Traction mechanism with infinitely adjustable transmission

专利摘要:
The invention relates to a traction mechanism with continuously variable transmission, the first, non-rotatably coupled to a primary shaft and a second rotatably coupled to a secondary shaft (103), each of two cone-shaped traction pulley halves (105a, 105b) formed pulley (105) and a traction means (106) looping around the two traction mechanism pulleys (105) for transmitting a drive power from the primary shaft to the secondary shaft (103). In this case, one of the two traction pulley halves (105a) is fixed axially and the other traction pulley half (105b) is axially displaceable such that an axial distance between the traction pulley halves (105a, 105b) is infinitely adjustable and thus a gear ratio of the traction mechanism. For setting an on the traction means (1 06) acting axial clamping force a clamping force device (140) is provided which has a coaxial with the secondary shaft torque transmitting portion (108), the upper freewheel (141, 142) with the axially movable Zugmittelscheiben- Half (105b) of the second pulley (105) is coupled.
公开号:AT516841A4
申请号:T449/2015
申请日:2015-07-09
公开日:2016-09-15
发明作者:Jozef Vermeulen
申请人:Avl List Gmbh；
IPC主号:

专利说明:

Traction drive with infinitely adjustable transmission description
The invention relates to a traction mechanism with infinitely adjustable ratio for a vehicle.
Infinitely variable traction drives for vehicles are known in principle from the prior art, for example from US Pat. No. 5,057,061 or the article "Design of an Electromechanical Ratio and Clamping Force Actuator for a Metal V-belt Type CVT by K.G.O. van de Meerakker, P.C.J.N. Rosielle, B. Bonson and T.W.G.L. Klaassen from Eindhoven University of Technology.
Such Zugmittelgetriebe with infinitely adjustable translation generally have a drive shaft of the traction mechanism forming primary shaft, arranged parallel to the primary shaft, usually the output shaft of the traction mechanism secondary shaft, a first coaxial with the primary shaft arranged pulley and a second coaxially arranged to the secondary shaft pulley and a the two Zugmitteischeiben looping traction means, which is provided for transmitting a drive power from the primary shaft to the secondary shaft. In this case, the first traction pulley and the second traction pulley are usually formed in each case from two substantially conical traction pulley halves, between each of which the traction means is guided.
In this case, usually one of the two traction pulley halves of a traction pulley is axially fixed and the other half pulley half so axially displaceable within certain limits, that in each case a defined axial distance between the Zugmitteischeiben halves of the first Zugmitteischeibe and between the Zugmitteischeiben halves of the second Zugmittelscheibe is infinitely adjustable, so that by adjusting the axial distance of Zugmitteischeiben halves of the first pulley and the second pulley each having a defined effective Umschlingungsradius the traction means is infinitely adjustable and thus a defined translation of the traction mechanism.
For adjusting or adjusting the axial distance between the Zugmitteischeiben halves of the first pulley and / or the Zugmitteischeiben halves of the second pulley generic power transmission usually have a correspondingly trained adjusting device, which from the prior art traction mechanism with different Stellkonzepten and different
Actuators are known.
In addition to an adjusting device for adjusting or adjusting the axial distance between the Zugmitteischeiben halves of Zugmittelscheiben have generic
Zugmittelgetriebe also often additionally additionally a clamping force device for adjusting a on the guided between the two Zugmitteteiliben halves of Zugmittelscheibe traction means axially acting clamping force, preferably to adjust a force acting between the traction means and the Zugmitteischeiben halves of the second pulley friction, so that a desired torque or ., a desired drive power can be transmitted.
Clamping force devices have proved to be particularly advantageous with which different axial clamping forces can be applied at a set axial distance between the traction sheave halves, in particular clamping force devices with which an axial clamping force is achieved at an axial distance between the traction sheave halves set by means of the adjusting device can be adjusted depending on a torque to be transmitted. In other words, such clamping force devices are advantageous in which the clamping force regardless of the set axial distance between the
Traction pulley halves of the first and the second pulley can be adjusted.
On the one hand so-called mechanically self-regulating clamping force devices are known from the state of the art, in which the axial clamping force acting on the traction mechanism is mechanically generated between the traction pulley halves and automatically adjusted as a function of a torque to be transmitted, for example from the aforementioned US Pat. No. 5,057,061 or US Pat from a continuously adjustable traction mechanism developed by Jatco for the scooter Suzuki Burgman. In this case, various principles for a self-regulated, mechanical generation of the axial clamping force are known from the prior art.
The clamping force of the developed by the company Jatco traction mechanism has for self-controlled, mechanical generation of the axial clamping force, for example, a kind of cam control, wherein the cam control is formed by the axially displaceable traction pulley half of the second pulley and the secondary shaft. In this case, the axially displaceably mounted traction pulley half is rotatably mounted relative to the secondary shaft and designed such that at a low axial clamping force to overcome a voltage applied to the secondary shaft load torque, a rotational movement of the axially displaceable pulley half against the secondary shaft is triggered, which by means of Cam control leads to an axial displacement of the axially displaceable Zugmittelscheiben-half of the second Zugmittelscheibe in the direction of the other Zugmittelscheiben half and thus to an increase of the axial clamping force.
On the other hand, electrically or electronically controlled clamping force devices are known from the prior art, which usually have an electrically or electronically controllable and thus controllable and / or controllable clamping force actuator for generating the axial clamping force, clamping force devices being known in particular a hydraulic clamping force actuator or an electromechanical clamping force actuator. A clamping force device with an electromechanical clamping force actuator is known for example from the aforementioned article by the TU Eindhoven.
However, known from the prior art traction mechanism with infinitely adjustable translation, as a rule, have one or more disadvantages. Traction transmissions with electronically controlled clamping force devices usually require a complex sensor and mechanically self-regulating clamping force devices are often designed for safety reasons that it comes to an overpressure for a large part of the operating time, i. the generated axial clamping force is mostly higher during operation than actually required to transfer the drive power.
An object of the present invention is to provide an alternative traction mechanism with continuously variable transmission for a vehicle, in particular an improved traction mechanism with an improved clamping force device.
This object is achieved by means of a traction mechanism according to the teaching of claim 1, and with a vehicle according to the teaching of claim 14. Preferred developments of the traction mechanism according to the invention are the subject of the dependent claims. The wording of the claims is incorporated herein by express reference.
A traction mechanism according to the invention is provided for a vehicle and has a primary shaft, a secondary shaft arranged parallel to the primary shaft, a first traction pulley and a second traction pulley, wherein the first traction pulley is arranged coaxially to the primary shaft and two, in each case rotates coupled to the primary shaft in the is formed substantially conical traction pulley halves, and wherein the second pulley is coaxial with the secondary shaft and is formed of two, in each case rotating with the secondary shaft coupled, also substantially conical pulley halves is formed.
A traction mechanism according to the invention is understood to mean a belt transmission in which a drive power can be transmitted by means of a traction device from a first shaft to a second shaft. For example, belt transmissions or chain transmission traction mechanism in the context of the invention.
In the sense of the invention, a traction mechanism with a continuously variable transmission is understood to mean a traction mechanism in which the transmission is steplessly adjustable at least in a certain range, for example in a specific speed range or in a forward range or in a reverse range.
In the context of the invention, a traction means is understood to mean an elongate, flexible force transmission element whose two ends are connected and which is effective only in the pulling direction, ie. a power transmission element with which only tensile forces can be transmitted. A traction means in the context of the invention is for example a rope, a belt or a chain whose ends are connected together.
A pulley in the context of the invention is a disk-shaped component, which is designed to guide a traction means, preferably for guiding a traction device around a shaft, i. for guiding a traction device in the region of a looping of a shaft. On the other hand, a drive power can be transmitted from a shaft to a traction means or from a traction means to a shaft with a traction pulley.
Under a coaxial arrangement of two components to each other is understood in the context of the invention, an arrangement in which the components are arranged to each other such that their axes of rotation coincide.
A traction sheave cone shaped in the sense of the invention has at least partially a conical and / or frusto-conical geometry, wherein a substantially cone-shaped geometry also includes conical and / or frusto-conical geometries with a round base and a curved guide curve, i. where a boundary line from the circular base to the top of the cone or to the apex of the cone is curved and not straight.
