US20130143713A1 - Cone/friction ring transmission and method for a cone/friction ring transmission - Google Patents

Cone/friction ring transmission and method for a cone/friction ring transmission Download PDF

Info

Publication number
US20130143713A1
US20130143713A1 US13/817,010 US201113817010A US2013143713A1 US 20130143713 A1 US20130143713 A1 US 20130143713A1 US 201113817010 A US201113817010 A US 201113817010A US 2013143713 A1 US2013143713 A1 US 2013143713A1
Authority
US
United States
Prior art keywords
cone
friction ring
transmission
subsidiary
friction
Prior art date
Legal status (The legal status 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 status listed.)
Abandoned
Application number
US13/817,010
Other languages
English (en)
Inventor
Ulrich Rohs
Christoph Draeger
Werner Brandwitte
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Individual
Original Assignee
Individual
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
Application filed by Individual filed Critical Individual
Assigned to ROHS, ULRICH reassignment ROHS, ULRICH ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: BRANDWITTE, WERNER, DRAEGER, CHRISTOPH, ROHS, ULRICH
Publication of US20130143713A1 publication Critical patent/US20130143713A1/en
Abandoned legal-status Critical Current

Links

Images

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
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/26—Generation or transmission of movements for final actuating mechanisms
    • 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
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/66—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for continuously variable gearings
    • F16H61/664—Friction gearings
    • 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
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/66—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for continuously variable gearings
    • F16H61/664—Friction gearings
    • F16H61/6648—Friction gearings controlling of shifting being influenced by a signal derived from the engine and the main coupling
    • 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
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/66—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for continuously variable gearings
    • F16H61/664—Friction gearings
    • F16H61/6649—Friction gearings characterised by the means for controlling the torque transmitting capability of the gearing

