WO2011160621A2 - Transmission à cônes et anneau de friction - Google Patents

Transmission à cônes et anneau de friction Download PDF

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Publication number
WO2011160621A2
WO2011160621A2 PCT/DE2011/001360 DE2011001360W WO2011160621A2 WO 2011160621 A2 WO2011160621 A2 WO 2011160621A2 DE 2011001360 W DE2011001360 W DE 2011001360W WO 2011160621 A2 WO2011160621 A2 WO 2011160621A2
Authority
WO
WIPO (PCT)
Prior art keywords
friction ring
adjusting
bridge
friction
gap
Prior art date
Application number
PCT/DE2011/001360
Other languages
German (de)
English (en)
Other versions
WO2011160621A3 (fr
Inventor
Ulrich Rohs
Christoph DRÄGER
Werner Brandwitte
Original Assignee
Ulrich Rohs
Draeger Christoph
Werner Brandwitte
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from DE201010025007 external-priority patent/DE102010025007A1/de
Priority claimed from DE201010025027 external-priority patent/DE102010025027A1/de
Application filed by Ulrich Rohs, Draeger Christoph, Werner Brandwitte filed Critical Ulrich Rohs
Priority to JP2013515693A priority Critical patent/JP2013529759A/ja
Priority to DE112011102103T priority patent/DE112011102103A5/de
Priority to CN201180030665.1A priority patent/CN102959278B/zh
Publication of WO2011160621A2 publication Critical patent/WO2011160621A2/fr
Publication of WO2011160621A3 publication Critical patent/WO2011160621A3/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H15/00—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by friction between rotary members
    • F16H15/02—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by friction between rotary members without members having orbital motion
    • F16H15/04—Gearings providing a continuous range of gear ratios
    • F16H15/42—Gearings providing a continuous range of gear ratios in which two members co-operate by means of rings or by means of parts of endless flexible members pressed between the first mentioned members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
    • F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
    • F16H37/021—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings toothed gearing combined with continuous variable friction gearing