For the purposes of the invention, "coupled" components are operatively connected to one another, wherein there is no need for a direct operative connection between the components, preferably any number of components in the chain of action can be arranged therebetween.
In the sense of the invention, a non-rotatable coupling is understood as meaning a coupling or an operative connection which is designed in this way. that the components together follow a rotational movement, d, h. that, for example, a second component rotates with a first component and is not rotatable relative thereto. The components need not be directly connected to each other, but may also be coupled to each other via intermediate elements. In a rotatable coupling, however, the mutually coupled components are rotatable relative to each other.
In a traction mechanism according to the invention, the first traction pulley and the second traction pulley are preferably looped around by a traction device guided in each case between the traction pulley halves of the first pulley and between the traction pulley halves of the second pulley, wherein the traction means for transmitting a drive power from the primary shaft to the Secondary shaft is provided.
In other words, in the traction mechanism according to the invention preferably the traction means is guided around the primary shaft by means of the first traction pulley and by means of the second pulley around the secondary shaft, wherein the traction means is guided in each case between the two traction pulley halves. To transmit the drive power from the primary shaft to the secondary shaft, the drive power applied to the primary shaft can be transmitted by the first pulley from the primary shaft to the traction means and by means of the second pulley from the traction device further to the secondary shaft.
One of the two Zugmittelscheiben halves of the first pulley and / or the second pulley is preferably axially fixed in the Zugmittelgetriebe invention and the other half pulley half so axially displaceable within certain limits, that a defined axial distance between the pulley halves of the first Zugmittelscheibe and / or the second Zugmittelscheibe can be adjusted continuously, whereby an effective radius of wrap of the traction means can be adjusted continuously and thus a defined translation of the traction mechanism.
The property of axial means according to the invention, in particular along a longitudinal axis and / or along a rotation axis.
For the purposes of the invention, the effective radius of wrap also refers to the current radius which, in the region in which the traction device wraps around the shaft, defines the distance of the traction device from the axis of rotation of the associated shaft.
The substantially cone-shaped traction pulley halves of the first pulley and the second pulley are preferably each arranged such that their substantially conical surfaces face each other and form a kind trapezoidal Zugmittelspur in which the traction means is guided, so that a change of the axial Distance between the traction pulley halves in each case leads to a change in the radial distance of the traction means to the axis of rotation of Zugmittelscheiben and consequently to a change in the effective radius of curvature.
The traction mechanism according to the invention preferably further comprises an adjusting device for adjusting the axial distance between the traction pulley halves of the first pulley and / or for adjusting the axial distance between the traction pulley halves of the second pulley.
Furthermore, the traction mechanism according to the invention preferably has a clamping force device for adjusting an axial, acting between the two Zugmittelscheiben halves of the second pulley on the traction means clamping force, wherein the clamping force device is adapted to mechanically generate at least a portion of the force acting on the traction means clamping force, ie , without an additional clamping force actuator.
According to the invention, the clamping force device for generating the mechanical clamping force portion between the two traction pulley halves of the second pulley preferably arranged coaxially to the secondary shaft, coupled to the secondary shaft, an output side of the traction mechanism forming and axially fixed torque transmission section rotatably relative to the rotationally fixed is mounted with the secondary shaft coupled, axially displaceable Zugmittelscheiben half of the second pulley. In this case, the torque-Qbertragungsabschnitt is preferably coupled via at least one coaxial with the secondary shaft arranged freewheel with the axially displaceable traction pulley half of the second pulley. The freewheel is preferably designed and coupled to the torque transmission section of the axially displaceable traction pulley half of the second pulley, that by a relative rotation between the torque transmission section and the axially displaceable pulley half of the second pulley an axial displacement of the axially movable pulley Half is effected and, as a result, a change in the axial clamping force.
In other words, in the traction mechanism according to the invention for generating an axial clamping force, a relative rotation between the torque transmission portion and the axially displaceably mounted traction pulley half of the second pulley is effected, through which axially displaceably mounted traction pulley half of the second pulley so axially can be that an axial clamping force arises.
Since the torque-transmitting portion is preferably rotatably mounted relative to the rotatably coupled to the secondary shaft, axially displaceable Zugmittelscheiben half of the second pulley, the torque transmission portion is thus rotatably mounted relative to the secondary shaft and consequently rotatable relative to the secondary shaft. As a result, purely mechanically and thus in a simple manner, an axial clamping force generating relative rotation between the torque transmission section and the axially displaceable Zugmittelscheiben half of the second pulley can be effected, for example, by a torque applied to the transmission section and one of the secondary shaft applied torque deviating load torque.
In the context of the invention, a load torque in the sense of the invention is understood as meaning a resistance torque directed in the opposite direction to a torque applied to the secondary shaft.
Under a freewheel in the context of the invention is understood to mean acting only in one direction of rotation clutch, which is often referred to as a so-called overrunning clutch. When reversing the direction of rotation or when the speed on the output side is greater than on the drive side, i. if slippage occurs, the rotary joint is released, i. a relative rotation is allowed. Freewheels are well known in the art and are used, for example, in bicycle hubs to allow the bicycle to roll without pedaling.
The use of a freewheel for coupling the torque transmission device with the axially displaceably mounted traction pulley half of the second pulley has the advantage over a cam control, which represents an alternative embodiment for a self-regulated, mechanical generation of an axial clamping force, that with a corresponding design of the freewheel , only a slight relative rotation, ie only a small angle of rotation, in particular only a twist angle of only about 10 °, between the torque-transmitting portion and the axially displaceable Zugmittelscheiben-half for generating or adjusting an axial clamping force is required. Furthermore, less wear usually occurs than with a cam control, in which a cam slides over a control surface or is guided along a control surface.
A further advantage of the traction mechanism according to the invention is further that by the inventive coupling of the torque transmission portion with the axially displaceably mounted traction pulley half of the second pulley on the freewheel and by the rotationally fixed coupling of the traction pulley halves of the second pulley with the secondary shaft relative rotation between The torque-transmitting portion and the axially displaceably mounted Zugmittelscheiben half can be effected without a relative rotation between the two Zugmittelscheiben halves of the second pulley results. As a result, acting on the traction means loads due to a relative rotation of the axially fixed
Traction pulley half and the axially displaceably mounted traction pulley half would arise and are particularly unfavorable for steel belts as traction means are avoided, so that a traction mechanism according to the invention is also suitable for the use of metallic traction means, in particular for the use of steel belts as traction means ,
Metallic traction means, in particular steel belts, have the advantage over traction means with plastic and plastic traction means that higher torques can be transmitted with them. Traction means with plastic, in particular traction means made of plastic, however, have the advantage that they do not have to be performed in oil.
It goes without saying that in a traction mechanism according to the invention, the material of Zugmittelscheiben halves and the material of the traction means are matched to each other and in particular the surfaces of the traction pulley halves and the contact surfaces of the traction means are designed such that an optimal power transmission as possible low friction losses.
In cases where high axial clamping forces are not required, i. In particular, in cases where no high torques must be transmitted, it is advantageous if not only a clamping force component can be generated with the clamping force device according to the invention, but the entire axial clamping force which is required by means of the traction means a means the traction mechanism maximum transferable torque to the second pulley and thus transmitted to the secondary shaft can.
Is to generate the necessary axial clamping force no additional clamping force actuator or the like required, a particularly simple construction of the clamping force device and thus the traction mechanism is possible, whereby a cost-effective traction mechanism can be provided.
