split friction ring

1301 first friction cone

1302 second friction cone 1303 divided outer tread

1304 outer gap

1305 first outer tread half

1306 second outer tread half

1307 divided inner tread 1308 inner gap

1309 first inner tread half

1310 second inner tread half

1311 gap

1312 gap width 1313 friction ring rotation axis

1314 friction cone rotation axis

1315 Reibkegelrotationsachse

1316 chamfers

1317 total width

1330 first separate bearing glasses

1331 second separate bearing glasses

1332 shaft seal

1333 friction cone shafts

1334 fluid space

1335 further gear compartment

1336 Cone journal seal

1337 environment

1338 cover plate

1339 first half of the housing

1340 second housing half

1341 opposite side

1342 bearing eyeglass neck

1343 gear member

1344 differential gear

1345 distance

1346 output shaft rotation axis

1347 differential gear rotation axis

1508 friction ring gear housing

1521 friction ring

2008 Tapered friction ring housing

2277 output shaft

2301 first friction cone

2302 second friction cone

3362 conical friction ring gear

3270 entrance cone

3271 exit cone

3360 planetary gear

3362 conical friction ring gear 3363 input cone axis

3364 output cone axis

3365 output shaft

3366 Output shaft sun gear

3367 input shaft sun gear

3368 input shaft

3369 planetary gear

3370 planetary gear axle

3371 ring gear

3372 shift linkage

3373 footbridge

4008 conical friction ring housing

4270 entrance cone

4271 outlet cone

4360 double planetary gearbox

4362 conical friction ring gear

4363 input cone axis

4364 output cone axis

4365 output shaft

4366 Output shaft gear

4368 input shaft

4369 first planetary gear

4370 first planetary axle

4380 first output shaft sun gear

4381 second planetary gear

4382 second planetary gear axle

4383 planetary gear frame

4384 first shift linkage

4385 second shift linkage

4386 second output shaft sun gear

5002 cage

5011 rotary axis

5014 axial guide device

5018 guide shaft 5019 adjustable bridge

5021 friction ring

5022 first roll holder

5023 second roll holder

5390 eccentric motor

5391 linker

5392 eccentric rod

5393 Cage rod

5394 Cage handlebar pivot

5395 overload protection

5396 positioning ball

5397 positioning spring

5398 recording

5399 Positioning ball holder

5400 overload protection cover

5401 locking screw

5402 double arrow

6391 linker

6394 Cage Swivel Fulcrum

6395 Overload protection

6410 pressure element

6411 bearing ring

6412 tension element

6413 Anlenkerrohr

6414 first compression spring

6415 Anlenkerrohrkragen

6416 Linker tube flange

6417 tensile forces

6418 pressure forces

6419 second compression spring

6420 Circlip

7430 failover

7431 Cam disc

7432 cam follower 7433 Cam follower spring

7434 first driver

7435 second driver

7436 retaining washer

7437 drive axle

7438 drive

7439 drive shaft

7440 double arrow

7441 Holding friction spring

7442 release mechanism

7443 Release piston

7444 direction

7445 contact force

7446 sink

7447 height profile

Claims

claims:

1. friction ring gear with two spaced apart from each other by a gap rolling elements, which correspond to each other on axial Wälzkörperachsen circumferentially by a friction ring, wherein the friction ring in an axially freely displaceable Verstellbrücke a displacement aaxially disposed along the gap, characterized in that the Verstell¬ bridge is supported by a single axial guide device.

Second friction ring gear according to claim 1, characterized in that the adjusting bridge (19) axially only on one side (28, 30) with respect to a by the Wälzkörperachsen (24) vorgegebe¬ nen surface (29) is mounted.

3. friction ring gear with two spaced from each other by a gap rolling elements solved, which correspond to each other on axial Wälzkörperachsen circumferentially via a friction ring, in which the friction ring in an axially freely displaceable Verstellbrücke a displacement aaxially disposed along the gap axially displaceable, characterized the adjusting bridge (19) is mounted axially only on one side (28, 30) with respect to a surface (29) predetermined by the rolling body axes (24).