Definitions

  • the invention relates to a cone/friction ring transmission, consisting of at least two subsidiary transmissions structured as cone/friction ring transmissions, and to a method for a cone/friction ring transmission having at least two subsidiary transmissions structured as cone/friction ring transmissions.
  • the power take-offs of the power take-off cones are connected with the planets of a planetary gear, so that a torque applied by the input cone is divided up among the power take-off cones, in each instance, and totaled up again by way of the planetary gear, where a constant speed of rotation of the planets as well as of the power take-off cones is forced to occur as the result of coupling of the planets.
  • this arrangement contains the problem that even tiny production tolerances or inaccuracies lead to friction losses between the friction rings and the cones.
  • each friction ring of each subsidiary transmission has an adjustment device that is mechanically independent of the others, which can be controlled a common regulation device.
  • the invention proposes a cone/friction ring transmission having at least two subsidiary transmissions structured as cone/friction ring transmissions, which have a first adjustment device for a friction ring of the first subsidiary transmission, and a second adjustment device for a friction ring of the second subsidiary transmission, whereby the cone/friction ring transmission has a regulation device for regulation of an axial position of the friction rings, and is characterized in that the regulation device has at least a first subsidiary regulation device having a first reference variable, and a second subsidiary regulation device having a second reference variable, which is separate from the first reference variable, whereby the first subsidiary transmission has the first subsidiary regulation device for regulation of the position of the friction ring of the first subsidiary transmission, and the second subsidiary transmission has at least the second subsidiary regulation device for regulation of the position of the friction ring of the second subsidiary transmission.
  • the use of regulation by means of a second subsidiary regulation device and a second reference variable separate from the first reference variable has the advantage that regulation of the position of the friction ring of the second subsidiary transmission, independent of production tolerances or inaccuracies, can take place.
  • a regulation device that makes the desired translation ratio of the transmission available by means of a control variable that is identical for both subsidiary transmissions, according to the state of the art, cannot be able to take the wear behavior in the two subsidiary transmissions into consideration in targeted manner, because the compulsory sameness of the speed of rotation of the two subsidiary transmissions can lead to increased slip in at least one of the subsidiary transmissions, or necessarily leads to an increased or undefined slip because of the unavoidable production tolerances.
  • a regulation device is implemented within an engine or transmission control device that is present, in any case, which device takes on all or most of the relevant control and regulation procedures in modern motor vehicles.
  • a regulation device is implemented within an engine or transmission control device that is present, in any case, which device takes on all or most of the relevant control and regulation procedures in modern motor vehicles.
  • such an engine or transmission control device that is present, in any case can be implemented with a regulating effect by means of inclusion in the regulation circuit described above.
  • the translation of the first subsidiary transmission can be regulated by means of a first subsidiary regulation device, which corresponds to a regulation device according to the state of the art, whereby, for example, the reference variable is a translation ratio predetermined by a characteristic field or a translation ratio otherwise predetermined by a control device.
  • a regulation variable of the first subsidiary regulation device is a reference variable of the second subsidiary regulation device.
  • a regulation variable of the first subsidiary transmission used according to this aspect of the invention can be, for example, the speed of rotation of the friction ring of the first subsidiary transmission or the speed-of-rotation slip at the friction ring of the first subsidiary transmission, or a torque transferred by way of the first subsidiary transmission.
  • the regulation variable of the first subsidiary transmission that is used is consequently linked with the second subsidiary regulation device in such a manner that the regulation variable of the first subsidiary transmission is a reference variable of the second subsidiary regulation device, and that a regulation variable of the second subsidiary regulation device, of the same type, in terms of value, as the regulation variable of the first subsidiary regulation device, is regulated to a corresponding value.
  • the reference variable of the first subsidiary regulation device can also be a reference variable of the second subsidiary regulation device.
  • a reference variable preset by a control device for example a transmission translation or a position of a friction ring of the first subsidiary transmission, but also an angular position of the first friction ring, can therefore also be used for regulation of the position of the friction ring of the second subsidiary transmission.
  • This method of regulation of the position of a friction ring of the second subsidiary transmission makes it possible to adjust the position of a friction ring of the second subsidiary transmission synchronous to the position of a friction ring of the first subsidiary transmission, and, if necessary, to balance out any production tolerances or inaccuracies by means of correcting the position of a friction ring of the second subsidiary transmission by way of the second subsidiary regulation device.
  • transmission control is also possible, by means of which the first subsidiary transmission and the second subsidiary transmission are regulated by way of the reference variable of the first subsidiary transmission, and in which correction of a slip value that is different in value at the friction rings takes place by way of correction of the position of the friction ring of the second subsidiary transmission, in that a position offset characteristic field is used as the reference variable for the second subsidiary regulation device.
  • a data set that is determined during running-in for example after assembly of a corresponding cone/friction ring transmission and before initial startup of the said cone/friction ring transmission, by means of measurement of same, for example on a test bench, can be used as the position offset characteristic field.
  • a characteristic field determined according to this method can be a two-dimensional diagram, for example, in which a correction variable is stored for every axial position of the friction ring of the second subsidiary transmission that is approached, which variable is necessary the amount of the required axial displacement of the friction ring of the second subsidiary transmission to the position set by the reference variable of the first subsidiary regulation device.
  • such a position offset characteristic field can also be recorded or changed during operation, by means of the existing transmission control device itself, if a device for detecting the slip that is applied to the friction rings is present and the values determined by it are evaluated in suitable manner. It is understood that such a position offset characteristic field can also be made available in various other ways,
  • the reference variable of the second subsidiary regulation device is a reference variable of the first subsidiary regulation device corrected by way of a position offset characteristic field.
  • the regulation process can be significantly simplified and accelerated during normal operation, or can be carried out with less computing effort.
  • first subsidiary transmission and the second subsidiary transmission have a common cone and a further cone, in each instance, that the friction ring of the first subsidiary transmission merely encloses the further cone of the first subsidiary transmission, and that the friction ring of the second subsidiary transmission merely encloses the further cone of the second subsidiary transmission.
  • the further cone of the first subsidiary transmission is connected to interact with a shaft, by means of a first transmission, particularly a gear wheel transmission, and the further cone of the second subsidiary transmission is also connected to interact with this shaft, by means of a second transmission, particularly a gear wheel transmission, whereby the first and the second transmission have an identical translation ratio.
  • a device for applying a press-down force can be provided on the common cone, instead of providing two different devices for applying the press-down force on two or more further cones. This has the advantage that a cost-advantageous transmission with relatively simple regulation of the press-down force, by means of a single unit, can be implemented.
  • cone/friction ring transmission consisting of at least two subsidiary transmissions structured as cone/friction ring transmissions, in which the subsidiary transmissions have an input cone and a common output cone, in each instance, and which is characterized in that the common output cone has a press-down device.
  • the subsidiary transmissions have an input cone and a common output cone, in each instance, and which is characterized in that the common output cone has a press-down device.
  • a cone/friction ring transmission consisting of at least a first subsidiary transmission structured as a cone/friction ring transmission and a second subsidiary transmission structured as a cone/friction ring transmission
  • a cone/friction ring transmission consisting of at least a first subsidiary transmission structured as a cone/friction ring transmission and a second subsidiary transmission structured as a cone/friction ring transmission
  • at least two cones from different subsidiary transmissions have a press-down device, in each instance, whereby the two press-down devices have a device for equalizing the difference in the press-down forces.
  • Force equalization performed according to this aspect of the invention can advantageously be implemented, in this connection, by means of a scale, whereby this scale can be a hydraulic scale or a mechanical scale.
  • a scale that acts hydraulically, between two press-down devices can be structured, for example, in such a manner that two oil-filled pressure chambers of the press-down device, filled with oil, are connected with one another by means of a line system, in such a manner that hydraulic pressure equalization between the press-down devices takes place.
  • An alternative scale which works mechanically, can be structured, for example, by means of a skillful arrangement of levers, whereby preferably, two levers having the same length and connected to interact opposite to one another, to balance out forces between the two press-down devices according to the balance scale principle, are provided. Also, such equalization can take place, for example, by means of pulleys and cables or similar arrangements. In this regard, force equalization can also take place mechanically.
  • a skillful arrangement of devices for applying a press-down force is also a possibility, whereby such a spring package or other type of device for applying a press-down force only has to be provided either in a press-down device, or can be provided at the pivot point of the lever mechanism of the mechanical force equalization device.
  • a previously proposed possibility of using a second subsidiary regulation device for a second subsidiary transmission consists in using a speed of rotation of a friction ring as a regulation variable of a regulation segment. It is therefore proposed to make available a cone/friction ring transmission consisting of at least one input cone and one output cone, and a friction ring disposed between the input cone and the output cone, enclosing at least one cone, which is characterized by a device for measuring the speed of rotation of the friction ring.
  • measuring the speed of rotation of the friction ring means a direct measurement of the physical speed of rotation of the friction ring that is actually present. It is therefore proposed that the device for measuring the speed of rotation of the friction ring preferably detects the speed of rotation of the friction ring directly at the friction ring, preferably by means of a sensor system that acts on the friction ring.
  • directly measurement of the speed of rotation is understood to mean measurement of the speed of rotation that does not take place by means of modules that are acted on by a main torque that passes through the corresponding subsidiary transmission and corresponds to the torque that acts on the input cone of the subsidiary transmission, in each instance.
  • the measurement can be undertaken by means of a sensor system that engages directly on the friction ring, for example by means of an inductive measurement or by means of an optical measurement, if the friction ring has corresponding devices, such as, for example, corresponding teeth or recesses.
  • a corresponding measurement can be carried out by way of a friction ring guide and the guide wheels that engage directly on the friction ring, for example.