An inventive traction mechanism is thus particularly suitable for vehicles in which only smaller torques are to be transmitted from the primary shaft to the secondary shaft, i. where only a small axial clamping force is necessary to produce the required frictional force, such as in quads, skidoos, scooters or the like.
The torque transmitting section, which forms the output side of the traction mechanism, is preferably a type of sleeve or the like, which is applied to the secondary shaft and arranged coaxially therewith, wherein the torque transmission section is preferably fixed axially.
In an advantageous embodiment of the traction mechanism according to the invention, the torque transmission section is rotatably supported only within certain limits in the circumferential direction with respect to the axially displaceable Zugmittelscheiben half of the second pulley and thus only within certain limits in the circumferential direction rotatable relative to the secondary shaft, i. only in a defined rotation angle range or with a defined play in the direction of rotation, so that only a defined slip, i. a defined speed difference in the circumferential direction, between the torque-transmitting portion and the rotatably coupled to the secondary shaft, axially displaceably mounted traction pulley half of the second pulley is permissible.
In a further advantageous embodiment of the traction mechanism according to the invention the traction mechanism is designed such that the drive power to be transmitted from the primary shaft to the secondary shaft is each frictionally transmitted to the traction means. In other words, in an advantageous embodiment, the traction means is a flat belt, a V-belt, a round belt or a lamella chain. If the transmission of the drive power from the first pulley to the traction means and / or from the traction means to the second pulley frictionally, the transmittable drive power, in particular a maximum transmissible torque depends directly on the axially acting on the traction means clamping force, which of the two traction pulleys -Halften, between which the traction means is guided, is applied to the traction means.
In a further advantageous embodiment of the traction mechanism according to the invention the adjusting device for adjusting the axial distance of the traction pulley halves of the first pulley and the second pulley is formed such that the axial distance of the traction pulley halves of the second pulley as a function of the axial distance of the traction pulley halves adjusts the first pulley, wherein preferably the axial distance of the traction pulley halves of the second pulley decreases when the axial distance of the traction pulley halves of the first pulley increases and vice versa.
In a further advantageous embodiment of the traction mechanism according to the invention, the clamping force device is designed such that the clamping force can be generated at least partially in response to a voltage applied to the torque transmission section load torque.
Thereby, the axial clamping force can be adjusted depending on the torque applied to the torque transmission section load torque, wherein the clamping force device is preferably designed such that the axial clamping force that is generated, each being as small as possible, but sufficiently large to by means of the traction means to transmit torque from the traction means to the second pulley and thus the secondary shaft, which is sufficiently large to overcome the load torque applied to the torque transmission section, provided that the load torque applied to the torque transmission section is smaller than the maximum transmissible torque of the traction mechanism. As a result, a need-based axial clamping force can be generated, in particular, thus leading to increased wear Überanpressung can be avoided or reduced.
In a further advantageous embodiment of the traction mechanism according to the invention, the clamping force device, in particular the freewheel, is designed such that a relative rotation between the torque transmission section and the axially displaceable pulley half of the second pulley axial displacement of the axially displaceable pulley half of the second pulley is effected and consequently a change in the axial clamping force when slip occurs between the torque transmission section and the axially displaceable traction pulley half of the second pulley, provided that the maximum transmissible by the traction mechanism torque has not been reached.
Slip according to the invention occurs when the current rotational speed of the torque-transmitting portion of the current rotational speed of the axially displaceable pulley half of the second pulley deviates, i. E. When the rotational speed of the torque-transmitting portion is greater or less than the current rotational speed of the axially displaceable Zugmittelscheiben-half of the second pulley, for example, as a result of a torque applied to the secondary shaft torque torque.
In a further development of the traction mechanism according to the invention, the clamping force device is configured such that a torque applied to the torque transmission section, which is smaller than a currently acting between the traction means and the traction pulley halves of the second pulley friction force currently transmissible torque (ie if the axial Clamping force is so large that a larger torque can be transmitted than the currently applied load torque), causes an increase in the distance between the Zugmittelscheiben halves of the second pulley and thus a decrease in the clamping force, and / or such that a voltage applied to the torque transmission section Lastmoment, which is greater than a currently acting between the traction means and the traction sheave halves of the second pulley friction force currently transmissible torque (ie, if the currently applied axial clamping force is insufficient to generate a corresponding frictional force between the traction pulley halves of the second pulley and the traction means to transmit a torque corresponding to the applied load torque), causes a reduction in the distance of the traction pulley halves of the second pulley and thus an increase in the clamping force.
Preferably, the clamping force device is designed such that in each case an axial displacement of the axially displaceable Zugmittelscheiben half of the second Zugmittelschelbe is effected, and thus a corresponding increase or decrease in the clamping force until each of the torque transmission section applied load torque due to the currently acting frictional force currently transferable
Torque corresponds. That Preferably, the clamping force device is designed such that an axial displacement is effected when the currently transferable torque and the applied load torque differ, in particular, no further axial displacement is effected when the currently transmissible torque corresponds to the applied load torque.
In a further advantageous embodiment of the traction mechanism according to the invention, the freewheel is arranged in the radial direction between an axially extending flange of the axially displaceable traction pulley half of the second pulley and the torque transmission section. That in other words, that the axially displaceable pulley half of the second pulley preferably has a flange extending in the axial direction over which the torque transmission section extends like a kind of sleeve on the outside and on the freewheel quasi "aufgesteckf and such, that the freewheel is in the radial direction between the flange of the axially displaceable Zugmittelscheiben half of the second pulley and the torque-transmitting portion.
Preferably, the freewheel is coupled via a thread with a defined pitch with the torque transmission section and in particular axially fixed to the axially displaceable Zugmittelscheiben half of the second Zugmittelscheibe and rotatably connected thereto, so that a relative rotation of the torque transmission section relative to the freewheel, if the freewheel is blocked, due to the thread and the rotatably connected to the freewheel, axially displaceable Zugmittelscheiben half causes axial displacement of the axially displaceably mounted traction pulley half of the second pulley and thus the generation or setting a desired axial force. Via a pitch of the thread, a gradient of the axial force or the axial clamping force in dependence on the relative rotation can be adjusted.
For this purpose, the torque transmission section preferably has a sleeve-shaped section with an internal thread, and the freewheel preferably has a correspondingly formed external thread which is formed corresponding to the thread of the torque transmission section.
Of course, the freewheel also be rotatably coupled to the torque-transmitting portion and be axially fixed to this and be coupled via a thread with the axially displaceably mounted Zugmittelschelben half of the second pulley, in which case the freewheel preferably has an internal thread and the pulleys Half of the second pulley, which is mounted axially displaceable, preferably corresponding to a correspondingly formed external thread.
In a further advantageous embodiment of the traction mechanism according to the invention, the torque transmission section has a first and a second freewheel and is coupled in each case via the first freewheel and the second freewheel with the axially displaceable traction pulley half of the second pulley. In this case, the first freewheel is preferably designed and coupled to the torque transmission section and the axially movable traction pulley half of the second pulley, which is adjustable by means of the first freewheel, the axial clamping force in a traction mode of the traction mechanism and preferably by means of the second freewheel, the axial clamping force in a push operation.
For the purposes of the invention, the term traction mode preferably describes a driving state in which the traction mechanism according to the invention is driven from the drive side, i. About the applied to the primary shaft drive power is kept in rotational motion, while the term coasting operation in the context of the invention, a driving condition is described, in which the traction mechanism according to the invention with closed power flow from the output side, i. via the torque transmission section applied load torque is kept in rotational motion.