4. friction-ring transmission according to claim 3, characterized in that the adjusting bridge (19) on the cage (2) by means of a single axial guide means (14) is mounted.

5. Friction-ring transmission according to one of claims 1 to 4, characterized in that a Dreh¬ axis (11) of a cage (2) on one side with respect to a by the Wälzkörperachsen (24) predetermined surface (29) is arranged.

6. Friction-ring transmission according to one of claims 1 to 5, characterized in that a Dreh¬ axis (11) of a cage (12) outside the Verstellwegbereichs the Verstellbrücke (19) is arranged ange¬.

7. friction ring gear with two spaced apart from each other by a gap rolling elements which correspond to axia- len Wälzkörperachsen circumferentially via a friction ring with each other wel¬ Chem the friction ring in a cage axially freely guided Verstellbrücke by a Ver¬ adjustment axially along the gap is arranged displaceable, characterized in that the adjusting bridge (19) on a single axial guide means (14) is mounted.

8. Friction-ring transmission according to one of claims 1 to 7, characterized by an axial guide device (14) which has means for limiting the axial adjustment path.

9. friction ring gear according to claim 8, characterized in that the limiting means are directed approximately transversely to the axially extending adjustment component groups, such as cross struts (354, 355) of a cage (2).

10. Friction-ring transmission according to one of claims 1 to 9, characterized by a rotation lock (25), which prevents rotation of the adjusting bridge (19) about a guide axis (18) of an axial Füh¬ guiding device (14).

11. Friction-ring transmission according to claim 10, characterized in that the axial guide device has an internal anti-rotation device.

12. friction ring transmission according to claim 11, characterized in that a holding rail (27) and a guide axis (18) of the axial guide means (14) are identical.

13, friction ring gear according to claim 10, characterized in that the rotation lock (25) spaced from the axial guide means (14) is arranged.

14, friction ring gear according to one of claims 10 to 13, characterized in that the Dreh¬ fuse (25) is arranged on a housing (8) of the friction ring gear.

15. Friction-ring transmission according to one of claims 10 to 14, characterized in that the rotation lock (25) has a retaining rail (27) for holding the adjusting bridge (19).

16, friction ring gear according to claim 15, characterized in that the holding rail (27) is free of axial limiting means.

17, friction ring gear according to one of claims 1 to 16, characterized in that a Füh¬ approximately axis (18) or a cage (2) of the friction ring with respect to a housing (8) of the friction ring gear has an elastic bearing means (4, 5, 6).

18. Friction-ring transmission according to claim 17, characterized in that the elastic bearing device (4, 5, 6) comprises a leaf spring (4, 5, 6).

19, friction ring gear according to claim 17, characterized in that the elastic Lagerein¬ direction (104) comprises a rubber element (140).

20. Friction-ring transmission according to claim 17, characterized in that the elastic Lagerein¬ direction (4, 5, 6) comprises a spring element (4, 5, 6).

21, friction ring gear according to one of claims 17 to 20, characterized in that the Kä¬ fig (2) is made of a sheet metal body or a component of a sheet metal body and the bearing means (4, 5, 6) through an area of this sheet metal body is formed.

22, friction ring gear according to claim 21, characterized in that the sheet metal body wenigs¬ least a fastening region and an elastic region, wherein the elastic region is more elastic than the fastening region and an elastic bearing means (4, 5, 6) provides.

23. friction-ring transmission according to one of claims 21 or 22, characterized in that the

Sheet metal body in the region of the elastic bearing means (4, 5, 6) rotates ver¬ about its neutral fiber, preferably rotated by 90 °, is formed.

24. Friction-ring transmission according to one of claims 1 to 23, characterized in that the cage (2) is mounted by means of a bearing device with a motion compensation to a housing.