Definitions

  • the invention relates to a conical friction ring transmission with two friction cones spaced apart from each other by a gap, which is arranged so as to be displaceable over a friction ring which passes through the gap around one of the two friction cones and is displaceable along the gap via an adjustment bridge freely displaceable along an adjustment bridge path wherein the adjusting bridge is supported on the one hand via an axial guide device which defines the Verstell Portugalnweg and tiltable, and wherein the adjusting bridge on the other hand is mounted on an axial guide means and having means for adjusting a friction ring.
  • Such conical friction ring transmissions are known from the prior art, as described, for example, in EP 0 878 641 A1, EP 0 980 993 A2 or WO 2006/012892 A2, wherein, on the one hand, the adjustment bridge is housed in a cage or by a one-sided one Guide rod can be held as an axial guide means and articulated about this, to effect a tilting of the friction ring, and on the other hand, the Verstell Georgia in a cage, held by two parallel sides of the two friction cone arranged axes, which are connected by two connecting rods, as an axial guide device and is axially displaceable along these axes and has an adjusting device, via which an adjustment angle of the friction ring can be influenced.
  • the term “adjustment bridge” designates an arrangement that can be displaced with the friction ring, but does not rotate with the friction ring that the adjustment bridge can in particular be followed by a displacement of the friction ring caused by other means, such as occurs when the friction ring is adjusted in its angle.
  • the term “friction ring” is understood to mean a device by means of which a contact is made between the two friction cones, so that forces, in particular torques, can be transmitted from one friction cone to the other friction cone.
  • the corresponding friction cone are arranged axially parallel to each other in the opposite direction, so that the tip of a cone is on the side of the stump of the other cone and vice versa.
  • both friction cones preferably have the have the same cone angle, but may have different radii, in order to be able to choose a basic ratio of the conical-friction ring gear in this way.
  • a friction ring in another embodiment may also be of the form in which it is arranged only in the gap between the two friction cones and none of the friction cone surrounds or in which he encompasses both friction cone, wherein in this Embodiments for the friction ring and a modified storage would have to be provided if necessary.
  • axial guide device means any device which is suitable for supporting the adjustment bridge in the friction-ring transmission such that the adjustment bridge can be displaced axially along the axial friction-cone axes in the region of an adjustment path and thus also axially along the gap Otherwise, the above-mentioned cage acts as such an axial guide device, as a result of which the axial guide device limits the degrees of freedom of the bridge part.
  • the adjustment path of the adjustment bridge can also have further directional components, as long as the adjustment bridge can follow the movement of the friction ring in the gap between the two friction cones.
  • a part of the axial guide device is designed such that this part only allows rotation about the displacement in the plane perpendicular to the adjustment, which can be easily realized for example by a circular axis. In this case, it may be sufficient if the adjusting bridge is sufficiently fixed with respect to the rotation or with respect to a movement in this plane, for example by the friction ring itself.
  • another part of the guide means for example by a tongue and groove guide, are used, by which the rotation about the adjustment can be prevented.
  • the friction cone rotates about an axis of rotation when it is adjusted by the adjustment angle, wherein this axis of rotation does not necessarily have to lie in a plane spanned by the Reibkegelachsen plane.
  • the axis of rotation has at least one component which is parallel or real parallel to a plane spanned by the Reibkegel axis sen.
  • the axial guide device is formed, inter alia, tiltable.
  • This can be realized, for example, that it is suitably stored or provided by thin-walled areas or the like an articulated connection that allows tilting.
  • This tilting causes a corresponding movement of the adjustment bridge, whereby then the friction ring is adjusted in its angle.
  • the axial guide means of the adjustment of the friction ring can be influenced accordingly, so that in this way the displacement of the friction ring and thus the transmission ratio can be defined.
  • tilting can be caused in any suitable form. Preferably, this is done by a corresponding actuator, as well known from the above-mentioned prior art.
  • a conical-friction ring transmission is proposed with two friction cones spaced apart from each other by a gap, which is arranged so as to be displaceable over a friction ring that passes through the gap around one of the two friction cones and is displaceable along the gap via an adjustment bridge that is freely displaceable along an adjustment bridge path.
  • the adjustment bridge is mounted via an axial guide device and wherein the conical friction ring gear characterized in that an arranged on the adjusting Verj ei device is controlled by means of a parallel positionable slide rail.
  • the control by means of the parallel positionable slide advantageously allows exact control of the adjusting device, wherein the term "parallel” expresses that the slide interacts substantially translationally, ie without rotational component, movable with the adjusting device and on a housing or Frame of the transmission is arranged.
  • the direction of movement of the slide rail at a right angle to a direction of displacement of the verse part bridge, the Verstell stipulatenweg be aligned, whereby the exact driving of the adjusting device is made particularly advantageous.