In a further advantageous embodiment of the traction mechanism according to the invention both freewheels, i. the first freewheel and the second freewheel, arranged in the radial direction between the axially displaceable Zugmittelscheiben half of the second pulley and the torque-transmitting portion, preferably both freewheels are each coupled via a thread with a defined pitch with the torque-transmitting portion. Preferably, the axially displaceably mounted traction pulley half of the second pulley to a correspondingly far in the axial direction extending, long flange.
Preferably, the first freewheel and the second freewheel are coupled to the torque transfer section via threads of different thread pitch, i. Preferably, the two threads, with which the first freewheel and the second freewheel are each coupled to the torque transmission section, have different thread pitches. As a result, for example, different Klemmkraftgradienten for the train operation and the overrun operation can be adjusted in a simple manner.
Preferably, the first provided for adjusting the axial clamping force in traction freewheel in the axial direction between the second, provided for adjusting the axial clamping force in overrun freewheel and the axially displaceable traction pulley half of the second pulley. As a result, the second freewheel can be relieved in the train operation, since then in the train operation cores power transmission via the second freewheel, whereby the second freewheel can be made smaller and thus cost-effective, because usually the time portion of the life, in which the traction mechanism according to the invention is operated in traction, significantly greater than the time component in overrun operation.
In a development of the traction mechanism according to the invention the clamping force device is designed such that only one freewheel is currently blocked, i. preferably both freewheels can not block at the same time.
In a further advantageous embodiment of the traction mechanism according to the invention, the torque transmission section for distributing the axial Kiemmkraft on both Zugmittelscheiben halves of the second pulley via a tie rod with the axial T x I x__ T. UüIAa iiapUi in # Iah ΠaUai aIIa CaI / i inrl » iπι / λΙΙλ preferably at least in the region of the second pulley a hollow shaft and the pull rod within the secondary shaft from the torque transmission section to the axially fixed traction pulley half out.
A tension rod in the sense of the invention is preferably a rod-shaped component with which tensile forces can be transmitted between the components connected to this component.
By using a tension rod, in particular a tension rod arranged in this way, the axial clamping force does not act on the bearings of the secondary shaft, so that they can be dimensioned smaller. Furthermore, a uniform distribution of the generated axial clamping force on both Zugmitteischeiben halves can be achieved and thus a particularly uniform frictional force between traction means and Zugmitteischeiben halves of the second pulley, whereby a particularly uniform force or torque transmission is ensured. With the aid of such a tension rod, a very precise adjustment of the required axial clamping force is thus possible, as a result of which an overpressure associated with increased wear can be largely avoided.
In a further advantageous embodiment of the traction mechanism according to the invention, the clamping force means for increasing the axial clamping force at least one coaxial with the secondary shaft arranged clamping force coil spring, wherein the clamping force coil spring preferably under bias on the axially displaceable pulley half of the second pulley and in particular on a a spring plate forming, is supported in the radially outwardly extending flange of the torque transmission portion. By supporting the clamping force coil spring on two rotatably mounted to each other components or two non-rotatable components, a rotation of the clamping force coil spring itself can be avoided, which in particular reduces the wear of the clamping force coil spring and the friction of the traction mechanism can be reduced can.
In some cases, it may be advantageous to use two co-axial clamping force coil springs, i. an inner clamping force coil spring and an outer clamping force coil spring.
In a further advantageous embodiment of the traction mechanism according to the invention, the clamping force device has a clamping force actuator and is adapted by means of the clamping force actuator in addition to the, depending on a voltage applied to the torque transmission section load torque share a further, axial Klemmkraft- Proportion to the second pulley, wherein the clamping force actuator is preferably coupled mechanically such with the clamping force coil spring that the clamping force coil spring for applying an additional clamping force share can be compressed by means of the clamping force actuator. For this purpose, the clamping force coil spring is preferably supported via a spring plate axially displaceable relative to the torque transmission section, the clamping force actuator being coupled in particular to the spring plate on which the clamping force coil spring is supported.
In an advantageous embodiment of the traction mechanism according to the invention, the actuator is an electric motor, in particular an electronically controllable electric motor.
In a further development of the traction mechanism according to the invention, the clamping force means for applying the generated by the clamping force actuator, further axial clamping force share on the second pulley on a coaxially arranged to the secondary shaft ball ramp, wherein the clamping force actuator is preferably coupled via a toothing with the ball ramp and in particular via the ball ramp with the clamping force coil spring. In this case, the clamping force actuator is in particular an electric motor,
Preferably, the axial force generated in this way can be transmitted from the ball ramp via a thrust bearing on the spring plate, with which the clamping force coil spring is supported.
Of course, the clamping force actuator may also be a hydraulic motor and / or be coupled via a gear and / or a gear with the ball ramp.
An inventive vehicle with a traction mechanism with infinitely variable transmission is characterized in that it comprises a prescribed, inventive traction mechanism,
These and other features are apparent from the claims and from the description also from the drawings, wherein the individual features may be implemented alone or in the form of sub-combinations in an embodiment of the invention and an advantageous and protectable in itself Execution can represent, for which also claimed protection.
In the following the invention with reference to several embodiments will be further explained, the invention being schematically illustrated in the accompanying drawings. It shows
Fig. 1 in sectional view a known from the prior art
Traction drive with infinitely variable transmission,
2 shows a detail of a first embodiment of a traction mechanism according to the invention in the region of the secondary shaft with a first embodiment of a Kiemmkrafteinrichtung invention in sectional view,
Fig. 3a also in section a section of a second
Embodiment of a traction mechanism according to the invention in the region of the secondary shaft with an alternative, inventive
Kiemmkrafteinrichtung,
3b shows the detail of Fig. 3a in perspective view,
4 is a detail of a third embodiment of a traction mechanism according to the invention in the region of the secondary shaft with parts of a third embodiment of a clamping force device according to the invention in a perspective view,
5 shows a further section of the third exemplary embodiment of a traction mechanism according to the invention in the region of the secondary shaft with the clamping force device from FIG. 4, FIG.
6a shows the detail of FIG. 5 in a longitudinal section with a set transmission ratio <1,
Fig. 6b shows a detail of a cross section through the invention
Clamping force device from FIG. 6a along the cutting plane D-D,
Fig. 6c shows a section of a cross section through the invention
Clamping force device of FIG. 6a along the cutting plane C-C,
6d shows the detail from FIG. 6a in a side view from the left, FIG.
7a shows the detail of FIG. 6a, but with a set transmission ratio> 1,
Fig. 7b, the detail of Fig. 7a in side view from the left and
Fig. 7c the detail of Fig. 7a in a side view from the right.
In Fig. 1 is an example of a generic, known from the prior art
Traction mechanism 1 with continuously adjustable ratio shown in cross-section to explain the basic function of a generic Zugmittelgetriebes with continuously adjustable ratio.
This, known from the prior art traction mechanism 1 has, as in generic Zugmittelgetrieben usual, a rotatable about a rotation axis 14 primary shaft 2 and a parallel to this arranged and rotatable about a rotation axis 15 secondary shaft 3, wherein the primary shaft 2 and the secondary shaft. 3 are each mounted on here unspecified ball bearings in a gear housing 10.
Coaxially to the primary shaft 2, a first pulley 4 is arranged, which is formed from two substantially conical pulley halves 4a and 4b, wherein the pulley halves 4a and 4b are each arranged such that the conical surfaces face each other.
Coaxially to the secondary shaft 3, a second pulley 5 is arranged, which is also formed of two substantially conical pulley halves 5a and 5b, wherein also in this pulley 5, the conical surfaces of the two pulley halves 5a and 5b are arranged such that they facing each other.