25, friction ring transmission according to claim 24, characterized in that the motion compensation um¬ a bushing (248A), a plate spring (248B) and / or a rubber bushing (248C) um¬ sums.

26. The friction ring transmission according to claim 1, wherein at least one bearing point of the friction ring with respect to the adjustment bridge and / or with respect to a further bearing point of the friction ring ) is arranged displaceably.

27, friction ring gear according to claim 26, characterized in that the adjusting bridge (19) has a joint between two bearing points.

28, friction ring gear according to one of claims 1 to 27, characterized in that a bearing point (423) is displaceably guided on a link arrangement (1100).

29, friction ring gear according to claim 28, characterized in that the link arrangement (1100) both a first group of components from a backdrop (1 103) with slide grooves (1 104, 1105) and a link plate (1106) and a second component group of sliding blocks (1 107, 1108).

30. Friction-ring transmission according to one of claims 1 to 29, characterized by means for Aus¬ steering a displaceable bearing point (423), with which the displaceable bearing point (423) of a zero axis (1115) from a zero position (1116) deflected becomes.

31, friction ring gear according to one of claims 1 to 30, characterized in that approximately transversely to a zero axis (1115) sliding blocks (1107, 1108) in slide grooves (1104, 1105) are arranged displaceably.

32. Friction-ring transmission according to one of claims 30 or 31, characterized in that deflection means comprise an adjusting lever (1110).

33. Friction-ring transmission according to claim 32, characterized in that the adjusting lever (1110) is mounted eccentrically to the zero axis (1 115).

34. Friction-ring transmission according to one of claims 30 to 33, characterized in that a zero position (1116) in an intersection of the zero axis (1 115) and the central longitudinal axis (1 114) of a control lever (1110).

35. Friction-ring transmission according to one of claims 30 to 34, characterized in that the Aus¬ steering means comprise a receptacle for a ring follower (1109).

36. friction ring according to claim 35, characterized in that the ring follower receiving a guide groove (1113).

37. Friction-ring transmission according to one of claims 1 to 36, characterized in that a ring follower (1109) is arranged on a link plate (1106).

38. Friction-ring transmission according to one of claims 30 to 37, characterized in that the Aus¬ steering means are mounted on a housing (8) of the friction-ring gear.

39. Friction-ring transmission according to one of claims 30 to 38, characterized in that the NuIl-axis (1115) substantially parallel to the gap (321A) of the axial guide means

(14) runs.

40. Friction-ring transmission according to one of claims 1 to 39, characterized by means for Ein¬ steering a displaceable bearing point (423), with which the displaceable bearing point, which from a zero axis (1 115) from a first zero position (1 116 ) is deflected, in another zero position on the zero axis (1 115) is deflected.

41. Friction-ring transmission according to claim 40, characterized in that the deflection means of the ver¬ storable bearing point (423) have a friction ring (21).

42. Friction-ring transmission according to one of claims 1 to 41, characterized in that the displacement bridge (19), optionally via a cage (2) by means of a linear drive (1220) with at least one lifting magnet (1224, 1225) for specifying the angle of attack is controllable.

43. Friction-ring transmission according to one of claims 1 to 42, characterized in that the friction ring gear has a linear drive (1220) with an adjustment axis (1227), which parallel to the axial guide means (14) and / or to a surface (29). formed by two Wälzkör¬ peraxes (24) runs.

44. Friction-ring transmission according to one of claims 42 or 43, characterized in that the linear drive (1220) has more than one linear drive motor.

45. Friction-ring transmission according to one of claims 42 to 44, characterized in that the linear drive (1220) has counter-rotating lifting magnets (1224, 1225).

46. The friction-ring transmission according to one of claims 42 to 45, characterized in that the linear drive (1220) has a pulse-pause control.

47. Friction-ring transmission according to one of claims 1 to 46, characterized in that at least one end of the adjustment path (1223) an adjustment path limit for the axially freely displaceable Verstellbrücke (19) is arranged.