  • an indirect determination of the speed of rotation of the friction ring is also possible, in which the speed of rotation of the cones that are connected to interact, by means of the friction ring, is detected, and the physical speed of rotation of the friction ring is detected by way of physical and/or mathematical models. In this connection, however, it is very difficult to include slip, which might occur differently in the output cone and the input cone, in these models.
  • the friction ring is freely movable in its axial position, it is then otherwise generally necessary to also dispose a measurement device in axially displaceable manner for a direct measurement of the speed of rotation of the friction ring, so that the measurement device assumes a non-changeable position relative to the friction ring. Therefore a guide device that is axially displaceable with the friction ring is proposed, on which the measurement device is disposed.
  • the cone/friction ring transmission can have not only the device for measuring the speed of rotation of the friction ring, but also a device for measuring the speed of rotation of at least one cone.
  • a cone/friction ring transmission having a device for measuring the speed of rotation of the friction ring particularly if this detects the speed of rotation directly on the friction ring, as well as a cone/friction ring transmission having a device for measuring the speed of rotation of at least one of the cones are correspondingly advantageous, even independent of the other characteristics of the present invention.
  • torque can also be used as the regulation variable for a cone/friction ring transmission, particularly as the regulation variable for a second subsidiary regulation device of a second subsidiary transmission, in other words for an overall transmission that comprises two cone/friction ring transmissions.
  • a cone/friction ring transmission consisting of at least one input cone and one output cone and a friction ring disposed between the input cone and the output cone, enclosing at least one cone, which is characterized by a torque measurement device, is advantageous.
  • the torque measurement device comprises contact-free data transmission
  • influences of the torque measurement device on the cone/friction ring transmission itself can be minimized; likewise, wear can be restricted to a minimum.
  • optical and/or inductive data transmission is possible for contact-free data transmission.
  • the modules of the torque measurement device that rotate and require energy can be supplied with energy in contact-free manner, for example optically or inductively.
  • the term data transmission comprises all data or measurement values, whether analog or digital, which provide information about the torque or stand in proportionality to the applied torque.
  • these can be measurement values that are already digitalized, which are supposed to be transferred from the rotating modules of the torque measurement device to fixed modules.
  • these can be measurement signals that still require further processing.
  • the torque measurement device comprises a cone shaft, in other words a shaft that is connected with one of the cones as a drive shaft or power take-off shaft.
  • the torque measurement device can have a module that is connected in one piece with the cone.
  • the measuring modules can be connected with the cone in rigid and at most bending-elastic manner, so that the torque measurement device, although it can be installed and removed, can measure the torque applied to the cone/friction ring transmission or to the corresponding cone directly, if at all possible.
  • a corresponding torque measurement device is provided both on the input cone and on the output cone, whereby a statement concerning the slip of the friction ring can also be made by means of the difference in the torques.
  • a cone/friction ring transmission consisting of at least one input cone as well as one output cone and a friction ring disposed between the input cone and the output cone, enclosing at least one cone, which is characterized in that a torque converter is disposed between an input shaft of the cone/friction ring transmission and the input cone.
  • this torque converter can be used for a cone/friction ring transmission, in such a manner that the input cone has a lower torque than the input shaft.
  • a cone/friction ring transmission is advantageously made available, which can transfer significantly greater drive power by means of the torque conversion on the input side.
  • the torque converter can comprise a gear-wheel transmission.
  • a gear-wheel transmission can be produced in particularly cost-advantageous manner, and therefore the advantages that result are not or insignificantly cancelled out by higher costs.
  • an input-side gear wheel of the gear-wheel transmission has an even number of teeth
  • an output-side gear wheel of the gear-wheel transmission has an odd number of teeth.
  • This embodiment can also be advantageous for a cone/friction ring transmission vice versa, in that the input-side gear wheel of the gear-wheel transmission has an odd number of teeth, and the output-side gear wheel of the gear-wheel transmission has an even number of teeth.
  • a method for a cone/friction ring transmission or for operation of a cone/friction ring transmission consisting of at least one input cone as well as one output cone and a friction ring disposed between the input cone as well as the output cone, enclosing at least one cone is proposed, which is characterized in that a torque of the input cone is converted to a lower torque, with reference to an input shaft of the cone/friction ring transmission.
  • the incoming torque is reduced, by means of the torque converter used ahead of the cone/friction ring transmission or ahead of the input cone of the cone/friction ring transmission, while simultaneously increasing the speed of rotation, to such an extent that significantly greater power can be transferred by the cone/friction ring transmission.
  • the torque of the input cone can be converted to approximately half the torque of the input shaft, making use of the advantages already explained above.
  • the cone/friction ring transmission is characterized in that the regulation device has at least a first subsidiary regulation device having a first reference variable and a second subsidiary regulation device having a second reference variable, separate from the first reference variable, whereby the position of the friction ring of the first subsidiary transmission is regulated by way of the first subsidiary regulation device, and the position of the friction ring of the second subsidiary transmission is regulated by way of the second subsidiary regulation device.
  • a cone/friction ring transmission regulated according to this method can be regulated, in its overall translation, in accordance with the state of the art, by way of a transmission control device that contains the first subsidiary regulation device, whereby the first subsidiary regulation device receives its reference variable by way of the transmission control device itself or by way of an engine control device that is present.
  • the control variable output by the first subsidiary regulation device is used for regulation of the axial position of a friction ring at least of the first subsidiary transmission, but also for regulation of a friction ring of every further subsidiary transmission that is present, particularly for regulation of the friction ring of the second subsidiary transmission.
  • a regulation variable detected at the first subsidiary transmission can be passed back to the second subsidiary regulation device, and as a result, the second subsidiary regulation device in turn outputs a second control variable for an adjustment device of a friction ring of the second subsidiary transmission.
  • Any desired speed of rotation for example the speed of rotation of the friction ring, the speed of rotation of a friction cone situated in the subsidiary transmission, a slip that occurs on the friction ring, or also a torque transferred by the subsidiary transmission, can be used as a regulation variable of the first regulation segment, in other words of the first subsidiary transmission.
  • the control variable output by the second subsidiary regulation device can then be used, together with the control variable output by the first subsidiary regulation device, to regulate the axial position of the friction ring of the second subsidiary transmission.
  • superimposition preferably takes place in such a manner that the axial position of the friction ring of the second subsidiary regulation device is set by the first control variable, so that it corresponds or is equivalent to the axial position of the friction ring of the first subsidiary transmission, and that the second control variable, which is superimposed on the first control variable, only slightly readjusts the friction ring of the second subsidiary transmission, in terms of its position, in such a manner that because of this slight relative change in position of the friction ring of the second subsidiary transmission, the regulation variables of the first subsidiary transmission and of the second subsidiary transmission reach the same value, in other words the regulation deviation of the second regulation variable from the first regulation variable, which is used as the second reference variable, approaches zero.
  • the position of the friction ring of the second subsidiary transmission can be regulated not just slightly by means of the control variable of the second subsidiary regulation device, but rather also in such a manner that it is possible to do without the first subsidiary regulation device for positioning of the friction ring of the second subsidiary transmission, and regulation of its position then takes place only by way of the second subsidiary regulation device.
  • a cone/friction ring transmission operated according to this method presumes that the position offset characteristic field that is used is either already present or is recorded during operation of the cone/friction ring transmission.
  • a testing and running-in program for determining the position offset characteristic field can advantageously be used, carried out on a test bench after assembly.
  • the production tolerances and inaccuracies are recorded, for example by means of measurement instruments present on the test bench, and permanently stored in the control device of the cone/friction ring transmission, thereby making it possible to do without additional sensors for determining the regulation variables required for regulation.
  • the position offset characteristic field consists, in this test bench calibration, for example of a position of the friction ring of the first subsidiary transmission predetermined by the first regulation device, and a position deviation of the friction ring of the second subsidiary transmission that correlates to it.
  • a corresponding correction variable for the first control variable is determined from this position deviation, and the corrected signal is output by the second subsidiary regulation device as a second control variable.
  • generation of a data set for a position offset characteristic field is not limited to a test bench run before initial startup of the cone/friction ring transmission, because a calibration process is possible also during operation, by means of a transmission control device present in the vehicle and a suitable sensor system on the cone/friction ring transmission.
  • a learning function can be implanted in a control device, according to this method, for example, by means of which function the position offset characteristic field is constantly adapted to the current wear state of the cone/friction ring transmission.
  • a cone/friction ring transmission consisting of a first subsidiary transmission structured as a cone/friction ring transmission and a second subsidiary transmission structured as a cone/friction ring transmission
  • the two subsidiary transmissions have a common cone and the first subsidiary transmission has a first further cone and the second subsidiary transmission has a second further cone, whereby the axes of rotation of the common cone as well as of the two further cones are disposed in an axis plane, whereby at least the common cone has a shaft-side friction cone bearing as well as a shoulder-side friction cone bearing, and whereby the cone/friction ring transmission is characterized in that the shaft-side friction cone bearing and/or the shoulder-side friction cone bearing has a degree of freedom of translation along the axis plane.
  • the torque transferred by the two subsidiary transmissions can be distributed to the two subsidiary transmissions in particularly uniform manner, by means of the configuration described above, in particularly advantageous manner.
  • the friction forces and press-down forces that occur at the friction contacts of the two subsidiary transmissions are uniformly distributed to two subsidiary transmissions by means of this configuration.
  • the configuration of any desired friction cone bearing or both friction cone bearings with a degree of freedom of translation along the axis plane is advantageous also in the case of a cone/friction ring transmission having two press-down units, whereby the press-down units are provided in the two further cones.
  • the arrangement explained above is advantageous if only one press-down unit is provided in the further cones.