In this example of a generic traction mechanism 1 with continuously variable transmission, the two traction pulley halves 4a and 4b of the first traction pulley 4 and the two traction pulley halves 5a and 5b of the second pulley 5 each rotatably coupled to the primary shaft 2 and the secondary shaft 3 and are wrapped by a traction means 6 in the form of a plastic flat belt whose ends are connected together. The traction means 6 is guided in each case between the conical surfaces of the traction pulley halves 4a and 4b and 5a and 5b. A drive power can be transmitted to the primary shaft 2 of the traction mechanism transmission 1 via a drive shaft 9, to which a gear assembly is flanged, which is likewise not specified here, from there via the first pulley 4 to the traction means 6. By means of the traction means 6, the drive power can be dissipated to the second pulley 5 and via this to the secondary shaft 3. The drive power can be dissipated via a torque transmission section 8 coupled in a rotationally fixed manner to the secondary shaft, for example to an output shaft of a vehicle.
In a generic traction mechanism is usually, as in this traction mechanism 1 each one of the two traction pulley halves 4a and 5a fixed axially, i. not movably mounted in the axial direction. In some cases, it may be advantageous, as in the traction mechanism 1 shown in Fig. 1, when the traction pulley halves 4a and 5a thereto are integrally formed with the associated shaft, i. with the primary shaft 2 and the secondary shaft. 3
The other pulley half 4b and 5b is usually axially displaceably mounted in a generic traction mechanism, in each case such that a defined axial distance between the traction pulley halves 4a and 4b of the first pulley 4 and between the pulley halves 5a and 5b of second pulley 5 can be adjusted continuously and thus an effective radius of wrap, with which the traction means 6 is guided around the first pulley 4 and the second pulley 5, and thus a defined translation of the traction mechanism first
The axial displaceability of the traction pulley halves 4b and 5b is in each case by different axial distances to the axially fixed traction pulley halves 4a and 5a of the axially displaceable traction pulley halves 4b and 5b above and below the primary shaft 2 and the secondary shaft 3 symbolic shown. In reality, the axial distance between the axially fixed traction pulley 4a and 5a and the axially displaceable traction pulley half 5a and 5b is of course constant in the circumferential direction over the entire circumference of a pulley half, i. Of course, the pulley half 4b and 5b are each rotationally symmetrical to a rotational axis 14 and 15, respectively.
For adjusting or adjusting the axial distance between the pulley halves 4a and 4b of the first pulley 4 and the pulley halves 5a and 5b of the second pulley 5, the traction mechanism 1 has an adjusting device with an electric motor 7 as a servo-actuator.
The electric motor 7 is coupled via an unspecified gear stage and a likewise not designated linear spindle with the axially displaceably mounted traction pulley half 4b, wherein the electric motor 7 is so operatively connected to the axially displaceably mounted pulley half 4b that by means of Stellstell- Actuator 7, an axial displacement of the axially displaceably mounted traction pulley half 4b can be effected. For an exact setting, the traction mechanism 1 shown here has a position sensor, which is not described here in more detail, with which a current position of the traction pulley half 4b mounted in an axially displaceable manner can be detected and adjusted.
The axially displaceable traction pulley half 4b has for this purpose a sleeve-shaped, unspecified portion which is arranged coaxially to the primary shaft 2 around this around and with which the axially displaceably mounted traction pulley half 4b is rotatably coupled to the primary shaft 2. About a ball bearing 12 is a gear axially fixed, but rotatably mounted relative to the axially displaceably mounted traction pulley half 4b on this sleeve-shaped portion of the axially displaceably mounted traction pulley half 4b.
By applying a rotational movement by means of the electric motor 7 to the gear wheel in engagement with the linear spindle thus axial displacement of the gear and consequently the axially fixed to the gear axially displaceable Zugmittelscheiben half 4b can be effected and the axial distance between the Zugmittelscheiben halves 4a and 4b of the second pulley 4 are adjusted or adjusted. If the distance between the traction pulley halves 4a and 4b of the first pulley 4 changes, a width of a traction means track changes, with the result that the effective radius of wrap, with which the traction means 6 between the two traction pulley halves 4a and 4b of the first Pulley 4 is guided, changes. That is, the traction means 6 moves further inwards, i. E. in the direction of the axis of rotation 14 or further outwards, i. away from the axis of rotation 14.
This is in Fig. 1, as already mentioned above, in each case by different axial distances between the pulley halves 4a and 4b of the first pulley 4 and between the pulley halves 5a and 5b of the second pulley 5 above and below the primary shaft. 2 or the secondary shaft 3 symbolically represented. In this case, a set, small distance between the pulley halves 4a and 4b of the first pulley, in which the belt 6 runs at the outermost edge of the pulley 4, in conjunction with a set, large distance between the pulley halves 5a and 5b, at wherein the belt 6 is guided around the second pulley 5 with a small radius of curvature, as shown above the primary shaft 2 and the secondary shaft 3, to a transmission ratio <1, while a set, large distance between the pulley halves 4a and 4b of the first Zugmittelscheibe in which the belt 6 is guided around the first pulley 4 with a small radius of curvature, in conjunction with a set, small distance between the Zugmittelscheiben halves 5a and 5b, in which the belt 6 runs at the outermost edge of the pulley 5, such as below the primary shaft 2 or the Seku 3, to a transmission ratio> 1.
Due to the peripherally formed traction means 6 causes an increase in the effective radius of wrap of the first pulley 4, i. a reduction of the axial distance between the Zugmittelscheiben halves 4a and 4b of the first pulley 4, in the embodiment shown due to the resulting changing forces on the traction means 6 quasi "automatically" an increase in the distance of the traction pulley halves 5a and 5b of the second pulley In particular, a tensile force acting on the traction means 6 due to the increasing effective radius of curvature of the first traction pulley 4 causes the two traction pulley halves 5a and 5b of the second pulley 5 to slide apart so that the effective radius of wrap of the second traction pulley 5 is automatically shifted due to the reduced constant Zugmittellänge.
Since the transmission of the drive power from the first pulley 4 on the flat belt 6 and from the belt 6 to the second pulley 5 each frictionally via the conical surfaces of the pulley halves 4a and 4b and 5a and 5b, is for transmitting the drive power, in particular a drive torque, in each case a sufficient frictional force and thus a sufficient axial clamping force between the traction means 6 and the traction pulley halves 4a and 4b or 5a and 5b required.
To generate an additional, axial clamping force component between the pulley halves 5a and 5b of the second pulley 5 in addition to the set by the set distance between the pulley halves 4a and 4b and 5a and 5b respectively adjusting, axial clamping force has the traction mechanism 1 a clamping force device 40 with a clamping force coil spring 11, which is installed with the axially displaceably mounted traction pulley half 5b under bias. In this case, the clamping force coil spring 11 is supported on the axially displaceably mounted traction pulley half 5b as well as on a likewise rotatably connected to the secondary shaft 3 spring plate 13. The size of the currently acting, additional axial clamping force proportion depends on the one hand on the spring stiffness of the clamping force coil spring 11 and on the other of the current axial distance between the pulley halves 5a and 5b of the second pulley 5 and is thus structurally predefined.
An inventive, not shown in its entirety traction mechanism is constructed in principle similar and also has a primary shaft with a first pulley, which is formed from two each substantially conical, rotatably coupled to the primary shaft Zugmittelscheiben halves and arranged coaxially to the primary shaft are, and a secondary shaft with a second pulley, which is also formed of two respectively substantially conical pulley halves, which are arranged coaxially to the secondary shaft and also rotatably coupled thereto. In a traction mechanism according to the invention, the primary shaft and the secondary shaft are preferably also mounted in a transmission housing similar to the traction mechanism described with reference to FIG. 1 from the prior art.
The first pulley and the second pulley of the traction mechanism according to the invention are also wrapped by a respectively between the pulley halves of the first pulley and the pulley halves of the second pulley guided traction means, wherein the traction means also for transmitting a drive power from the primary shaft to the Secondary shaft is provided.
One of the two Zugmittelscheiben halves of the first pulley and / or the second pulley is also axially fixed in the Zugmittelgetriebe invention and the other Zugmittelscheiben half axially within certain limits such that a defined axial distance between the pulley halves of the first pulley and / or the second Zugmittelscheibe can be adjusted continuously, whereby an effective radius of wrap of the traction means can be adjusted continuously and thus a defined translation of the traction mechanism.
An inventive traction mechanism further also has an adjusting device which is adapted to adjust an axial distance between the traction pulley halves of the first pulley and the pulley halves of the second pulley and to set a defined axial distance. The adjusting device can also be formed, as described with reference to the generic, known from the prior art and shown in Fig. 1 traction mechanism 1, described actuator. But it can also have a common actuator actuator for adjusting or adjusting the axial distance between the traction pulley halves of the first pulley and the pulley halves of the second pulley. Such adjusting devices are well known from the prior art.