48. Friction-ring transmission according to claim 47, characterized in that the Verstellwegbegrenzung an adjustable end stop (1240).

49. Friction-ring transmission according to claim 48, characterized in that the adjustable Endan¬ impact (1240) has a displaceable Endanschlagsbolzen (1241).

50. Friction-ring transmission according to claim 49, characterized in that the displaceable Endan¬ impact pin (1241) is arranged axially movable to the axial guide means (14).

51. Friction-ring transmission according to one of claims 48 to 52, characterized in that the adjustable end stop (1241) has a rotary magnet (1242).

52. Friction-ring transmission according to one of claims 49 to 51, characterized in that between the adjustable Endanschlagsbolzen (1241) and a rotary magnet (1242) a An adjusting disc (1250) for adjusting the displaceable Endanschlagsbolzen (1241) is arranged.

53. Friction-ring transmission according to one of claims 1 to 52, characterized by a pressure regulating device (1285) with static and dynamic pressure regulating means, the dynamic pressure regulating means being displaceable relative to the static pressure regulating means on or in one of the rolling bodies.

54. conical friction ring transmission according to claim 53, characterized in that the dynamic pressure regulating means are mounted on a supplementary shaft (1288) of a rolling body, which zu¬ at least partially disposed within the rolling body.

55. Friction-ring transmission according to one of claims 53 or 54, characterized in that the static pressure-regulating means are arranged on a further component of the friction ring which is foreign to the rolling elements.

56. Friction-ring transmission according to one of claims 53 to 55, characterized in that the dynamic pressure-regulating means comprise a piston (1287) revolving around a rolling body, which piston is excited by the static pressure regulating means.

57. Friction-ring transmission according to one of claims 53 to 56, characterized in that the static pressure regulating means comprise a lifting magnet (1286).

58. Friction-ring transmission according to one of claims 56 or 57, characterized in that the revolving piston (1287) has a magnetic pin, which is arranged within a Hubmag¬ net (1286).

59. Friction-ring transmission according to one of claims 1 to 58, characterized in that the Reib¬ ring (1300) has a split tread (1303, 1307).

60. Friction-ring transmission according to claim 59, characterized in that the split tread

(1303, 1307) has a gap (1304, 1308) which divides the split tread (1303, 1307) into a first tread half (1305, 1309) and dividing into a further tread half (1306, 1310) having a nip width (1312) which is at least 10% of the total width (1317) of the friction ring (1300), preferably at least 10% of the total effective width Tread is.

61. Friction-ring transmission according to one of claims 1 to 60, characterized in that Wälzkör¬ are arranged by Hauptkrafteinleitungsfrei in a friction-ring gear housing (8).

62. Friction-ring transmission according to one of claims 1 to 61, characterized in that in each case one side of the rolling bodies clamped together in one of a friction-ring gear housing (8) autarkic Wälzkörperlagereinrichtung on a friction-ring gear housing (8) are arranged.

63. Friction-ring transmission according to claim 62, characterized in that the self-contained Wälzkörperla¬ gereinrichtung comprises a steel frame.

64. Friction-ring transmission according to one of claims 1 to 63, characterized in that the Wälz¬ body are clamped on both sides clamped in self-contained Wälzkörperlagereinrichtungen.

65. Friction-ring transmission according to claim 64, characterized in that the self-contained Wälzkörper¬ storage facilities are interconnected by means of a steel frame.

66. Friction-ring transmission according to one of claims 62 to 65, characterized in that the au¬ tark Wälzkörperlagereinrichtungen in the friction-ring gear housing (8) are arranged.

67. Friction-ring transmission according to one of claims 62 to 66, characterized by a differential gear which is connected to the friction-ring transmission and itself or at least gear members of the differential gear is arranged on a self-contained Wälzkörperlagereinrichtung.