  • the direction of movement of the slide in an angle, that is not parallel extends to the displacement direction of the adjusting bridge in order to be able to control the adjustment arranged on the adjustment in a suitable manner on the slide.
  • the slide rail can also be guided, for example, on at least one straight-line rail guide, in particular on two parallel rail guides.
  • the adjusting device is arranged on the adjusting bridge and accordingly shifts together with the friction ring.
  • the adjustment angle and the neutral orientation of the friction ring are determined by the displacing with the friction ring adjusting device.
  • the adjusting device can also be controlled via subassemblies which are not associated with it, for example via tiltable slide rails, which are already known from the prior art, or else via the slide rails which can be positioned in parallel. The latter cause, as already explained above, in deviation from the tiltable slides an extremely precise control, which can be done in particular regardless of the position of the friction ring with the same precession.
  • the parallel positionable slide is driven by a spindle drive, whereby an extremely precise drive and thus a precise control of the adjusting device is made possible.
  • a parallel positionable slide rail a tiltable slide rail via a spindle drive is driven.
  • such a drive has proven to be advantageous regardless of the other features of the present invention.
  • a conical friction ring transmission is proposed with two mutually spaced by a gap friction cones, which rotates about a friction ring which passes through the gap to one of the two friction cone and along the gap via a freely displaceable along a Verstelleaunweges adjustable bridge is arranged to be displaceable, wherein the Verstellmaschine is mounted on an axial guide means and wherein the conical friction ring is characterized in that an adjusting device arranged on the Verstellmaschine is driven by a spindle drive.
  • the spindle drive advantageously offers the possibility of driving the adjusting device more precisely or of positioning the friction ring more precisely in the conical-friction-ring transmission via the adjusting device.
  • the spindle drive it is possible in this case for the spindle drive to be designed either directly on the adjusting device or directly on the slide rail explained above.
  • the spindle drive comprises a ball screw or a roller screw, which advantageously a very high accuracy for the control or for the drive of the adjusting device can be achieved can.
  • a conical friction ring transmission is proposed with two friction cones spaced apart from each other by a gap, which rotates about one of the two friction cones through a friction ring which passes through the gap and along the gap over a free axis Verstellmaschinenweges displaceable Verstellmaschine is arranged displaceably, wherein the Verstellmaschine is mounted on an axial guide means and wherein the conical friction ring is characterized in that an adjusting arranged on the adjusting VerstellISSISS is driven by a stationary drive shaft which interacts with a corresponding with the adjusting device output on the Verstellmaschine ,
  • the drive shaft is a profiled shaft or a rail, whereby the drive shaft can be brought into positive engagement with the hereby interacting subsequent components of the output and this form-fitting naturally, in particular against friction, the Operational safety increased.
  • the drive shaft deviating from a round cross section also have a rectangular or a poly
  • the term "stationary” is hereby used synonymously with the term “housing-fixed”, wherein the drive shaft along the Verstellmaschinenweges is not arranged to be displaced.
  • a “stationary” component thus does not shift its position relative to a housing of the conical-friction ring transmission, although expressly a rotational degree of freedom of the component "stationary” is to be retained.
  • a rotatably mounted in the housing of Kegelreibringgetriebes spindle but also in the housing of Kegelreibringgetriebes friction cone of Kegelreibringgetriebes are therefore "stationary", this definition does not apply to the displaceable friction ring and the corresponding following Verstellmaschine and carried by this adjusting device.
  • the parallel positionable slides are excellent because of their immutability in terms of the angle to the Verstellmaschinenweg, as this also represent the above-described spindle drive or the above-described drive shaft, so that here also controls the arranged on the Verstellmaschine adjustment regardless of the axial position of the adjustment can be done on their Verstell vitenweg.
  • the above-mentioned solutions based on the common inventive basic idea to control the drive arranged on the adjusting Verstell responded by a respect to the Verstellmaschinenweg independent mechanical drive or driven, which is independent by an angle to the Verstelleaunweg mechanical transmission part for the drive or for the Control of the adjusting device can be achieved.
  • the term refers to any energy-converting device with which mechanical energy can be provided as a drive for the adjusting device.
  • motors in particular electric motors, but also hydraulic or pneumatic motors, as well as linear drives, or electromagnets or piezoelectric drives in question, in particular, the number of mechanical assemblies in the use of linear motors can be reduced to a minimum.
  • the electric motors can be designed as stepper motors.
  • the axial guide device of the conical-friction ring transmission it is advantageous if it is arranged stationarily with respect to the cone axes.
  • the stationarily arranged guide means thus provides high reliability, but can also contribute to an increase in the stability or rigidity and thus for an accurate positioning of the adjustment. It is possible, as in the guide for the slide also that the guide device has at least one or at least two parallel guided sliding guides.
  • the term "stationary" also refers to a housing-fixed coordinate system when the cone axes are arranged fixed to the housing.