According to the invention, a traction mechanism according to the invention, in contrast to the traction mechanism 1 shown in FIG. 1, however, has a mechanically self-regulating clamping force device, with which different, axial clamping forces on the second
Zugmittelscheibe can be applied, in particular, a clamping force component can be generated mechanically controlled self-controlled.
The components of a first embodiment of a clamping force device 140 according to the invention of a first embodiment of a traction mechanism according to the invention are shown in Fig. 2, which shows a detail of a first embodiment of a traction mechanism according to the invention for a vehicle with continuously variable transmission in the region of the secondary shaft 103.
As described above, a traction mechanism according to the invention and thus also this embodiment has a second traction pulley 105 arranged coaxially to a secondary shaft 103, which is formed from two respectively substantially cone-shaped traction pulley halves 105a and 105b, which are non-rotatable with the about an axis of rotation 115th rotatable secondary shaft 103 are coupled. The secondary shaft 103 is mounted similar to the traction mechanism described in FIG. 1 in the transmission housing, not shown here.
The second pulley 105 is thereby, as in the known from the prior art with reference to FIG. 1 traction mechanism from a, in each case between the pulley halves 105a and 105b of the second pulley 105 out, but not shown here traction means in the form of a plastic Flat belt entwined, wherein the traction means is provided for transmitting the drive power from the primary shaft, not shown, to the secondary shaft 103.
The clamping force device 140 is designed to apply an axial force to the axially displaceable traction pulley half 105b such that the axially displaceable traction pulley half 105b with an axial clamping force against the traction means, not shown here, between the two traction pulley halves 105a and 105b 106 is pressed, whereby the traction means is also pressed against the traction pulley half 105a, so that between the traction means and the pulley halves 105a and 105b each sufficient frictional force can be adjusted so that a desired torque from the traction means on the pulley 105, in particular the two pulley halves 105a and 105b can be transmitted.
In this embodiment, the left in Fig. 2 Zugmittelscheiben half 105 a is integrally formed with the secondary shaft 103 and thus axially fixed to the secondary shaft 103. The right half pulley half 105b is mounted so axially displaceable that a defined axial distance between the pulley halves 105a and 105b of the second pulley 105 can be adjusted continuously, whereby an effective radius of wrap of the traction means can be adjusted continuously and thus a defined translation of the Zugmittelgetriebes invention. According to the invention, the traction pulley half 105b mounted in an axially displaceable manner is non-rotatably coupled to the secondary shaft 103.
Further, the clamping force device 140 according to the invention arranged coaxially to the secondary shaft 103 and rotatably mounted relative to the secondary shaft 103 torque transmission section 108, which forms a driven side of the traction mechanism according to the invention and is provided for discharging the drive power from the traction mechanism and coupled for example with an output shaft of a vehicle can be. In this case, the torque transmission section 108 has a sleeve-shaped region with which the torque transmission section 108 is coupled via two freewheels 141 and 142 to the axially displaceable traction pulley half 105b of the second pulley 105, with the freewheels 141 and 142 being designed in this way in that by a relative rotation between the torque-transmitting portion 108 and the axially displaceable
Zugmittelscheiben half 105b of the second Zugmittelscheibe 105 axial displacement of the axially movable Zugmittelscheiben half 105b is effected and consequently a change in the axial clamping force.
The freewheels 141 and 142 are arranged in the radial direction between an axially extending flange of the axially displaceable Zugmittelscheiben half 105b of the second pulley 105 and the torque transmission portion 108 and each have a thread 145 and 146 with a defined pitch with the Torque transmission portion 108 is coupled, wherein the torque transmission portion 108 each having an internal thread and the freewheels 141 and 142 each have a corresponding thereto formed external thread.
The two freewheels 141 and 142 are each axially fixed to the axially displaceable traction pulley half 105b of the second pulley 105 and rotatably connected to the axially displaceable pulley half 105b of the second pulley 105.
The closer to the pulley 105 and between the Zugmittelschiebe 105 and the second freewheel 142 arranged freewheel 141 is designed for power transmission in the train operation, while the freewheel 142 is formed for a power transmission in overrun operation, wherein the pitches of the threads 145 and 146 are formed differently , so that in the train operation against the overrun operation with the same relative rotation of the torque transmission section 108 relative to the axially displaceable traction pulley half 105b sets a different axial clamping force.
The two freewheels 141 and 142 are designed such that in each case only one freewheel currently, i. at the same time, can block, which provided for the power transmission in traction freewheel 141 blocked in train operation and provided for the overrun freewheel 142 in overrun mode.
If the freewheel provided for the traction operation 141 is blocked and if a torque which can be transmitted to the traction pulley 105 by means of the traction means is smaller than a load torque applied to the torque transmission section 108, a relative rotation can occur due to the blocking of the freewheel 141 and the load torque applied to the torque transmission section 108 be effected between the freewheel 141 and the torque-transmitting portion 108 and formed by the trained between the freewheel 141 and the torque transmission portion 108 thread 145 a relative movement in the axial direction between the freewheel 141, the axially mounted on the axially displaceable traction pulley half 105 b is and the torque-transmitting portion 108 which is axially fixed in the transmission housing, are generated. In such a way that the traction pulley half 105b moves in the direction of the axially fixed traction pulley half 105a and as a result an axial clamping force on the traction means is increased. The other freewheel 140 is not blocked and thus enables the corresponding relative rotation of the torque transmission section 108 relative to the axially displaceably mounted traction pulley half 105 b.
In the opposite case, i. If a load torque applied to the torque transmission section 108 is greater than a torque transmissible by the traction means to the traction pulley 105, a relative rotation in the opposite direction can be effected accordingly and thus axial displacement of the axially displaceable traction pulley half 105b from the axially due to the thread 145 fixed traction pulley half 105 a, whereby the axial clamping force decreases.
In overrun, however, blocks the second freewheel 142, while the first freewheel 141 is released. In this case, a relative movement in the axial direction between the torque transmission section 108 and the freewheel 142 can be effected by means of the other thread 146 and consequently the axial displacement of the axially displaceable pulley half 105 b. In this case, an axial displacement of the traction pulley half 105b of the second pulley 105 can also be effected, which leads to an increase of the axial clamping force, if the torque transmittable by the traction means on the pulley 105 is smaller than the load torque applied to the torque transmission portion 108 and an axial displacement , which leads to a reduction of the axial clamping force when the transferable from the traction means on the Zugmittelscheibe 105 torque is greater than the voltage applied to the torque transmission portion 108 load torque.
In order to achieve the best possible distribution of the axial clamping force on both Zugmittelscheiben halves 105a and 105b of the second pulley, a pull rod 117 is provided which extends through the interior of the secondary shaft 103 designed as a hollow shaft. For damping occurring force peaks of the tie rod 117 is coupled via a biased plate spring 118 to the secondary shaft 103.
Furthermore, this exemplary embodiment of a clamping force device 140 according to the invention has a clamping force coil spring 111 which is supported on the axially displaceably mounted traction pulley half 105b and on a flange-like projection forming a type of spring plate 113 on the torque-Clbertragungsabschnitt 108, so that the axially displaceably mounted traction pulley half 105b is under prestress.
Fig. 3a shows, also in a sectional view, a detail of a second embodiment of a traction mechanism according to the invention in the region of the secondary shaft 103 with an alternative clamping force device 240 according to the invention, which additionally has a clamping force actuator 144 for generating a further clamping force share, via a ball ramp 129 with a separately formed to the torque transmission portion 208, axially displaceably mounted spring plate 213, on which the clamping force coil spring 111 is supported, is coupled such that by means of the clamping force actuator 144, an axial displacement of the spring plate 213 can be effected, in particular a Compressing the clamping force coil spring 111, and thus an additional axial clamping force portion can be generated. The torque transmission section 208 is mounted via a ball bearing 137 in the transmission housing, not shown here.
The ball ramp 129 is composed of two annular disc halves 131 and 133, between which a plurality of balls 138 are guided in a plurality of circumferentially extending grooves 132, wherein the grooves 132 have over their length in the circumferential direction a variable groove depth, wherein in the lower part of Fig. 3a identifiable groove 132 thereby aulweist in the sectional plane has a maximum groove depth, while the recognizable in the upper part of Fig. 3a groove 132 aulweist in the sectional plane has a very small groove depth.