  • roller bearings in particular, but also slide bearings, if necessary, can be used as friction cone bearings.
  • four-point bearings, other ball bearings are suitable as roller bearings, or, in the case of certain bearings, also conical roller bearings; likewise, needle bearings can be used.
  • an individual cone For transferring the torque transferred by the cone/friction ring transmission, an individual cone has an input shaft connected with this cone, or an output shaft.
  • the term “shaft-side” therefore characterizes that end of the axial expanse of a cone that faces such an input or output shaft. Accordingly, the term “shoulder-side” refers to the side of the cone that faces away from the corresponding shaft. If a second output shaft or a second input shaft is provided on a cone, for a possible secondary drive, the reference point for the terms “shaft-side” and “shoulder-side” is always the shaft that transfers the main drive torque.
  • the term “axial” always refers to the axis of rotation or symmetry of a cone.
  • degree of freedom of translation refers to the movement directions of a point or of a body in the coordinate system, independent of one another, in each instance.
  • the present invention here is based on the Cartesian coordinate system and thus on six degrees of freedom, three degrees of freedom of translation and three degrees of freedom of rotation.
  • a degree of freedom of translation that runs along the axis plane and essentially radial to the axis of rotation of the common cone therefore describes a movement direction of two axes of rotation, which are moving toward one another or away from one another, or of two points on two axes of rotation, which are moving toward one another or away from one another.
  • the term “essentially” expresses that the movement of a friction cone bearing along the axis plane and radial to the axes of rotation does not have to involve only a translational movement of a corresponding bearing in the direction of a further axis of rotation, whereby the axis of rotation of the moving cone moves parallel to the remaining axis of rotation, but rather can also involve movement of the cone axis or bearing axis of rotation about a rotational point on the axis of rotation. Therefore it is true that a point on the moving axis of rotation would always move perpendicular to this axis of rotation, but this movement would not be perpendicular or radial to the axis of rotation toward which the bearing in question is moving.
  • a shaft of the common cone can have at least one movable, torsionally rigid coupling.
  • a “movable, torsionally rigid coupling” can be structured, for example, as a universal joint, as a constant velocity ball joint, as a curved-tooth coupling, or as a multiple disk clutch. Essentially, the coupling must balance out an angle and/or an offset of the common cone.
  • a rotational movement of the common cone results if only one of the two bearings performs a translational movement in the axis plane.
  • the term “essentially” becomes clear once again, because a friction cone bearing will move on a circular path if the common cone is immovably clamped on a further friction cone bearing.
  • the angle range represented in such a case is so small that movement on a straight line can be approximated.
  • the shaft-side friction cone bearing and the shoulder-side friction cone bearing are structured as floating bearings. In this way, tensions on the basis of movement, but also tensions caused by thermal expansion processes in the common cone or in the shaft can be balanced out.
  • it is also advantageous, alternatively to a floating bearing structured on the shaft side and shoulder side if one of the shaft-side or shoulder-side friction cone bearings is structured as a floating bearing, and the further shaft-side or shoulder-side friction cone bearing is structured as a fixed bearing.
  • the fixed bearing is an angle-movable bearing.
  • An “angle-movable bearing” can particularly be a spherical roller bearing or a self-aligning bearing, which is able to balance out an angle offset of the shaft.
  • the shaft-side and/or the shoulder-side friction cone bearing have a bearing guide.
  • This can be advantageously implemented, in particular, if the bearing is merely used for mounting a rotating axle, and is firmly clamped in the stated bearing guide, and the bearing guide is therefore responsible for translational movement in the axis plane.
  • the various bearing tasks are also distributed among different modules.
  • a cone/friction ring transmission particularly in connection with a common cone that can move in the axis plane, if at least one friction ring of the cone/friction ring transmission has a contact surface that faces the common cone, whereby the contact surface is configured to be convex relative to a surface of the common cone, at least at a sectional plane that lies in the axis plane.
  • This crowned configuration of a friction ring surface furthermore promotes the slanted position or an angle offset of the axis of rotation of the common cone, in that the same contact geometry between friction ring and common cone is always guaranteed.
  • the friction ring were to have a level contact surface relative to the common cone, thereby causing a contact line to form at this friction contact instead of a contact point, and furthermore also at the other friction contacts, the surface of the common cone would no longer run parallel to the friction ring surface in the event of an angle offset of the common cone, thereby causing overly strong edge pressures on this friction ring.
  • a surface of the friction ring configured in crowned manner counters this edge pressure and always allows a uniformly structured contact point between the friction ring and the common cone.
  • FIG. 1 a cone/friction ring transmission having a first subsidiary transmission and a second subsidiary transmission, as well as a first gear-wheel transmission and a second gear-wheel transmission, which connects the further cones of the first subsidiary transmission and of the second subsidiary transmission so as to interact with a common shaft, with synchronous speeds of rotation;
  • FIG. 2 a cone/friction ring transmission having a first subsidiary transmission, having a second subsidiary transmission, and having a first power-split equalization transmission, which connects the further cones of the first subsidiary transmission and of the second subsidiary transmission so as to interact with a common shaft;
  • FIG. 3 a further cone/friction ring transmission having a first subsidiary transmission, having a second subsidiary transmission, and having a second power-split equalization transmission, which connects the further cones of the first subsidiary transmission and of the second subsidiary transmission so as to interact with a common shaft;
  • FIG. 4 a further cone/friction ring transmission having a first subsidiary transmission, having a second subsidiary transmission, and having a third power-split equalization transmission, which connects the further cones of the first subsidiary transmission and of the second subsidiary transmission so as to interact with a common shaft;
  • FIG. 5 a cone/friction ring transmission having a first subsidiary transmission, having a second subsidiary transmission, having a first press-down unit for a further cone of the first subsidiary transmission, having a second press-down unit for a further cone of the second subsidiary transmission, and having hydraulic force equalization between the first press-down unit as well as the second press-down unit;
  • FIG. 6 a cone/friction ring transmission having a first subsidiary transmission, having a second subsidiary transmission, having a first press-down unit for a further cone of the first subsidiary transmission, having a second press-down unit for a further cone of the second subsidiary transmission, and having mechanical force equalization between the first press-down unit as well as the second press-down unit;
  • FIG. 7 a cone/friction ring transmission having a first subsidiary transmission, having a second subsidiary transmission, and having a common press-down unit situated on a common cone;
  • FIG. 8 a cone/friction ring transmission having a first subsidiary transmission, having a second subsidiary transmission, and having a common cone that is freely movable in an axis plane, which cone has two movable and torsionally rigid couplings on its shaft;
  • FIG. 9 the arrangement of the bearings and shafts shown in
  • FIG. 8 in a top view
  • FIG. 10 a cone/friction ring transmission having a first subsidiary transmission, having a second subsidiary transmission, having mechanical coupling between the two transmissions, in a first perspective view, at a low translation ratio;
  • FIG. 11 the cone/friction ring transmission according to FIG. 10 in another perspective view
  • FIG. 12 the cone/friction ring transmission according to FIGS. 10 and 11 in a perspective view similar to FIG. 10 , at a high translation ratio;
  • FIG. 13 the cone/friction ring transmission according to FIGS. 10 to 12 in a perspective view similar to FIG. 11 , at a high translation ratio;
  • FIG. 14 the cone/friction ring transmission according to FIGS. 10 to 13 in a top view, at a high translation ratio
  • FIG. 15 a schematic top view of another cone/friction ring transmission.
  • FIG. 1 shows the cone/friction ring transmission 1 having a first subsidiary transmission 11 and a second subsidiary transmission 21 , as well as a first gear-wheel transmission 13 and a second gear-wheel transmission 23 , which connects the further cone of the first subsidiary transmission 12 and the further cone of the second subsidiary transmission 22 with a common shaft, with synchronous speeds of rotation.
  • the introduction of force into the cone/friction ring transmission 1 takes place, in this embodiment, by way of an input shaft of a common cone 2 of the two subsidiary transmissions 11 , 12 .
  • the further cones 12 , 22 pass the shaft power passed on by the common cone 2 to friction rings 14 , 24 on to an output shaft, the common shaft 3 .
  • the friction rings 14 , 24 are axially adjusted by way of adjustment devices 15 , 25 having servomotors 16 , 26 , which are controlled by way of a reference variable 18 .
  • the output shafts of the further cones 12 , 22 are connected with a common spur gear that sits on the common shaft 3 , in order to pass the shaft power on by way of two spur gears, in each instance.
  • the power transfer from the common cone 2 to the common shaft 3 is structured in such a manner, because of these two spur gears, that the further cones 12 , 22 of the two subsidiary transmissions 11 , 21 are always driven at a synchronous speed of rotation, and a difference in the speed of rotation between the further cones 12 , 22 , caused by a deviation between the axial position of the friction ring 14 of the first subsidiary transmission and the axial position of the friction ring 24 of the second subsidiary transmission cannot be balanced out.
  • a position deviation between the friction rings 14 , 24 therefore also necessarily leads to a difference in the speed of rotation between the friction ring of the first subsidiary transmission 14 and the friction ring of the second subsidiary transmission 24 , although this difference in the speed of rotation can also achieve a very small value or, in an idealized, theoretical cone/friction ring transmission, is not present at all.
  • a friction ring operated at a different speed of rotation is subject, as a result, to greater slip at a friction pairing present at this friction ring, such as the friction surface between the surface that lies radially outside of the friction ring and the surface of the common cone 2 , or the surface that lies radially within the friction ring and a surface of the further cone connected with the common cone, so as to interact with it, by means of the friction ring.
  • the second servomotor 26 of the second subsidiary transmission 21 uses not only the first reference variable 18 , which is used to generate a common control variable 19 for regulation of the two adjustment devices 15 , 25 , but also a second reference variable 28 , which in turn is formed from the regulation variable of the first subsidiary transmission 11 , here the difference in the speeds of rotation of the friction ring of the first subsidiary transmission 14 and of the friction ring of the second subsidiary transmission 24 , whereby here, for example, the absolute position of the first friction ring 14 or the like can also be used, for example.
  • the adjustment devices of the friction rings 15 , 25 furthermore include two small guide wheels 5 , in each instance, which engage around the friction rings 14 , 24 without play, so that on the one hand, axial adjustment of the friction rings 14 , 24 can take place without delay, and, on the other hand, the axial position of the friction rings 14 , 24 in a stationary state, in other words at a translation ratio that remains the same, can be kept as stable as possible, so that the friction rings are not additionally subject to fluttering or axial migration between the cones 2 , 12 , 22 .
  • Measurement of the difference in the speed of rotation between the friction rings 14 , 24 takes place by way of measurement devices 20 , 30 situated on the adjustment devices of the friction rings 15 , 25 , whereby these measurement devices 20 , 30 consist, in this exemplary embodiment, of optical or inductive sensors, not shown, which recognizes the friction ring speed of rotation by means of notches or recesses on the friction rings.