  • an advantageous operationally reliable angle adjustment can also be achieved in a conical friction gear in an advantageous embodiment in that the adjusting bridge has at least two guide points for the friction ring and at least one of the two guide points on the adjusting device is adjustable.
  • the two guide points In this case, for example, in each case two guide wheels revolving on both sides of the friction ring, for example a guide wheel arranged in the ring plane, which surrounds the friction ring with two flanks, or for example one or two corresponding scenes or two corresponding guide surfaces. If both guide points are adjustable depending on the specific configuration of the conical-friction ring transmission, an opposite adjustment of both guide points offers further advantages, since in this case stresses can be avoided.
  • the conical-friction-ring transmission has a mechanical feedback between the axial position of the friction ring and the adjusting device.
  • This mechanical feedback which may consist of, for example, a lever mechanism, in particular, provides reliability in the event of failure of an electrical control of the conical-friction ring transmission.
  • the friction ring is moved via the mechanical feedback position-controlled in the preselected before the failure of the electrical position.
  • the control of the friction ring is simplified, since only a desired position of the friction ring and not the actual position of the friction ring needs to be adjusted, since the friction ring is positioned accordingly by the feedback itself.
  • a conical friction ring gear is proposed with two spaced apart from each other by a gap friction cones over a friction ring, which passes through the gap to one of the two friction cone revolves and along the gap over a freely along an adjustment path displaceable adjusting bridge is arranged displaceably, wherein the adjusting bridge is mounted on an axial guide means and wherein the conical friction ring transmission is characterized by a mechanical feedback between the position of the friction ring and the position of the matterssseimichtung which defines the Verstell Portugalnweg and tilted.
  • a conical-friction ring transmission with a mechanical feedback provides a mechanical, fixed position adjustment such that the desired ring setting needs to be specified only by a corresponding control of the conditional by the feedback control loops. Specifically, this means that only a desired position of the friction ring needs to be preset and the regulation of the final position of the friction ring is oriented at the previously set value until the position of the friction ring corresponds to the desired value.
  • the fact is also advantageous that the energy for the actual adjustment of the friction ring by the proper motion and thus can be removed from the drive of the conical friction ring, since the kinematics of the friction ring from the contact of the friction ring with the results in two cones.
  • the friction ring is moved out of its stable and stationary position by forces which arise and act on the frictional contact, if these forces acting on the frictional contact are no longer in equilibrium. This is the case when the friction ring is rotated by the guide means by a pivot angle, wherein the pivot angle is proportional to the total force acting on the ring and thus proportional to the adjustment speed of the friction ring. Consequently, the presetting of the desired friction ring position requires only a minimum of energy, since only at the beginning of the wandering of the friction ring the angle of rotation needs to be adjusted.
  • the feedback has the further advantageous effect on the conical friction ring transmission that in case of failure of an actuator for controlling the adjusting device, the angle of the friction ring initially in its predetermined by the actuator at the time of failure position remains and that thereby sudden changes omit the transmission behavior.
  • the feedback is mechanically implemented, whereby a high reliability can be achieved even in the event of a power failure.
  • the feedback can also be done electronically, for example by an electronic position sensor, which in turn acts on the setting mechanism via an actuator.
  • the adjusting bridge is mounted via an axial guide means which defines the Verstell viten- and tilted via an actuator, wherein the actuating drive is operatively connected to the axial guide means via a control gear and wherein Means are provided for determining the position of the friction ring, which act mechanically on the control behavior of the adjusting gear.
  • the setting behavior can be, for example, the adjustment speed, whereby depending on the difference between the actual position of the friction ring and the desired position of the friction ring, a different setting speed can be set automatically.
  • a local specification for the actuating gear can be made by the determination means and thus directly to be reached a position of the adjustment bridge can be specified.
  • the determination means for determining the position of the friction ring can also be designed mechanically, whereby advantageously additional control algorithms, in particular electronic assemblies, can be dispensed with.
  • the action of the determination means on the control behavior of the adjusting gear via a planetary gear.
  • a planetary gear but also another conceivable transmission is both compact and precise executable and combined with little constructive effort with an electric motor drive or an electric actuator. As can be seen immediately, an electrical control is thus further complemen- tary readily implementable.
  • the lever arm may have a slot, whereby in particular translational and rotational movements, as they occur in a multi-layered form in a conical friction ring gear, for example in a displacement of the adjustment bridge, an axial guide means or the angle of the friction ring, are coupled easily and reliable.
  • the lever arm can represent an arm of a toggle lever, so that the corresponding advantages can be implemented even in a toggle mechanism, which contributes accordingly to operational safety.
  • the determination means may comprise a toothed belt.