68. Friction-ring transmission according to one of claims 1 to 69, characterized by a Doppelplane¬ tengetriebe (4360).

69. Friction-ring transmission according to one of claims 1 to 68, characterized in that an articulated link of the adjusting bridge (19) or a guide cage (2) of the adjusting bridge (19) on the one hand with a drive, such as with an eccentric motor (5390), operatively connected and on the other hand at a Anlenkerdrehpunkt (5394) of the adjustment bridge (19) or the Führungskä¬ figs (2) is mounted, and the link arm (5391) has an overload protection (5395).

70. Friction-ring transmission according to claim 69, characterized in that the overload protection (6395) within the armature (6391) is arranged.

71. Friction-ring transmission according to one of claims 69 or 70, characterized in that the link (6391) has a tube (6413) in which the overload protection (6395) is arranged.

72. Friction-ring transmission according to one of claims 69 to 71, characterized in that the Überlastsicherung (6395) has non-destructive overload protection means.

73. Friction-ring transmission according to one of claims 69 to 72, characterized in that the overload safety device (6395) has at least one pressure element (6412) and / or at least one tension element (6410).

74. Friction-ring transmission according to claim 73, characterized in that the pressure element (6412) and the tension element (6410) are arranged displaceable relative to each other.

75. Friction-ring transmission according to claim 73 or 74, characterized in that both the Druck¬ element (6412) and the tension element (6410) relative to the link (6391) are mounted displaceably.

76. Friction-ring transmission according to one of claims 73 to 75, characterized in that the pressure element (6412) and the tension element (6410) in each case with a spring element (6414, 6419) are biased.

77. Friction-ring transmission according to one of claims 73 to 76, characterized in that the pressure element (6412) and the tension element (6410) are dynamically acting overload protection means.

78. Friction-ring transmission according to one of claims 73 to 77, characterized in that the tension element (6410) is mounted on a drive of the adjustment bridge (19) or on a drive of the guide cage (2) of the adjustment bridge (19).

79. Friction-ring transmission according to one of claims 73 to 78, characterized in that the

Pressure element (6412) on the adjusting bridge (19) or on the guide cage (2) of Verstell¬ bridge (19) is mounted.

80. Friction-ring transmission according to one of claims 69 to 79, characterized in that the overload safety device (6395) has destructible overload protection means (6420) as a predetermined breaking point.

81. Friction gear according to claim 80, characterized in that the predetermined breaking point is a statically acting overload protection means.

82. Friction-ring transmission according to one of claims 1 to 81, characterized by a fail-safe (7430) with means for adjusting the Verstellbrücke (19) or a guide cage (2) of the Verstellbrücke (19) in a Notlaufposition independent of a primary drive (7438 ) of the adjustment bridge (19) or of the guide cage (2).

83. Friction-ring transmission according to claim 82, characterized in that the fail-safe

(7430) represents a secondary drive for the adjustment bridge (19) or for the guide cage (2).

84. Friction-ring transmission according to one of claims 82 or 83, characterized in that the

Fail-safe (7430) between the adjustment bridge (19) and a prime mover (7438) of the adjustment bridge (19) is arranged.

85. Friction-ring transmission according to one of claims 82 to 84, characterized in that the fail-safe device (7430) has a blocking / unblocking device for a force flow between the displacement bridge (19) and the primary drive (7438).

86. The friction-ring transmission according to one of claims 82 to 85, characterized in that the adjustment means have a cam disc (7431) and a cam follower (7432) rolling thereon.

87. Friction-ring transmission according to claim 86, characterized in that the cam follower (7432) in an emergency position between two cams of the cam disc (7431) is arranged.

88. Friction-ring transmission according to one of claims 85 to 87, characterized in that the blocking / unblocking device for blocking the flow of force a release (7442), such as ei¬ nen electrically driven piston (7443), and to unlock the power flow Einrü¬ Cker, such as a spring element (7441), having. Friction-ring transmission according to one of claims 1 to 88, characterized in that the Wälz¬ body, in particular the friction cone, the friction ring and / or provided Wälzkörperwellen, such as additional waves of a Reibkegels, are made of steel.