  • the common control variable 19 of a first subsidiary regulation device 17 used for the servomotors 16 , 26 of the two adjustment devices 15 , 25 is superimposed on the second reference variable 29 of the second subsidiary regulation device 27 , for regulation of the axial position of the friction ring of the second subsidiary transmission 21 .
  • the first subsidiary regulation device 17 therefore presets the axial position for the friction ring of the second subsidiary transmission 24 , as well, whereby it is made possible that the friction ring of the second subsidiary transmission 24 can follow the position of the friction ring of the first subsidiary transmission 14 almost without delay, at high adjustment speeds.
  • Equalization of a relative axial malpositioning of the friction ring of the second subsidiary transmission 24 therefore takes place solely by way of the second subsidiary regulation device 27 , so that in this exemplary embodiment, the second subsidiary regulation device 27 is used only for relative positioning, in other words relative to the current position of the friction ring of the second subsidiary transmission 24 itself, and the first subsidiary regulation device 17 is used only for absolute positioning, in other words with reference to a coordinate system fixed on the cone, of the friction ring of the second subsidiary transmission 21 .
  • the cone/friction ring transmission 1 shown in FIG. 2 having a first subsidiary transmission 11 and a second subsidiary transmission 21 , whereby the first subsidiary transmission 11 has a common cone 2 and a further cone 12 , and the second subsidiary transmission 21 has the common cone 2 and a further cone 22 , transfers a torque issued by way of the common shaft 3 , by means of a first power-split equalization transmission 31 .
  • the power-split equalization transmission 31 consists of a differential transmission (not numbered), whereby the coaxial bevel gears are connected with the output shafts of the further cones 12 , 22 of the two subsidiary transmissions 11 , 21 by way of further switchable bevel gears, and whereby a differential case of the differential transmission is connected to interact with the common shaft 3 .
  • the switchable further bevel gears situated at the output shafts of the further cones 12 , 22 allow the representation of a reverse gear, by means of the clutch sleeve, which is not numbered.
  • An equalization transmission 31 configured in this manner is therefore able to permit differences in speed of rotation between the friction rings 14 , 24 , in that no synchronous speed of rotation between the first subsidiary transmission 11 and the second subsidiary transmission 21 has to be forced to occur. Consequently, a minimum of slip always comes about at the friction rings 14 , 24 , thereby causing only the further cones 12 , 22 to demonstrate a speed of rotation difference between one another.
  • the power-split transmission 31 is able to balance out these speed of rotation differences, and therefore, in turn, relative movements in the differential transmission of the power-split equalization transmission 31 occur instead of increased slip at the friction rings 14 , 24 , and these relative movements, which balance out the speed of rotation, lead to a reduction in the degree of effectiveness of the transmission, due to friction heat. Regulation of the axial position of the friction rings 14 , 24 according to the invention consequently brings about an increase in the degree of effectiveness of the transmission, because of avoidance of these relative movements as explained.
  • the reference variable 28 in turn consists of a regulation variable of the first subsidiary transmission 11 made available by the first regulation variable detection 20 and a regulation variable of the second subsidiary transmission 21 made available by the second regulation variable detection 30 .
  • the reference variable 28 evaluated by the subsidiary regulation device is formed by the difference in the speed of rotation of the friction rings 14 , 24 , whereby here, too, an axial position of the first friction ring 14 , for example, can be used, possibly with the inclusion of a position offset characteristic field, to take a calibration measurement into consideration.
  • a speed of rotation measurement of the friction rings at the small guide wheels 5 of the adjustment devices 15 , 25 is provided, in that the speed of rotation of the small guide wheels 5 themselves is detected. It is immediately evident that slip can occur between a small guide wheel 5 and a friction ring, as well, and therefore the measurement of the speed of rotation of the friction ring can be subject to error for this reason, but this is actually very unlikely or can be the case only to an extremely slight degree, because no torque is transferred at this location and the small guide wheels 5 lie very precisely against the friction ring, for secure guidance of the latter, in any case.
  • a correction variable can be superimposed on this measurement variable determined on the small guide wheel, depending on the requirements, depending on the operating state of the cone/friction ring transmission 1 , such as stationary operation or an adjustment of the translation ratio in a specific direction. Furthermore, a measurement at the power-split equalization transmission 31 used in this embodiment is also possible, whereby the relative speed of rotation of two transmission elements can be measured, for example, at which the relative speed of rotation or difference in speed of rotation amounts to just zero—as explained further above—during slip-free operation.
  • the cone/friction ring transmission shown in FIG. 3 having a first subsidiary transmission 11 and a second subsidiary transmission 21 , has a second power-split equalization transmission 32 , whereby this second power-split equalization transmission 32 represents a simplified embodiment of the first power-split equalization transmission 31 according to the exemplary embodiment from FIG. 2 .
  • this second power-split equalization transmission 32 represents a simplified embodiment of the first power-split equalization transmission 31 according to the exemplary embodiment from FIG. 2 .
  • multiple subsidiary transmissions and a direct gear connecting the common cone 2 with the common shaft 3 , so as to interact, were eliminated, thereby resulting in a further possibility for increasing the degree of effectiveness of the transmission, by reducing friction losses.
  • Regulation of the axial position of the friction rings 14 , 24 shown in this exemplary embodiment once again uses two superimposed control variables 19 , 29 of the two subsidiary regulation devices 17 , 27 for regulation of the axial position of the friction ring of the second subsidiary transmission 24 .
  • the second subsidiary regulation device 27 uses the speed of rotation difference of the further cones 12 , 22 of the two subsidiary transmissions 11 , 21 as the reference variable, at this point, instead of the speed of rotation difference of the friction rings 14 , 24 , for relative positioning of the friction ring of the second subsidiary transmission 24 .
  • Use of the second equalization transmission 32 which is subject to losses in the degree of effectiveness, preferably allows the use, in this embodiment, of the speed of rotation difference of the further cones 12 , 22 for generating a second control variable 19 by means of the reference variable 28 that is made available, so that making the reference variable 28 available can take place by means of simple regulation variable detection 20 , 30 fixed in place on the housing.
  • FIG. 4 shows a further exemplary embodiment of a cone/friction ring transmission 1 , whereby a third power-split equalization transmission 33 is used, which is structured as a planetary gear and also is able to balance out differences in speed of rotation and torque between the first subsidiary transmission 11 and the second subsidiary transmission 21 , and clearly reduces the construction space of the cone/friction ring transmission 1 in the axial direction, as compared with the exemplary embodiments having the first and second power-split equalization transmissions 31 , 32 shown in FIGS. 2 and 3 .
  • the subsidiary regulation device 27 shown in this exemplary embodiment uses a second reference variable 28 , which is generated from three speed of rotation signals, the speeds of rotation of the friction rings 14 , 24 and the speed of rotation of the common cone 2 , to make available the second control variable 29 .
  • a second reference variable 28 is generated from three speed of rotation signals, the speeds of rotation of the friction rings 14 , 24 and the speed of rotation of the common cone 2 , to make available the second control variable 29 .
  • Use of the speed of rotation signal of the common cone 2 made available by way of the speed of rotation sensor 4 makes it possible to draw conclusions concerning the slip that occurs in the friction rings 14 , 24 , by way of mathematical, physical and/or tribological models, so that instead of a speed of rotation signal, this determined slip can also be used as a reference variable 28 for regulation of the axial position of the friction ring of the second subsidiary transmission.
  • an equalization transmission such as the third power-split equalization transmission 33 used here, does effectively prevent the occurrence of different slip at the friction rings 14 , 24 , for which reason use of this regulation on further friction cones 12 , 22 that are coupled in torsionally rigid manner is preferably preferred, but the present regulation strategy allows the use of a differential block in the power-split equalization transmissions 31 , 32 , 33 , for example, which block prevents relative movements in the gear set of the equalization transmissions 31 , 32 , 33 .
  • FIG. 5 a cone/friction ring transmission 1 according to the invention is shown, with a further cone 12 of the first subsidiary transmission 11 , on which a first press-down unit 42 acts, and a further cone 22 of the second subsidiary transmission 21 , on which a second press-down unit 43 acts.
  • a regulation device for axial positioning of the friction rings 14 , 24 , in this embodiment, requires essentially identical tribological conditions in the friction contacts between the friction rings 14 , 24 and the cones 2 , 12 , 22 connected to interact by means of these friction rings 14 , 24 , particularly if the second subsidiary regulation device 27 regulates the axial position of the friction ring of the second subsidiary transmission 24 by way of measuring the speed of rotation of the friction rings 14 , 24 , or by way of measuring the slip that is present at the friction rings.
  • the hydraulic equalization 44 connects an oil-filled first pressure chamber 45 of the first press-down unit 42 with an also oil-filled second pressure chamber 46 of the second press-down unit 43 .
  • the oil contained in the press-down units 42 , 43 can therefore flow back and forth between the pressure chambers 45 , 46 , so that the press-down forces on the further cones 12 , 22 of the two subsidiary transmissions 11 , 12 always assume the same value, and in this way, the tribological conditions at the friction contacts of the friction rings 14 , 24 achieve the same state.
  • the further cones 12 , 22 are mounted, on both sides, by means of radial bearings, and therefore are freely movable in the axial direction. All the axial forces, as well as the equalization forces of the press-down units 42 , 43 , are supported by a conical roller bearing situated on the common cone 2 . Additional axial bearings between the press-down units 42 , 43 and the further cones 12 , 22 uncouple the rotational movement of the further cones 12 , 22 from the press-down units 42 , 43 .
  • FIG. 5 furthermore shows an alternative regulation strategy for the second subsidiary regulation device.
  • the difference of the torques applied at the further cones 12 , 22 measured by way of the regulation variable detection 20 , 30 is used as the reference variable 28 ; this difference results from axial incorrect positioning of the friction rings 14 , 24 , because a reduction in the transferred power takes place by means of an increase in the slip in one of the friction rings 14 , 24 .
  • the embodiment shown in FIG. 6 comprises a correspondingly acting equalization of force between the first press-down unit 42 and the second press-down unit 43 .
  • different press-down forces acting on the further cones 12 , 22 are equalized by way of mechanical equalization 47 .
  • the mechanical equalization 47 acts by way of a lever situated between the first subsidiary transmission 11 and the second subsidiary transmission 21 , which is mounted so as to rotate in its pivot point 48 , situated on its axis of symmetry, on the housing of the cone/friction ring transmission 1 , so that the levers that act on the press-down units 42 , 43 have the same active length and the press-down forces that act on the further cones 12 , 22 always have the same value.
  • the cone/friction ring transmission 1 furthermore has a torque converter structured as a spur gear transmission having a first gear-wheel transmission 13 and a second gear-wheel transmission 23 , in order to reduce a torque of the common shaft 3 before this torque is introduced into the further cone 12 of the first subsidiary transmission 11 and into the further cone 22 of the second subsidiary transmission 21 .