  • a toothed belt As a result, for example, external requirements, which are provided by third parties, such as OEMs or engine manufacturers to the transmission, can be implemented more easily. Toothed belts can, but need not, be used permanently without any lubricant, which, for example, compared to chains, have a much lower noise emission and at the same time can reduce the total mass of the conical-type transmission over other applications.
  • the conical friction ring gear can have means for reversing the direction of action of the determining means in their action on the setting behavior of the adjusting gear, wherein such reversal of the direction of effect is advantageous for the reasons mentioned above, if the positioning of the friction ring is stable only in one direction of rotation.
  • the effective direction reversing means may comprise a brake-adjustable planetary gear.
  • a planetary gear is particularly space-saving and reliable applied to a conical friction ring gear, with these benefits also affect the effective direction reversing, [55] include the effective direction reversal a lever assembly with a dead center, where two directions of movement of the levers to each other are possible, and An actuator for selectively setting the direction of movement, also a very simple direction of direction can be realized, which also builds very reliable.
  • the adjuster can be controlled mechanically or electrically.
  • the adjuster may be a spring arrangement that biases a lever in the dead center in one direction so that it leaves the dead center in one direction. If the actuator acts in a different direction, the lever leaves the dead center in a different direction.
  • FIG. 1 shows a device for adjusting a friction ring angle with a parallel positionable slide rail
  • Figure 2 shows a further embodiment of a device for adjusting a friction ring angle with an electro-motor actuator on the adjustment bridge;
  • FIG. 3 shows a further embodiment of a device for adjusting a friction ring angle with a mechanical actuator
  • Figure 4 is a detail view of the arrangement of Figure 3;
  • Figure 5 is a schematic diagram of an adjusting device and a control for a
  • Adjustment device with mechanical feedback in a schematic plan view with a schematic partial view of the side of a setting gear
  • Figure 6 shows the adjusting device and control with mechanical feedback of Figure 5 in a perspective view
  • FIG. 7 shows a further adjusting device and control for the adjusting device with mechanical feedback in the position of an average transmission ratio
  • FIG. 8 shows the adjusting device and the control according to FIG. 7 in the position of a large transmission ratio
  • FIG. 9 shows the adjusting device and the control according to FIGS. 7 and 8 in FIG.
  • FIG. 10 shows an adjusting device and control for the adjusting device with mechanical feedback and with a switching unit for reversing the direction of action in a schematic front view
  • Figure 11 shows the adjusting device and control with mechanical feedback of Figure 10 in a schematic plan view
  • FIG. 12 shows a further adjustment device and control for the adjusting device with mechanical feedback and with a switching unit for reversing the direction of action in a schematic front view
  • FIG. 13 shows the adjusting device and control with mechanical feedback of Figure 12 in a schematic plan view
  • FIG. 14 shows a further adjusting device and control for the adjusting device with mechanical feedback and with a switching unit for reversing the direction of action in a schematic front view;
  • Figure 15 shows the adjusting device and control with mechanical feedback of Figure 14 in a schematic plan view
  • FIG. 16 shows a further adjusting device and control for the adjusting device with mechanical feedback and with a switching unit for reversing the direction of action in a schematic front view;
  • FIG. 18 shows a further adjusting device and control for the adjusting device with mechanical feedback and with a switching unit for reversing the direction of action in the front view.
  • a first embodiment as shown in particular in Figure 1, has an adjusting device 2 of a conical-friction ring 1 - not shown in Figure 1, wherein in the present case similarly effective components of the various embodiments are numbered identically - via a friction ring 6, which a friction ring 5 for determining a friction ring position leads, which interacts with friction cones 3 of the conical friction ring 1 in a conventional manner.
  • the adjusting device 2 has an adjusting bridge 8 which carries the friction ring guide 6 and, within the adjustment 2 by means of two axial guide devices or two Verstelleau- guides 9 translationally substantially in the direction of a rotation axis (not shown) of a gap between the friction cones 3 in a conventional manner.
  • a slide rail 1 1 is arranged in the adjustment device 2.
  • This slide rail 11 in turn is arranged to be displaceable parallel to two sliding guides 12, wherein both slide guides are substantially perpendicular to the axis of rotation and thus parallel to a rotation axis containing rotation plane, which in turn is pierced perpendicularly through the axis of rotation of the friction ring 5.
  • Also used for adjusting the slide 1 1 spindle drive 13 is aligned parallel to the two sliding guides 12 in this embodiment, but this is not necessary for adjusting the slide 1 1 necessary. In this respect, it is also possible to arrange the spindle drive 13 askew to the two sliding guides 12.
  • the two sliding guides 12 may be at an angle to the plane of rotation.
  • the slide 1 1 is coupled to the friction ring 5 via a steering slide 10 which controls an adjustable, in this embodiment, two guide wheels friction ring guide 7, which in the slide rail 1 1 substantially along an adjustment path of the friction ring 5 in a first Displacement direction is arranged displaceable.
  • a second displacement direction of the steering slide 10 is set at the adjusting bridge 8, whereby the steering slide 10, when the slide 1 1 is guided parallel to the plane of rotation of the friction ring 5, is displaced within the adjustment bridge 8 relative to the friction ring 5.