The annular disc half 131 is mounted axially and non-rotatably in the gear housing, not shown here, while the annular disc half 133 is rotatably coupled via a ball bearing 134, but in the axial direction with the axially displaceably mounted spring plate 213 and a spur gear 130 with a correspondingly formed spur gear teeth 143 of the clamping force actuator 144 is engaged, see Fig. 3b.
To generate or for setting the additional, axial clamping force share can be applied by means of the clamping force actuator 144 via the spur gear 143 of the clamping force actuator 144 and the spur gear 130 of the ball ramp 129, a rotational movement on the ball ramp 129, with the rotational movement in an axial displacement can be converted.
The rotational movement can be applied to the rotatably mounted annular disc half 133 in this clamping force device 240, wherein the application of a rotational movement on the annular disc half 133 leads to a change in the position of the balls 138 in the circumferentially extending grooves 132, so that due to the circumferential direction variable groove depth an axial distance between the two annular disc halves 131 and 133 changes and in particular an axial displacement of the annular disc half 133 is effected.
An axial displacement of the annular disc half 133 to the left, based on this representation, together with a consequent caused axial displacement of the spring plate 213 to the left to a compression of the clamping force coil spring 111 and thus an increase in the axial clamping force, while applied by an applied in the opposite direction Rotary movement an axial displacement to the right, based on this representation, can be effected, which leads to a reduction of the axial clamping force.
3a shows a perspective view of the detail from FIG. 3a, the arrangement of the clamping force coil spring 111 and its support on the axially displaceably mounted traction pulley half 105b and the spring plate 213 being particularly well recognizable in this illustration. Also, the interaction of the clamping force actuator 144 with the ball ramp 129 via the toothing 143 of the clamping force actuator 144 and the toothing 130 of the annular disk half 133 of the ball ramp 129 can be seen particularly well.
4 shows a section of a third embodiment of a traction mechanism according to the invention in the region of the secondary shaft 103 with parts of a third embodiment of a clamping force device 340 according to the invention in a perspective view, wherein in particular the second pulley 105 and the interior of the clutches 141 and 142 are clearly visible, the coaxial to the torque transmission portion 208 are arranged.
Fig. 5 shows, also in perspective view, a further detail of the third embodiment of a traction mechanism according to the invention with the clamping force device of Fig. 4 in the region of the secondary shaft 103, said clamping force device 340 from the clamping force device 240 shown in FIGS. 3a and 3b distinguishes that the clamping force actuator 244 has no spur gear as the clamping force actuator 144, but is designed as a threaded spindle and is coupled via a thread 243 and a helical gear 230 with the ball ramp 229.
However, just as with the clamping force device 240 according to the invention described with reference to FIGS. 3 a and 3 b, the clamping force actuator 340 can also act by means of the clamping force actuator 244 via the ball ramp 229 and the axially displaceable spring plate 213 on which the clamping force coil spring 111 is supported additional axial clamping force component are applied and thus the force acting on the between the traction pulley halves 105a and 105b of the second pulley driven tension means axial clamping force can be adjusted.
FIG. 6a shows the detail from FIG. 5 in a longitudinal section along the section plane B-B, cf. Fig. 6d, with a set ratio <1, in which the individual components of the clamping force device 340 are particularly well recognized.
As with the embodiment described with reference to FIGS. 3a and 3b, in this clamping force device 340 according to the invention the torque transmission section 208 is coupled via two freewheels 141 and 142 respectively to the axially displaceably mounted traction pulley half 105b, wherein the torque transmission section 208, likewise like FIG in the above-described clamping force device 240 according to the invention, via the ball bearing 137 rotatably relative to the axially displaceably mounted traction pulley half 105b in not shown here
Gearbox is mounted. The secondary shaft 103 is mounted Uber a ball bearing 139 in the transmission housing.
The freewheels 141 and 142 are also formed in this case and coupled to the torque-Überertragungsabschnitt 208 and the axially displaceable Zugmittelscheiben half 105b of the second pulley 105, by a relative rotation between the torque-transmitting portion 208 and the axially displaceable Zugmittelscheiben half 105b of the second pulley 105, an axial displacement of the axially movable pulley half 105b is effected and consequently a change in the axial clamping force.
Likewise, only one freewheel 141 or 142 is currently blockable, i. not both at the same time, whereby in this case the freewheel 141 is provided for power transmission in train operation and the freewheel 142 for power transmission in overrun operation. The freewheels are also coupled via the threads 145 and 146, respectively, to the torque transmission section, wherein the freewheel 141 is coupled to the torque transmission section with a different thread pitch than the freewheel 142. In other words, the thread 145 points a pitch other than the thread 146, wherein on the thread pitch of a Klemmkraftgradient can be adjusted.
Also, in this clamping force device 340, a clamping force coil spring 111 is provided to apply an axial biasing force to the axially displaceably mounted traction pulley half 105b of the second pulley 105, wherein the clamping force coil spring 111 is supported in this case via an axially displaceable spring plate 213 which is coupled via a ball bearing 134 with the annular disc half 233 of the ball ramp 229, wherein on the annular disc half 233 for generating an axial displacement also by means of a clamping force actuator 244, a rotational movement can be applied. As already explained with reference to FIG. 5, in contrast to the clamping force actuator 144 of the clamping force device 240 shown in FIGS. 3 a and 3 b, the clamping force actuator 244 is in this case designed as a threaded spindle 244 with a thread 243 and the toothing 230 of the rotatable
Ring disk section 233 of the ball ramp 229 correspondingly as helical teeth and not as a spur gear toothing.
FIG. 6b shows a detail of a cross section through the clamping force device according to the invention from FIG. 6a along the sectional plane D-D according to FIG. 6a, wherein the design of the first free-wheel 141 can be clearly seen in this illustration. In this case, Fig. 6b shows the freewheel 141 in a dissolved and thus non-blocked state, i. in this state, the traction mechanism according to the invention is in overrun mode and the power transmission takes place via the second freewheel 142, see Fig. 6c.
In Fig. 6c, which shows a section of a cross section through the clamping force device according to the invention from Fig. 6a along the sectional plane CC of FIG. 6a by the second freewheel 142, it can be clearly seen that the balls of the freewheel 142 abut respectively at the edge of the grooves and thus a torque can be transmitted, ie the freewheel 142, which is provided for power transmission in overrun mode, is blocked in this state and the traction mechanism is in overrun mode.
Fig. 6d shows for better understanding the detail of Fig. 6a in a side view from the left, i. in plan view of the externally projecting end of the tie rod 117. In this illustration, in particular the formation of the clamping force actuator 244 as a threaded spindle 244 with the thread 243 can be clearly seen.
7a shows the detail from FIGS. 6a to 6d in a longitudinal section along the section plane BB, but with a set transmission ratio> 1 and a maximum axial displacement of the ball ramp 229, which is indicated by the balls 138 located between the two annular disk halves 131 and 233 should be.
In this case, the pulley half 105b is almost completely pushed against the axially fixed pulley half 105a. In order to produce a sufficient axial clamping force in this case, the two annular disc halves 131 and 233 are spread apart as far as possible.
For a better understanding analogous to FIG. 6d, FIG. 7b shows the detail from FIG. 7a in a side view from the left, likewise onto the free end of the tension rod 117, ie. 7c shows the detail from FIG. 7a in a side view from the right, wherein in FIG. 7c in particular the coupling of the threaded spindle 244 with the thread 230 of the second annular disc half 233 is clearly visible is.
1 Zugmittelgetriebe from the prior art 2 Primary 3,103 secondary shaft 4 first pulley 4a axially fixed pulley half of the first pulley 4b axially displaceably mounted pulley half of the second
Zugmittelscheibe 5,105,205 second pulley 5a, 105a axially fixed traction pulley half of the second pulley 5b, 105b, 205b axially displaceably mounted pulley half of the second
Zugmittelscheibe 6 traction means 7 actuator 6,108,208 torque transmission section 9 drive shaft with gear assembly 10 gear housing 11,111 clamping force coil spring 111a outer clamping force coil spring 111 i inner clamping force coil spring 12 Rolling 13,113,213 spring plate 14 axis of rotation of the primary shaft 15,115 axis of rotation of the secondary shaft 40 clamping force device from the prior Technique 117 Tension rod 118 Disc spring 129.229 Ball ramp 130.230 Gearing second half-disc 131 First half-disc 132 Groove with variable depth 133.233 Second half-disc 134 Rolling bearings 137 Rolling bearings 138 Ball 139 Rolling bearings 140, 240, 340 Clamping device 141 First freewheeling 142 Second freewheeling 143.243 Gearing 144.244 Clamping force Actuator 145 First freewheel thread 146 Second freewheel thread