  • the speed of rotation of the two further cones is increased in proportion to the reduction in torque, as is usual in the case of transmissions having a fixed transmission translation.
  • the cone/friction ring transmission 1 In contrast to an embodiment of a cone/friction ring transmission 1 having only one input cone and one output cone, the cone/friction ring transmission 1 according to the embodiment shown in FIG. 5 is now suitable for transferring four times the torque originally introduced.
  • the first doubling of the transferred torque follows from the use of two input cones 12 , 22 , and, accompanying these, two subsidiary transmissions 11 , 21 , and the friction contacts therefore present twice between the input cones 12 , 22 and the common output cone 2 .
  • cone-side gear wheels of the two gear-wheel transmissions in each instance, have about half the diameter of a shaft-side gear wheel, disposed on the common shaft 3 .
  • the numbers of teeth of two gear wheels situated in engagement within a gear-wheel transmission do not correspond to precisely twice or half the number of teeth of the other gear wheel, in each instance.
  • the number of teeth of one of the two gear wheels within a gear-wheel transmission 13 , 23 is reduced or increased by one tooth. This embodiment brings about constantly different pairings of two teeth during engagement.
  • FIG. 7 shows a device for applying a press-down force between the friction rings 14 , 24 and the cones 2 , 12 , 22 , which can be used preferably supplementally but also alternatively to the press-down force equalizations according to FIGS. 5 and 6 .
  • a common press-down unit 41 is used on the common cone 2 , so that the press-down force required for the transfer of force between the cones 12 , 22 , in each instance, and the common cone 2 is applied by means of this single common press-down unit 41 and not by means of the use of two separate press-down units.
  • the arrangement shown, with a common press-down unit 41 makes it possible to simplify the assembly of the cone/friction ring transmission 1 by means of the elimination of assembly-intensive modules.
  • the press-down unit 41 itself, in terms of design, in such a manner that no further components are required for force equalization between the further cones 12 , 22 of the two subsidiary transmissions 11 , 21 , because the press-down unit 41 already acts uniformly on both further cones 12 , 22 , without any further aids.
  • the press-down unit 41 applies a press-down force required for transfer of force, at least by way of two plate springs, not numbered, of a first subsidiary press-down device, whereby the press-down force is constant, at first, in the entire operating range of the cone/friction ring transmission 1 .
  • the second subsidiary press-down unit shown can generate a torque-dependent press-down force by means of a roller body and a run-up ramp on which the roller body, also not numbered, rolls. Therefore the press-down unit 41 shown can advantageously be used in the case of greatly varying input torques.
  • a torque can be measured, if necessary directly, by way of the press-down unit 41 , and used for the regulation procedures described above, in that the displacement of the different modules of the press-down unit 41 is used to generate a corresponding measurement signal.
  • the cone/friction ring transmission 1 has a shaft coupling 56 consisting of two universal joints, which follows displacement of the axis of rotation 61 of the common cone 2 and also makes these possible.
  • the shaft 51 of the common cone 2 is connected with the shaft coupling 56 , whereby this shaft 51 is mounted in the cone/friction ring transmission 1 by means of a shaft-side friction cone bearing 52 .
  • a shoulder-side friction cone bearing 54 is provided, which mounts the common cone 2 in a housing of the cone/friction ring transmission 1 , at a shoulder 53 .
  • each of the two further cones 12 , 22 has a shaft 51 and a shoulder 53 , which are furthermore used for mounting, by means of the shaft-side friction cone bearing 52 and the shoulder-side friction cone bearing 54 .
  • the two further cones 12 , 22 are enclosed by their friction ring 14 , 24 , in each instance, and transfer a torque to the common cone 2 by means of this friction ring 14 , 24 .
  • the guide bearing 55 is structured as a conical roller bearing, and supports the axial forces on a shoulder situated on the shaft 51 .
  • the two further cones 12 , 22 of the two subsidiary transmissions 11 , 21 have a fixed/floating mounting usual in the state of the art, with a conical roller bearing as the shoulder-side friction cone bearing 54 , and a cylindrical roller bearing as the shaft-side friction cone bearing 52 .
  • the exemplary embodiment according to FIG. 8 allows translational offset, particularly by means of the two floating bearings of the common cone 2 , by means of its shaft-side friction cone bearing 52 and its shoulder-side friction cone bearing 54 , and also rotational offset of the common cone 2 , in that the two friction cone bearings 52 , 54 of the cone 2 have a degree of freedom, in each instance, in the direction of the axes of rotation 52 , 53 of the first further cone 12 and of the second further cone 22 .
  • Such an exemplary embodiment allows mounting of the common cone 2 similar to the method known in the state of the art, whereby the translational freedom of movement of the other friction cone bearing, in each instance, of the floating bearing, is maintained by means of the angular mobility of the fixed bearing.
  • an exemplary embodiment having a rotationally movable bearing as a friction cone bearing makes available a common cone having only one degree of freedom, a rotational degree of freedom.
  • a ring contact surface 58 of a friction ring 14 , 24 of the first or of the second subsidiary transmission 11 , 21 is equipped with a surface structured, at least in cross-section, as a straight line. This brings about linear contact between the ring contact surface 58 and the cone surface 57 , as is immediately evident.
  • the common cone 2 has only one degree of freedom of rotation instead of one degree of freedom of rotation and an additional degree of freedom of translation.
  • this restriction of the degrees of freedom of the common cone 2 leads to the result that the cone surface 57 can no longer be guided parallel to the surfaces of the further cones 12 , 22 . Consequently, it is problematical, in a certain sense, to also no longer structure the ring contact surface 58 of the two friction rings 14 , 24 to be level, at least level in a cross-section.
  • a ring contact surface that is structured to be crowned in other words a contact surface that has a convex curvature at least in the axis plane, can balance out the angle offset of the common cone 2 .
  • impermissibly high edge pressure at one of the two friction rings 14 , 24 does not occur.
  • a cone/friction ring transmission structured according to FIG. 8 having a movable common cone 2
  • a movable common cone 2 is able to balance out non-uniform contact forces at the two friction rings 14 , 24 , by means of a press-down device applied in this common cone 2 .
  • the shoulder-side friction cone bearing 54 of the common cone 2 is disposed in a horizontally structured cone guide 64 according to FIG. 9 .
  • This guide 64 allows migration of the friction cone bearing, in this case of the shoulder-side friction cone bearing 54 , along an axis plane 60 , which is spanned by the axes of rotation 62 , 63 of the two further cones 12 , 22 and by the axis of rotation 61 of the common cone 2 .
  • the term “horizontal” refers, in this case, to a direction within the axis plane, whereby “vertical” would mean a movement direction perpendicular to the axis plane 60 .
  • the bearing guide 64 is structured as an oblong hole having an orientation relative to the axis plane 60 .
  • the bearing guide 64 has an accommodation or socket for an outer ring of the shoulder-side friction cone bearing 54 and therefore the bearing guide 64 itself is disposed within a housing 59 of the cone/ring transmission 1 , as a carriage.
  • the use of a separate component as a carriage for a bearing guide 64 furthermore allows better clamping of the friction cone bearing used, in each instance, and uncoupling of the translational guidance of the common cone 2 within the axis plane 60 and the rotational mounting of the common cone 2 by means of the friction cone bearing, in each instance.
  • two friction cone bearings of the two further cones 12 , 22 have a friction cone bearing guide 64 , whereby in such an exemplary embodiment, these bearing guides 64 can also be equipped with press-down devices, in order to brace the two further cones 12 , 22 in the direction of the common cone 2 , by means of a force.
  • control or regulation of the second subsidiary transmission 21 can also take place mechanically, as is explained as an example, using the exemplary embodiment shown in FIGS. 10 to 15 .
  • control or regulation of the first subsidiary transmission 11 preferably takes place in known manner, so that here, known devices can be used, in particular.
  • the servomotor 16 by way of a transmission arrangement 71 , can displace a case 72 at a work angle, which case in turn displaces the friction ring 14 in terms of its work angle, by way of an adjustment bridge 73 , which is mounted in axially displaceable manner on this case and a rotation prevention device 74 , so that this friction ring migrates accordingly, on its own and due to the rotation of the cones 2 , 12 .
  • the case 72 can also be structured as a two-axle case or otherwise, as long as it accordingly guides the adjustment bridge axially and allows an angle adjustment.
  • the rotation prevention device 72 can also be implemented by means of a second guide rod or in the first guide rod of the case 72 . Also, it is not absolutely necessary to configure the adjustment bridge 73 in the manner of a bridge, as long as it guarantees sufficiently stable guidance and angle adjustment.
  • the position of the adjustment bridge 73 is transferred to the second adjustment device 25 by means of a transfer rod 76 , by way of a mechanical position sensor 75 , which can also be used for recording measurement values, if necessary, by way of a potentiometer.
  • the second adjustment device 25 also has a case 77 that mounts an adjustment bridge 78 in axially displaceable manner, by means of a rotation prevention device 79 , in known manner, and allows angle adjustment of the friction ring 24 mounted by the adjustment bridge 78 and allows the adjustment bridge 78 to freely follow axial migration of the friction ring 24 .
  • the case 77 is controlled by way of a feedback linkage 81 , which encloses the position sensor 80 , on the one hand, and the control rod 82 , on the other hand, and is oriented in such a manner that an axial position of the friction ring 24 can be preset by way of the control rod 82 , which position is then approached, under the control of the position sensor 80 , by means of mechanical feedback of the feedback linkage 81 .
  • the transfer rod 76 is coupled with the control rod 82 , so that the mechanically determined position of the adjustment bridge 73 and therefore of the friction ring 14 serves as a reference variable of the second adjustment device 25 .
  • modules of the exemplary embodiment shown in FIGS. 10 to 14 that act in identical manner are also identically numbered, so that in order to avoid repetitions, they will not be described again here, and reference is made to the above explanations.
  • the adjustment devices 15 , 25 do not necessarily have to be provided on the side of the cones 12 , 22 that faces away from the cone 2 , in each instance. Instead, it is possible to provide the adjustment devices 15 , 25 above or below the cones 2 , 12 , 22 , which are essentially disposed in one plane, as is shown as an example in FIG. 15 . In this way, mechanical coupling can be significantly simplified, if applicable.
  • mechanical coupling of the two adjustment devices 15 , 25 is accordingly also provided, whereby the adjustment bridge 73 of the adjustment device 15 is regulated in known manner, while the adjustment bridge 78 of the adjustment device 25 is configured as a following adjustment device, in that a case of the adjustment device 25 , not shown, allows axial displacement of the adjustment bridge 78 in the manner already described above, but in deviation from the exemplary embodiment described above, does not preset an angular position but rather can freely follow an angular position preset by the adjustment bridge 78 .
  • the adjustment bridge 78 is tilted if it has an axial position that deviates from the axial position of the adjustment bridge 73 .
  • the case of the adjustment device 25 follows this tilting accordingly, as has been described above, so that the friction ring can migrate in accordance with the angular position, until the angle has been regulated back to zero. Therefore if the adjustment bridge 73 is displaced, the adjustment bridge 78 or the corresponding friction ring follows this displacement.
  • the rotational/sliding connection 85 is formed by a groove in the adjustment bridge 78 , into which a round tongue of the adjustment bridge 73 engages.
  • a rotational/sliding connection is formed by a groove in the adjustment bridge 78 , into which a round tongue of the adjustment bridge 73 engages.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Friction Gearing (AREA)
US13/817,010 2010-08-16 2011-08-16 Cone/friction ring transmission and method for a cone/friction ring transmission Abandoned US20130143713A1 (en)