  • This displacement of the steering slide 10 has the consequence that the friction ring 5, since the displacement path of the steering slide 10 within the adjustment 8 is not parallel to the plane of rotation of the friction ring 5, tilted.
  • shaft 15 acts on a switching shaft 16 (numbered exemplarily in FIGS. 3 and 4), which is operatively connected to an adjustable friction-ring guide 7 and is capable of adjusting this friction-ring guide 7 parallel to the axis of rotation of friction-ring 5.
  • the adjustable friction ring guide 7 provided on the adjusting bridge 8 causes, as in the embodiment explained above, tilting of the friction ring 5, whereby the friction ring 5 is automatically displaced. With the displacement of the friction ring 5 takes place, as can be seen immediately on the friction ring 6 but also on the adjustable friction ring 7, a displacement of the entire adjustment bridge 8 along the two Verstell stipulaten Replacementen. 9
  • a further embodiment of a conical-friction ring transmission 1 with an adjusting device 2 is explained with reference to FIGS. 5 and 6, wherein the adjusting device 2 has a mechanical feedback of the position of the friction ring 5 or the adjusting bridge 8 by means of a feedback transmission 30.
  • the adjustment bridge guide 9 is rotatably arranged about a Verstell vitenachse 18 in this embodiment.
  • a feedback coupling rod 33 is arranged on the adjusting bridge 8 or on a displaceable feedback axis 36, which returns the current position of the adjusting bridge 8 to the feedback gear 30.
  • This feedback of the feedback coupling rod 33 takes place via a feedback lever 31, which is operatively connected to the feedback coupling rod 33 by means of a feedback knee 35.
  • the feedback lever 31 acts on a ring gear 44 of a planetary gear 40
  • the Verstellkoppelstange 22 via a Verstellknie 23 and an adjusting lever 21 with a sun gear 41 of said planetary gear 40 is operatively connected.
  • a the adjusting lever 21 and the Verstellkoppelstange 22 including adjusting 20 is coupled to the feedback gear 30 via planetary gear 43 of the planetary gear 40, wherein a planetary carrier 42, on which the planet 43 are arranged on a control shaft 51 of a servo motor 50 are adjustable and wherein Adjusting 20 in this embodiment is part of a control gear of the conical friction ring 1, which is controlled by the servo motor 50 and on which the feedback mechanism 30 acts mechanically.
  • a feedback force 63 acts on the feedback coupling rod 33, which in turn results from an axial force 61 and a transverse force 62 of the adjustment bridge 8.
  • the feedback force 63 which moves the feedback lever 31 in the illustrated view counterclockwise, acts now, if the servo motor 50 remains in a fixed position, by means of the planet 43 on the adjusting lever 21, which is again adjusted in a clockwise direction and the Verstell stipulaten Entry 9 pivots back to its original position.
  • the adjustment bridge guide 9 is pivoted in an adjustment direction 76.
  • a walking of the adjusting bridge 8 in the direction of the large transmission ratio 74 wherein the feedback lever 31 is moved in the illustrated view in the clockwise direction and by means of the planetary gear 40, the adjusting lever 21 moves counterclockwise about its axis of rotation.
  • the conical friction ring transmission 1 has a lever arrangement with an actuating drive 52, which acts on an adjusting lever 53.
  • an adjustment of the actuator 52 acts in the adjustment direction 75 to smaller ratios 73 and in the adjustment 76 to larger ratios 74 initially on the adjustment lever 21, which is operatively connected by means of Verstellknies 23 with the lever 53, on the Verstell Supremen Entry 9 and on the adjustment bridge 8.
  • the adjustment bridge 9 is here also arranged rotatably about the Verstell vitenachse 18, It is understood that instead of the adjustment drive 52, a servomotor or other actuator may be provided.
  • a feedback lever 32 designed as a lever arm or toggle lever is arranged on the displaceable feedback axis 36 of the adjusting bridge 8, which rotates about a housing-fixed feedback axis 37 and thereby actuates a feedback coupling rod 34 of the feedback gear 30.
  • the interaction of the feedback lever 32 with the housing-fixed feedback axis 37 causes a groove or a slot in the feedback lever 32, by means of which or by means of which the adjustment bridge 8 actuates and guides the feedback lever 32.
  • the reaction of the feedback gear 30 on the adjusting knee 23 causes, if the actuator 52 is held, a reset of the adjusting 20, whereby the adjustment bridge 8 is in turn pivoted back to its original position.
  • the adjusting bridge 8 is only around the adjusting bridge axis 18 by means of the adjusting bridge guide 9 arranged displaceably.
  • the adjustment bridge 8 is guided on the Verstell stipulaten Entry 9 side facing away by means of Verstell Supremenfix réelle 17 slidably.
  • the adjustment bridge 17 leaves the adjustment bridge 8 a degree of freedom of movement in a plane on which the adjustment bridge axis 18 is perpendicular.
  • the adjustment keeps the possibility to pivot about Verstellmaschinenachse 18 and the Verstellmaschinenfix réelle 17 is at the same time fixed to the housing, which causes a significant reduction in vibration of the adjustment.
  • the friction ring 5 pivots about an axis which on the one hand with the adjustment bridge axis 18 coincides or at least parallel to it and on the other hand extends at least with a directional component parallel to a plane which is spanned by the cone axes 4 of the two friction cone 3 shown as an example.
  • a further embodiment of an adjusting device 2 for a conical-friction ring transmission 1 contains, in addition to the planetary gear 40 used for feedback, an additional gearbox interposed between the adjusting gear 20 and the planetary gear 40 for reversing the direction of action of the adjusting gear 20, as implemented in the exemplary embodiments described below.
  • the stable position of the friction ring 5 along the adjusting position 70 of the adjusting bridge 8 depends - depending on the concrete implementation of the friction ring and / or the feedback - inter alia, on the direction of rotation of the friction cone 3, since the direction of rotation of the friction cone 3 on the friction ring 5 acting forces and torques determine. If the direction of rotation in the conical-friction ring gear 1 changes, this also results in a change in the force relationships in frictional contact between the cones 3 and the friction ring 5, as a result of which the automatically controlled adjustment direction of the adjusting bridge 8 also changes. The reversal of motion of the adjustment bridge 8 thus also results in a reversal of the feedback of these by means of the feedback gear 30 to the planetary gear 40 result.
  • the cone friction gear 1 Because of the reversal of the feedback dynamics, the cone friction gear 1 according to FIGS. 10 and 11 therefore has a forwardly running bevel gear 89 and a backward-running bevel gear 90, which can be selectively driven by means of a switched via a switching unit 84 shift sleeve 85.
  • the planetary gear 40 controlled via the servomotor 50 is coupled in the illustrated embodiment by means of the planetary carrier 42 to a driving bevel gear 88, which in turn meshes with both bevel gears 89, 90.
  • the adjusting bridge 8 is mounted on the adjusting bridge guide 9 by means of a linear guide 82, which drives the friction ring 5 in a particularly wear-resistant and low-friction manner and, in particular, with a very high accuracy.
  • the switching unit 84 includes a toothed coupling 87 which fixes a planetary carrier 92 and a ring gear 94 of the switching unit 84 designed as a planetary gear can.
  • a predetermined by the servo motor 50 and, by the planet carrier 42 direction of rotation is thus passed unchanged when setting the planet carrier 92 and the ring gear 94 to the adjusting 20, as well as planet 93 of the switching unit 84 are fixed.
  • the toothed coupling 87 is actuated so that the planet carrier 92 is interconnected with a housing 95 and the direction of rotation of the ring gear 94 with respect to a sun gear 91 is changed via the planets 93.
  • the embodiments according to FIGS. 12 to 15 furthermore contain a toothed belt 83.
  • This toothed belt 83 which engages the ring gear 44 of the planetary gear 40, is coupled to the adjusting bridge 8 and in this case brings about the feedback on the adjusting bridge guide 9, which previously explained, about the Verstell vitenachse 18 is pivotally mounted in the adjusting device 2 and the Verstellmaschine 8 by means of the linear guide 82 on one side.
  • the adjustment bridge fixing 17 for stabilizing the adjustment bridge 8 is again provided in this embodiment.
  • the feedback of the adjusting bridge 8 with the planetary gear 40 is carried out in the embodiment of Figures 12 and 13, characterized in that the toothed belt 83 is connected to the adjustment bridge 8, and in the embodiment of Figures 14 and 15 via a toothed belt clutch 77 on the adjustment 8.
  • the toothed belt clutch 77 causes a fixed connection of the toothed belt 83 with the adjusting bridge 8, whereby a movement of the adjusting bridge 8 via the toothed belt 83 to the ring gear 44 of the planetary gear 40th is transmitted.
  • the control of the transmission ratio is thus similar to the embodiments described above.
  • the embodiment according to FIGS. 14 and 15 offers an adjustment possibility of the adjustment bridge 8 through a four-limb adjustment bridge guide 80.
  • Two parallel guided guide rods 79 of this four-membered adjustment bridge guide 80 which guide the adjustment bridge 8 Guide over the linear guide 82, although performed parallel to each other for adjusting the friction ring 5, but without performing a rotation about the Verstell vitenachse 18.
  • Only two pivotable guide rods 78 of the four-limb Verstellmaschinen Entry 80 are pivoted about the Verstell vitenachse 18 and about a not shown, however, the Verstell vitenachse 18 parallel axis and thus set the friction ring 5 at appropriate angles.
  • the tension of the toothed belt 83 changes only insignificantly.
  • the switching unit 84 or the ring gear 94 acts on the adjustment bridge guide 9, in this case on at least one of the two pivotable guide rods 78.
  • the toothed belt 83, which drives the ring gear 44, is connected to the adjustment bridge 8 via a Synchronous toothed belt clutch connected.
  • the two embodiments according to FIGS. 16 to 18 also have a four-limb adjustment bridge guide 80, but this consists of a rigid frame without pivotable guide rods 78.
  • the adjusting mechanism 20 acts directly on the adjustment bridge axis 18 which is arranged centrally on the four-membered adjustment bridge guide 80 and which in turn is operatively connected to the planetary gear 40 by means of the shake unit 84.
  • the interconnection or feedback of the adjusting bridge 8 with the four-limbed Verstell Georgian Entry 80 by means of the planetary gear 40 and the switching unit 84 is thus in accordance with the embodiments described above.
  • the servomotor 50 of the exemplary embodiment according to FIG. 18 is fixedly arranged on the adjusting bridge 8.
  • the servo motor 50 with the adjusting bridge 8 is arranged displaceably.
  • the ring gear 44 is now operatively connected by means of a rack 97 with the housing 95, whereby the movement of the adjusting bridge 8 causes the feedback to the planetary gear 40.
  • the switching unit 84 used for reversing the direction of action is arranged on a guide pivot axis 98 of a pivotable friction ring guide 96 which replaces the adjustment bridge axis 18 explained above.
  • the adjustment bridge 8 is arranged by means of the linear guide 82 only translationally on the Verstell Georgian Entry 9 movable and performs no own rotation more.
  • a control of the servomotor 50 causes logical, depending on the position of the shift sleeve 85 pivoting the pivotable friction ring 96 in clockwise or counterclockwise about the guide pivot axis 98.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Friction Gearing (AREA)