权利要求:
Claims (14)
[1]
claims
1. A traction mechanism with an adjustable ratio for a vehicle, comprising: - a primary shaft, - arranged parallel to the primary shaft secondary shaft (103), - a first pulley, which is arranged coaxially to the primary shaft and two, each rotatably coupled to the primary shaft, in a second traction sheave (105) which is arranged coaxially to the secondary shaft (103) and consists of two, in each case rotationally fixed to the secondary shaft (103) coupled, substantially conical traction pulley halves (105a, 105b) is formed, - one the first pulley and the second pulley (105) and in each case between the Zugmittelscheiben halves (105a, 105b) of the first pulley and the second pulley (105) guided traction means for transmitting a drive power from the primary shaft to the secondary shaft (103), - whereby one of the two traction means Cheibe halves (105a) of the first pulley and / or the second pulley (105) is axially fixed and the other pulley half (105b) is axially displaceable such that a defined axial distance between the pulley halves (105a, 105b) the first Zugmittelscheibe and / or the second Zugmittelscheibe (105), in particular continuously, is adjustable to adjust an effective radius of wrap of the traction means, - an adjusting device for adjusting the axial distance between the traction pulley halves of the first pulley and / or for adjusting the axial Distance between the Zugmittelscheiben halves (105a, 105b) of the second Zugmittelscheibe (105), - a clamping force device at least for adjusting, between the two Zugmittelscheiben halves (105a, 105b) of the second Zugmittelscheibe (105) acting on the traction means, axial clamping force wherein the clamping force device is designed to be at least mechanically to generate a portion of the axial clamping force, wherein the clamping force means arranged coaxially to the secondary shaft (103), with the secondary shaft (103) coupled, an output side of the traction mechanism forming and axially fixed torque transmission section (108. 208), wherein the torque transmission section (108, 208) rotatably mounted with respect to the rotation test with the secondary shaft (103), axially displaceable Zugmittelscheiben half (105b) of the second pulley (105) is mounted and at least one coaxial to the secondary shaft ( 103) arranged freewheel (141, 142) is coupled to the axially displaceable Zugmittelscheiben half (105b) of the second pulley (105), wherein the freewheel (141, 142), formed in such a way and with the torque-transmitting portion (108, 208) and the axially displaceable Zugmittelscheiben half (105b) of the second Zugmittelscheibe (105) is coupled, that by a relative rotation between the torque transmission portion (108,208) and the axially displaceable Zugmitteischeiben half (105b) of the second Zugmittelscheibe (105) an axial displacement of axially movable pulley half (105b) is effected to change the axial clamping force.
[2]
Second traction mechanism according to claim 1, characterized in that the clamping force device is designed such that the clamping force is at least partially generated in response to a load on the torque transmission portion (108, 208) load torque.
[3]
3. traction mechanism according to claim 1 or 2, characterized in that the clamping force device, in particular the freewheel (141, 142), is designed such that a relative rotation between the torque transmission section (108, 208) and the axially displaceable pulley half ( 105b) of the second pulley (105) causes an axial displacement of the axially movable pulley half (105b) of the second pulley (105) and consequently a change in the axial clamping force when between the torque transmission portion (108, 208) and the axially displaceable Zugmitteischeiben Half occurs (105b) of the second pulley (105) slip, if the maximum transmissible by the traction gear torque is not reached, wherein slip occurs when the current rotational speed of the torque transmission section (108, 208) of the current rotational speed of the axially displaceable pulleys-H half (105b) of the second pulley (105) deviates.
[4]
4. Zugmittelgetriebe according to claim 3, characterized in that the clamping force device is designed such that a torque transmission section (108, 208) applied load torque, which is smaller than one due to the currently between the traction means and the pulley halves (105a, 105b) of the second Zugmittelscheibe (105) acting friction force currently transmissible torque, increasing the distance of the Zugmittelscheiben halves (105a, 105b) of the second Zugmittelscheibe (105) causes and thus a decrease in the clamping force, and / or such that a torque -Transmission section (108, 208) applied load torque which is greater than a torque currently transmittable due to the currently acting between the traction means and the Zugmittelscheiben halves (105a, 105b) of the second pulley (105) friction force, reducing the distance of Zugmittelscheiben- Halves (105 a, 105 b) causes the second pulley (105) and thus ei ne increase in clamping force.
[5]
5. traction mechanism according to one of the preceding claims, characterized in that the freewheel (141, 142) in the radial direction between an axially extending flange of the axially displaceable pulley half (105b) of the second pulley (105) and the torque Transmission portion (108, 208) is arranged, wherein the freewheel (141, 142) preferably via a thread (145, 146) with a defined pitch with the torque-transmitting portion (108, 208) is coupled and in particular to the axially displaceable Zugmittelscheiben half (105b) of the second Zugmittelscheibe (105) is axially fixed and rotatably connected to the axially displaceable Zugmittelscheiben half (105b) of the second pulley (105) is connected.
[6]
6. Zugmilteigetriebe according to any one of the preceding claims, characterized in that the torque transmission section (108, 208) via a first freewheel (141) and a second freewheel (142) with the axially displaceable Zugmittelscheiben half (105b) of the second pulley ( 105) is coupled, wherein preferably the first freewheel (141) is formed and coupled to the torque transmission section (108, 208) and the axially displaceable Zugmittelscheiben half (105b) of the second pulley (105) that by means of the first freewheel (141) the axial clamping force is adjustable in a traction mode of the traction mechanism and wherein preferably the second freewheel (142) formed and with the torque-transmitting portion (108, 208) and the axially displaceable Zugmittelscheiben half (105b) of the second pulley (105 ) is coupled, that by means of the second freewheel (142) set the axial clamping force in a pushing operation lbar is.
[7]
7. traction mechanism according to claim 5 and 6, characterized in that the first freewheel (141) and the second freewheel (142) respectively in the radial direction between the axially displaceable pulley half (105b) of the second pulley (105) and the torque converter Transmission portion (108, 208) are arranged, wherein the first freewheel (141) and the second freewheel (142) are preferably each coupled via a thread (145, 146) with a defined pitch with the torque-transmitting portion (108, 208) the first freewheel (141) is coupled to the torque transmission section (108. 208), in particular via a thread (145) with a different thread pitch, than the second freewheel (142).
[8]
8. traction mechanism according to one of claims 6 or 7, characterized in that the first, provided for adjusting the axial clamping force in traction freewheel (141) in the axial direction between the second, provided for adjusting the axial clamping force in overrun freewheel (142) and the axially displaceable traction pulley half (105b) of the second pulley (105) is arranged.
[9]
9. ZugmiWelgetriebe according to one of claims 5 to 8, characterized in that the clamping force device is designed such that in each case only one freewheel (141, 142) is currently blocked.
[10]
10. traction mechanism according to one of the preceding claims, characterized in that the torque transmission section (108 208) for distributing the clamping force on both Zugmittelscheiben halves (105 a, 105 b) of the second Zugmitteischeibe (105) above a pull rod (117) with the Axially fixed traction pulley half (105a) is connected, wherein preferably the secondary shaft (103) at least in the region of the second pulley (105) is a hollow shaft and the tension rod (117) within the secondary shaft (103) from the torque-transmitting portion (108, 208 ) is guided to the axially fixed traction pulley half (105a).
[11]
11. Zugmittelgetriebe according to one of the preceding claims, characterized in that the clamping force means for increasing the axial clamping force at least one coaxial with the secondary shaft (103) arranged clamping force coil spring (111), wherein the clamping force coil spring (111) under bias to the axial displaceable Zugmittelscheiben half (105b) of the second Zugmittelscheibe and preferably on a, a spring plate (113) forming, in the radially outwardly extending flange of the torque-transmitting portion (108) is supported.
[12]
12. Zugmittelgetriebe according to any one of the preceding claims, characterized in that the clamping force device has a clamping force actuator (144, 244) and is adapted by means of the clamping force actuator (144, 244) in addition to, in dependence on the torque Transferring portion (208) applied load torque applied clamping force share a further, axial clamping force share on the second pulley (105), wherein the clamping force actuator (144, 244) is preferably mechanically coupled to the clamping force coil spring (111), in that the clamping force coil spring (111) is compressible for applying an additional clamping force component with the aid of the clamping force actuator (144, 244), the clamping force coil spring (111) preferably being disposed above a torque transmission section (209). axially displaceable spring plate (213) is supported.
[13]
13. Zugmittelgetriebe according to claim 12, characterized in that the clamping force means for applying the clamping force actuator (144, 244) generated, further, axial clamping force share on the second pulley a coaxial with the secondary shaft (103) arranged ball ramp (129, 229 ), wherein the clamping force actuator (144, 244) preferably via a toothing (143, 243, 130, 230) with the ball ramp (129, 229) is coupled and the ball ramp (129, 229) with the clamping force coil spring (111), wherein the clamping force actuator (144,244) is in particular an electric motor.
[14]
14. Vehicle with a traction mechanism with continuously variable transmission, characterized in that the traction mechanism according to one of claims 1 to 13 is formed.

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同族专利:

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公开号 | 公开日

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AT516841B1|2016-09-15|

引用文献:

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公开号 | 申请日 | 公开日 | 申请人 | 专利标题

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US5057061A|1988-12-30|1991-10-15|Aisin Aw Kabushiki Kaisha|Continuously variable speed transmission|

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DE10139121A1|2000-09-08|2002-03-21|Luk Lamellen & Kupplungsbau|Pressure system especially for continuous gearbox, generates force on output side dependent on input torque, has at least one conversion device that converts or gears the torque and/or force|DE102017114178A1|2017-06-27|2018-12-27|Schaeffler Technologies AG & Co. KG|Actuator arrangement for changing a transmission ratio of a continuously variable transmission|

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法律状态:
2017-08-15| HA| Change or addition of new inventor|Inventor name: JOZEF VERMEULEN, AU Effective date: 20170619 Inventor name: ADAM WARBURTON, AU Effective date: 20170619 |

优先权:

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申请号 | 申请日 | 专利标题

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ATA449/2015A|AT516841B1|2015-07-09|2015-07-09|Traction mechanism with infinitely adjustable transmission|ATA449/2015A| AT516841B1|2015-07-09|2015-07-09|Traction mechanism with infinitely adjustable transmission|