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
DE102010034502 2010-08-16
DE102010034502.4 2010-08-16
DE102011008863.6 2011-01-18
DE102011008863A DE102011008863A1 (de) 2010-08-16 2011-01-18 Kegelreibringgetriebe und Verfahren für ein Kegelreibringgetriebe
PCT/DE2011/001597 WO2012022303A2 (de) 2010-08-16 2011-08-16 Kegelreibringgetriebe und verfahren für ein kegelreibringgetriebe

Related Parent Applications (1)

Application Number Title Priority Date Filing Date
PCT/DE2011/001597 A-371-Of-International WO2012022303A2 (de) 2010-08-16 2011-08-16 Kegelreibringgetriebe und verfahren für ein kegelreibringgetriebe

Related Child Applications (1)

Application Number Title Priority Date Filing Date
US15/213,616 Division US10267392B2 (en) 2010-08-16 2016-07-19 Cone/friction ring transmission and method for a cone/friction ring transmission

Publications (1)

Publication Number Publication Date
US20130143713A1 true US20130143713A1 (en) 2013-06-06

Family

ID=45528516

Family Applications (2)

Application Number Title Priority Date Filing Date
US13/817,010 Abandoned US20130143713A1 (en) 2010-08-16 2011-08-16 Cone/friction ring transmission and method for a cone/friction ring transmission
US15/213,616 Expired - Fee Related US10267392B2 (en) 2010-08-16 2016-07-19 Cone/friction ring transmission and method for a cone/friction ring transmission

Family Applications After (1)

Application Number Title Priority Date Filing Date
US15/213,616 Expired - Fee Related US10267392B2 (en) 2010-08-16 2016-07-19 Cone/friction ring transmission and method for a cone/friction ring transmission

Country Status (8)

Country Link
US (2) US20130143713A1 (ja)
EP (1) EP2606257B1 (ja)
JP (1) JP5910891B2 (ja)
KR (1) KR101801428B1 (ja)
CN (1) CN103154575B (ja)
DE (2) DE102011008863A1 (ja)
ES (1) ES2573732T3 (ja)
WO (1) WO2012022303A2 (ja)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20160090151A1 (en) * 2013-04-15 2016-03-31 Robert Bosch Gmbh Vehicle operable by motor and by muscular energy
US20230264781A1 (en) * 2022-02-18 2023-08-24 Joseph Francis Keenan System and method for bicycle transmission