Abstract

L'invention concerne une transmission à cônes et anneau de friction comprenant deux cônes de friction qui sont espacés par un interstice et présentent un anneau de friction qui tourne autour de l'un des deux cônes de friction dans l'interstice et est disposé de manière à pouvoir être déplacé le long de l'interstice par l'intermédiaire d'un pont de réglage pouvant être déplacé librement le long d'une trajectoire de pont de réglage. Le pont de réglage est monté par l'intermédiaire d'un dispositif de guidage axial et présente un dispositif pour régler un angle de l'anneau de friction. Selon l'invention, pour que cette transmission présente une haute fiabilité, en particulier en cas de défaillance de la commande du basculement du dispositif de guidage, le dispositif de réglage est commandé au moyen d'une glissière pouvant être positionnée en parallèle.
PCT/DE2011/001360 2010-06-24 2011-06-24 Transmission à cônes et anneau de friction WO2011160621A2 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
JP2013515693A JP2013529759A (ja) 2010-06-24 2011-06-24 円錐摩擦リングギヤ
DE112011102103T DE112011102103A5 (de) 2010-06-24 2011-06-24 Kegelreibringgetriebe
CN201180030665.1A CN102959278B (zh) 2010-06-24 2011-06-24 锥形摩擦环传动装置

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE102010025007.4 2010-06-24
DE201010025007 DE102010025007A1 (de) 2010-06-24 2010-06-24 Kegelreibringgetriebe
DE201010025027 DE102010025027A1 (de) 2010-06-24 2010-06-24 Kegelreibringgetriebe
DE102010025027.9 2010-06-24

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WO2011160621A2 true WO2011160621A2 (fr) 2011-12-29
WO2011160621A3 WO2011160621A3 (fr) 2012-06-21

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CN (1) CN102959278B (fr)
DE (1) DE112011102103A5 (fr)
WO (1) WO2011160621A2 (fr)

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WO2014067509A1 (fr) * 2012-10-29 2014-05-08 Ulrich Rohs Variateur à cônes et anneau à friction

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Publication number Priority date Publication date Assignee Title
CN104006127B (zh) * 2014-06-06 2016-08-24 张阳松 无级变速器及设有该无级变速器的机动车
DE102014013468A1 (de) * 2014-09-17 2016-03-17 Ulrich Rohs Kegelreibringgetriebe und Verfahren zum Betrieb eines Kegelreibringgetriebes
CN105673834A (zh) * 2016-03-16 2016-06-15 浙江德孚力汽车变速箱有限公司 锥环式无级变速器传动环控制机构
CN112213123B (zh) * 2020-10-21 2022-05-20 浙江森森汽车零部件有限公司 一种汽车减震器性能检测装置

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EP0878641A1 (fr) 1995-11-16 1998-11-18 Rohs, Ulrich, Dr. Transmission avec éléments coniques et anneau de friction
EP0980993A2 (fr) 1998-08-18 2000-02-23 Rohs, Ulrich, Dr. Transmission avec éléments coniques et anneau de friction et méthode de commande du rapport de vitesses d'une telle transmission
WO2006012892A2 (fr) 2004-08-06 2006-02-09 Ulrich Rohs Mecanisme de transmission a anneau de friction comprenant deux corps de roulement places a distance l'un de l'autre autour d'une fente

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DE10303896A1 (de) * 2002-09-30 2004-06-17 Ulrich Dr.-Ing. Rohs Umlaufendes Getriebe
CN1623053B (zh) * 2002-10-07 2011-07-20 乌尔里克·罗斯 传动机构
KR101139182B1 (ko) * 2003-12-23 2012-04-26 울리히 로스 무단 변속장치
EP1729037B1 (fr) * 2005-05-30 2010-03-10 Getrag Ford Transmissions GmbH Transmission d'anneau de friction
DE102006023648B4 (de) * 2006-05-18 2009-08-13 Getrag-Ford Transmissions Gmbh Anpressvorrichtung für ein Kegelringgetriebe
DE102009032164A1 (de) * 2008-07-16 2010-01-21 Rohs, Ulrich, Dr. Ing. Reibringgetriebe mit einem Reibring und Verfahren zum Herstellen eines Reibkegels
JP5018684B2 (ja) * 2008-08-06 2012-09-05 アイシン・エィ・ダブリュ株式会社 無段変速機

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EP0878641A1 (fr) 1995-11-16 1998-11-18 Rohs, Ulrich, Dr. Transmission avec éléments coniques et anneau de friction
EP0980993A2 (fr) 1998-08-18 2000-02-23 Rohs, Ulrich, Dr. Transmission avec éléments coniques et anneau de friction et méthode de commande du rapport de vitesses d'une telle transmission
WO2006012892A2 (fr) 2004-08-06 2006-02-09 Ulrich Rohs Mecanisme de transmission a anneau de friction comprenant deux corps de roulement places a distance l'un de l'autre autour d'une fente

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2014067509A1 (fr) * 2012-10-29 2014-05-08 Ulrich Rohs Variateur à cônes et anneau à friction
JP2015532970A (ja) * 2012-10-29 2015-11-16 ロース，ウルリッヒ 円錐摩擦リング変速機
US9719582B2 (en) 2012-10-29 2017-08-01 Ulrich Rohs Conical friction ring transmission

Also Published As

Publication number Publication date
WO2011160621A3 (fr) 2012-06-21
CN102959278A (zh) 2013-03-06
JP2013529759A (ja) 2013-07-22
CN102959278B (zh) 2015-11-25
DE112011102103A5 (de) 2013-03-28

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