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN106438906B (zh) * 2016-10-18 2019-01-15 绍兴文理学院 一种圆锥带式汽车无级变速器
CN106917864A (zh) * 2017-04-28 2017-07-04 石少雄 一种手自一体多级变速结构
CN108679181A (zh) * 2018-07-12 2018-10-19 上海欣原汽车技术开发有限公司 一种锥带式无级变速传动装置
CN110159715A (zh) * 2019-06-13 2019-08-23 宁波东液传动科技有限公司 用于液压马达的减速机构
CN110145592A (zh) * 2019-06-13 2019-08-20 宁波东液传动科技有限公司 一种用于液压马达的减速机构
CN110700111B (zh) * 2019-10-31 2021-01-29 河南城建学院 一种桥面混凝土层钢筋定位装置
CN113323999A (zh) * 2021-07-01 2021-08-31 郭玉刚 一种变速器
CN115091939A (zh) * 2022-08-26 2022-09-23 苏州亚太精睿传动科技股份有限公司 车辆驱动系统及方法、车辆

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1727232A (en) * 1928-02-03 1929-09-03 Stephen A Farrell Flexible mechanical power transmission

Family Cites Families (26)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1709346A (en) 1929-04-16 garrard
DE526751C (de) * 1929-04-04 1931-06-10 Escher Wyss Maschf Ag Reibraederwechselgetriebe
US2178859A (en) * 1937-06-25 1939-11-07 Robert M Jett Power transmission mechanism
JPS51114721A (en) 1975-04-01 1976-10-08 Taiyo Kogyo Kk Detachable pipe coupling
US4882948A (en) * 1987-06-08 1989-11-28 Byrnes Jr Raymond A Speed control assembly for nutating cone transmission
JPH07127702A (ja) * 1993-11-02 1995-05-16 Nobuhiko Matsumoto 無段変速装置
JP3661299B2 (ja) * 1996-09-13 2005-06-15 日産自動車株式会社 トロイダル型無段変速機
US5924953A (en) * 1997-05-21 1999-07-20 Rohs; Ulrich Friction cone gearing
US6028304A (en) 1998-01-21 2000-02-22 Sandia Corporation Precision displacement reference system
DE19837368A1 (de) * 1998-08-18 2000-02-24 Ulrich Rohs Kegelreibringgetriebe und Verfahren zur Regelung des Übersetzungsverhältnisses bei einem Kegelgetriebe
JP3855142B2 (ja) 1999-04-08 2006-12-06 允彦 丹原 無段変速機
US6387009B1 (en) 1999-11-22 2002-05-14 General Motors Corporation Traction drive with slip control and method of controlling the slip
US6471618B2 (en) * 2000-05-16 2002-10-29 Visteon Global Technologies, Inc. Torque biasing device, speed matching device and control methods
CN1623053B (zh) 2002-10-07 2011-07-20 乌尔里克·罗斯 传动机构
US7654930B2 (en) * 2003-01-09 2010-02-02 Ulrich Rohs Continuously adjustable gear
JP2004312881A (ja) 2003-04-07 2004-11-04 Smc Corp アクチュエータ
DE10350917B3 (de) * 2003-10-31 2005-05-25 Rle International Produktentwicklungsgesellschaft Mbh Übertragungsunterbrechungsfreies Schaltgetriebe
DE102004003716A1 (de) * 2004-01-24 2005-08-11 Zf Friedrichshafen Ag Kegelringgetriebe
ES2611087T3 (es) * 2004-08-06 2017-05-04 Ulrich Rohs Transmisión de anillo de fricción con dos cuerpos rodantes distanciados el uno del otro por una hendidura
JP2006250625A (ja) * 2005-03-09 2006-09-21 Ogasawara Precision Engineering:Kk 歯車歯形測定方法、歯車歯形測定装置およびこの歯車歯形測定装置に使用する測定用親歯車
EP1777441A1 (de) * 2005-10-24 2007-04-25 Getrag Ford Transmissions GmbH Stufenloses Getriebe und Verfahren zum Steuern desselben
US9328810B2 (en) * 2006-08-28 2016-05-03 Richard C. Raney Variable ratio gearmotor with interactive ratio control
DE102009032164A1 (de) * 2008-07-16 2010-01-21 Rohs, Ulrich, Dr. Ing. Reibringgetriebe mit einem Reibring und Verfahren zum Herstellen eines Reibkegels
US8574110B2 (en) * 2010-08-02 2013-11-05 Ford Global Technologies, Llc Transmission producing stepless variable speed ratios
US9903471B2 (en) * 2012-09-12 2018-02-27 GM Global Technology Operations LLC Control system and method for continuously variable transmission with variator speed ratio closed-loop feedback
US9970521B1 (en) * 2016-02-26 2018-05-15 Rodney J. Cook and successors in trust Infinitely variable transmission

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1727232A (en) * 1928-02-03 1929-09-03 Stephen A Farrell Flexible mechanical power transmission

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20160090151A1 (en) * 2013-04-15 2016-03-31 Robert Bosch Gmbh Vehicle operable by motor and by muscular energy
US9555854B2 (en) * 2013-04-15 2017-01-31 Robert Bosch Gmbh Vehicle operable by motor and by muscular energy
TWI648196B (zh) * 2013-04-15 2019-01-21 羅伯特博斯奇股份有限公司 可用馬達力和踏板力之中至少一種力驅動的車子
US20230264781A1 (en) * 2022-02-18 2023-08-24 Joseph Francis Keenan System and method for bicycle transmission
US11772743B2 (en) * 2022-02-18 2023-10-03 Joseph Francis Keenan System and method for bicycle transmission
US20230339572A1 (en) * 2022-02-18 2023-10-26 Joseph Francis Keenan System and method for bicycle transmission

Also Published As

Publication number Publication date
DE102011008863A1 (de) 2012-02-16
US20160327136A1 (en) 2016-11-10
CN103154575B (zh) 2016-02-17
DE112011102714A5 (de) 2013-05-29
JP2013534299A (ja) 2013-09-02
EP2606257B1 (de) 2016-04-13
WO2012022303A2 (de) 2012-02-23
KR101801428B1 (ko) 2017-11-24
WO2012022303A3 (de) 2012-06-14
EP2606257A2 (de) 2013-06-26
US10267392B2 (en) 2019-04-23
KR20130097188A (ko) 2013-09-02
CN103154575A (zh) 2013-06-12
JP5910891B2 (ja) 2016-04-27
ES2573732T3 (es) 2016-06-09

Similar Documents

Publication Publication Date Title
US10267392B2 (en) Cone/friction ring transmission and method for a cone/friction ring transmission
TWI413737B (zh) 無段變速器
CN102165219B (zh) 无级变速器
CN101535110A (zh) 无级变速传动装置
JP2005527741A (ja) 摩擦クラッチにより伝達されるトルクの調節装置及び方法
JP6622924B2 (ja) 自動変速機のプーリ推進装置および自動変速機の制御装置
US10473196B2 (en) Toroidal variable speed traction drive
RU2746972C2 (ru) Зубчатая передача
JP5712759B2 (ja) 歯車伝達装置用物理量測定装置
CN207212967U (zh) 即插即用型压扭联轴器
EP4170199A1 (en) Strain wave gear device and actuator
US20050160850A1 (en) Cone ring transmission
US4520693A (en) High ratio drive
WO2020188967A1 (ja) 摩擦ローラ減速機
US11293531B2 (en) Automatic transmission and control method of automatic transmission
JP2006503248A (ja) 鉄道車両のためのシャフトトレイン、特にカルダン軸および等速のボギー車駆動装置
CN107477102A (zh) 即插即用型压扭联轴器
JP5407399B2 (ja) 変速制御装置
KR102046835B1 (ko) 차동기어의 백래시 측정 장치
JP5077683B2 (ja) 車両の駆動制御装置
SE450737B (sv) Givaranordning for vridvinkelmetverden
US20040235612A1 (en) Toroidal gearbox with adjuster device
KR20090073957A (ko) 무단변속기
WO2018128848A9 (en) Method for control of a continuously variable drive having a ball planetary type continuously variable transmission
JP2014070731A (ja) 無段変速機の制御装置

Legal Events

Date Code Title Description
AS Assignment

Owner name: ROHS, ULRICH, GERMANY

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:ROHS, ULRICH;DRAEGER, CHRISTOPH;BRANDWITTE, WERNER;REEL/FRAME:029928/0851

Effective date: 20130213

STCB Information on status: application discontinuation

Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION