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 Zugmittelscheiben halves (105a) is axially fixed and the other Zugmittelscheiben half (105b) is axially displaceable such that an axial distance between the Zugmittelscheiben halves (105a, 105b) is infinitely adjustable and thus a translation of flexible drive. For setting an on the traction means (1 06) acting axial clamping force is a clamping force device (140) is provided which has a coaxial with the secondary shaft (103) arranged torque-transmitting portion (108) formed and with the secondary shaft (103) and the axially displaceable traction pulley half (105b) of the second pulley (105) is coupled, that by a relative rotation between the torque transmission portion (108) and the axially displaceable pulley half (1 05b) of the second pulley (105) an axial displacement of the axially displaceable Zugmittelscheiben half (105b) is effected.
公开号:AT517594A4
申请号:T447/2015
申请日:2015-07-09
公开日:2017-03-15
发明作者:Vermeulen Jozef
申请人:Avl List Gmbh；
IPC主号:

专利说明:

Zugmittelgetriebe with stages los adjustable translation
The invention relates to a traction mechanism with continuously variable transmission for a vehicle, especially for a quad, skidoo or the like.
Steplessly adjustable 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 KGO van de Meerakker, PCJN Rosielle, B. Bonson and TWGL Klaassen from the Technical University of Eindhoven.
Such Zugmittelgetriebe with infinitely adjustable translation generally have a drive shaft of the traction mechanism forming primary shaft, a parallel to the primary shaft arranged, usually the output shaft of the Zugmitteigetriebes forming 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 Zugmittelscheiben wrap around traction means, which is provided for transmitting a drive power from the primary shaft to the secondary shaft. The first Zugmittei and the second Zugmittelscheibe are usually formed in each case two, substantially conical Zugmittelscheiben 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 pulley half so axially displaceable within certain limits, that in each case a defined axial distance between the traction pulley halves of the first pulley and between the Zugmlttelscheiben halves of the second Zugmittelscheibe is infinitely adjustable, so that by adjusting the axial distance of the traction pulley halves of the first pulley and the second pulley each a defined effective Umschlingungsradius the traction means is continuously adjustable and thus a defined translation of Zugmiltelgetriebes.
For adjusting or adjusting the axial distance between the traction pulley halves of the first pulley and / or the Zugmlttelscheiben halves of the second pulley generic gen Zugmittelgetriebe usually have a suitably trained adjusting device, being from the prior art Zugmilteigetriebe with different Stellkonzepten and different
Actuators are known.
In addition to an adjusting device for adjusting or adjusting the axial distance between the traction pulley halves of Zugmittelscheiben have generic
Zugmittelgetriebe also often additionally additionally a clamping force device for adjusting a on the guided between the two Zugmlttelscheiben halves of Zugmittelscheibe traction means axially acting clamping force, preferably to adjust a force acting between the traction means and the pulley halves of the second pulley friction force, so that a desired torque or ., a desired Antriebsielstung 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 pulley hooks, in particular clamping force devices with which an axial clamping force is achieved at an axial distance between the traction pulley 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 can be adjusted independently of the set axial distance between the traction pulley halves of the first and the second pulley.
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 one, by the company Jatco for the scooter Suzuki Burgman developed, slollably adjustable Zugmittelgelriebe. 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 example, a kind of cam control for self-controlled mechanical generation of the axial Klemmkrait, wherein the cam control is formed by the axially displaceably mounted Zugmittelschelben 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 veschiebbaren pulley half against the secondary shaft is triggered, which by means of Cam control to an axial displacement of the axially displaceable Zugmittelscheiben-half of the second Zugmilteischeibe leads 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.
An object of the present invention is to provide an alternative traction mechanism with continuously variable transmission for a vehicle, in particular for a quad, skidoo or the like, 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 15, Preferred embodiments 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.
An inventive traction mechanism is provided for a vehicle, in particular for a quad, skidoo or the like and allows a continuous adjustment of the translation.
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 infinitely variable transmission means a traction mechanism in which the transmission is steplessly adjustable at least in a certain range, for example in a certain 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 Krattübertragungseiement 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.
The traction mechanism according to the invention has a Primärwelie, arranged parallel to the primary shaft secondary shaft, a first pulley and a second pulley, wherein the first pulley is coaxial with the primary shaft and formed of two, each rotatably coupled to the primary shaft, substantially conical pulley halves formed is, and wherein the second Zugmittelscheibe is arranged coaxially to the secondary shaft and of two, each rotatably coupled to the secondary shaft, also formed substantially conical pulley half halves.
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
A coaxial arrangement of two components relative to each other is understood in the sense of the invention to mean an arrangement in which the components are arranged relative to one another in such a way that their axes of rotation coincide.
A traction pulley 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 context of the invention, a non-rotatable coupling is understood as meaning a coupling or an operative connection which is designed in such a way that the components jointly follow a rotational movement, i. 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, preferably the first traction pulley and the second traction pulley are looped by a traction device guided between the traction pulley halves of the first traction pulley and between the traction sheave halves of the second traction sheave, the traction means transmitting a drive power from the primary shaft to the traction sheave 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 from the primary shaft to the traction means by means of the first traction pulley and from the traction means by the second traction shifter to the secondary shaft.
One of the two pulley halves of the first pulley and / or the second Zugmittelschelbe is preferably axially fixed in the Zugmittelgetriebe invention and the other Zugmittelscheiben half axially displaceable within certain limits such 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 Zugmlttelscheiben halves each lead 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 Elnsteilen an axial, acting between the two Zugmittelscheiben halves of the second Zugmilteischeibe on the traction means clamping force, wherein the clamping force means is adapted to mechanically generate at least a portion of the force acting on the traction means clamping force, i. without an additional clamping force actuator.
In an advantageous embodiment of the traction mechanism according to the invention, the clamping force device is also designed for setting an axial, acting between the two Zugmittelscheiben halves of the first Zugmlttelscheibe on the traction means clamping force, preferably also such that at least a portion of the force acting on the traction means clamping force can be generated mechanically ,
According to the invention, the clamping force device for generating the mechanical clamping force component between the two traction pulley halves of the second
Zugmitteibeibe preferably arranged coaxially to the secondary shaft, coupled to the secondary shaft, an output side of the Zugmittelgetriebes forming and axially fixed torque transmission section which is rotatably mounted relative to the rotatably coupled to the secondary shaft, axially displaceable Zugmittelscheiben half of the second pulley and so formed and is coupled to the axially displaceable traction pulley half of the second pulley, that by a relative rotation between the torque transmission section and the axially movable pulley half of the second pulley axial displacement of the axially movable pulley half can be effected and consequently a change in the axial clamping force.
In other words, in the ZugmiUelgetriebe invention for generating an axial clamping force, a relative rotation between the torque transmitting portion and the axially displaceably mounted Zugmittelscheiben half of the second Zugmittelscheibe effected by which the axially displaceably mounted traction pulley half of the second Zugmittelscheibe be moved axially can, 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 Sekundärwelie. As a result, purely mechanically and thus in a simple manner an axial clamping force generating Reiativdrehung between the torque transmission portion and the axially displaceable Zugmittelscheiben half of the second pulley can be effected, for example, by an applied to the torque transmission section and adjacent to one of the secondary shaft 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.
Another advantage of the traction mechanism according to the invention is further that by the inventive coupling of the torque transmission section with the axially displaceably mounted traction pulley half of the second pulley and the secondary shaft and by the rotationally fixed coupling of the traction pulley halves of the second pulley with the Sekundärwelie a 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, loads acting on the traction means, which would arise as a result of a relative rotation of the axially fixed traction pulley half and the axially displaceably mounted traction pulley half and which are particularly unfavorable for steel belts as traction means, can be avoided so that a traction mechanism according to the invention is also suitable for use of metallic traction means, in particular for the use of steel belts as traction means, is suitable.
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 coordinated 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 Klemmkrafteinrichlung and thus the traction mechanism is possible, whereby a cost-effective traction mechanism can be provided.
An inventive Zugmittelgelriebe is thus particularly suitable for vehicles in which only small torques are to be transmitted from the primary shaft to the secondary shaft, i. where only a small axial clamping force is needed to generate the required frictional force, such as in quads. Skidoos, scooters or the like.
The torque transmission 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 to the secondary shaft.
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 traction pulley half of the second pulley and thus only within certain limits in the circumferential direction brehbeweglich opposite the Sekundärweile, 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 transmission portion and the rotatably coupled to the secondary shaft, axially displaceably mounted traction pulley half of the second pulley is permissible is.
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. That is, 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 transferable drive power, in particular a maximum transmissible torque depends directly on the axially acting on the traction means clamping force, which of the two Zugmittelschelben -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 Zugmittelschelbe and the second Zugmittelschelbe is formed such that the axial distance of the traction pulley halves of the second pulley as a function of the axial distance of Zugmittelscheiben- Adjusting halves of the first pulley, wherein preferably the axial distance of the traction pulley halves of the second pulley decreases when the axial distance of the pulley halves of the first pulley increases and vice versa.
In a further advantageous embodiment of Zugmitteigetriebes invention the Klemmkrafteinrichlung is formed such that the axial clamping force is at least partially generated in response to a torque applied to the Drehmomentabschnitl load torque, i. depending on a voltage applied to the output side of the traction mechanism 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.
In a further advantageous embodiment of the Zugmilteigetriebes invention, the clamping force device is designed such that a relative rotation between the torque transmission section and the axially displaceable Zugmittelscheiben half of the second Zugmittelscheibe an axial displacement of. Axially displaceable Zugmittelscheiben half of the second pulley and as a result a change in causes axial clamping force when slip occurs between the torque-transmitting portion and the axially displaceable Zugmittelscheiben half of the second pulley center slip. if the maximum transmissible by the traction mechanism torque is not reached yet.
Slip according to the invention occurs when the current rotational speed of the torque transmission section deviates from the current rotational speed of the axially displaceable Zugmittelscheiben half of the second Zugmittelscheibe, for example, if the rotational speed of the torque transmission section is greater than the rotational speed of the torque transmission section due to the applied load torque Axially displaceably mounted traction pulley half of the second pulley or when the rotational speed of the axially displaceable Zugmittelscheiben half is greater than the rotational speed of the torque transmission section, for example, as a result of a torque applied to the secondary shaft torque torque.
In a further advantageous embodiment 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 pulley halves of the second Zugmitteische Reibkraft currently from the traction means to the second Zugmittelscheibe transmissible torque, an increase in the distance of the traction pulley halves of the second pulley and thus causes a decrease in the axial clamping force, and / or such that a voltage applied to the torque transmission section load torque, which is greater than one due to the currently between the traction means and Friction force currently acting on the traction means halves of the second traction sheave wheel torque currently transmittable from the traction means to the second traction sheave, a reduction of the distance of the
ZugmlUelscheiben halves of the second Zugmittelschelbe causes and thus an increase in the axial clamping force.
In other words, the clamping force device is preferably designed such that the axial clamping force, which adjoins, is at least so large that the torque applied to the torque transmission section load torque can be transmitted from the traction means to the second pulley, and thus to the secondary shaft.
In particular, the clamping force device is designed such that the axial Kiemmkraft that is einelit, just so large that the voltage applied to the torque transmission section load torque can be transmitted from the traction means to the second Zugmilteischibe. As a result, a wear-promoting Überanpressung can be avoided. This can for example be achieved by the clamping force device is designed such that between the torque-transmitting portion and the axially displaceably mounted
Traction pulley half of the second pulley no slip occurs more and thus no more relative rotation when the transferable from the traction means on the second pulley and the secondary whip torque and the voltage applied to the torque transmission section load torque on the output side are the same, in particular the same size and rectified.
In a further advantageous embodiment of the traction mechanism according to the invention, the torque transmission section forms with the axially movable traction pulley half of the second pulley a kind of cam control, the clamping force device preferably has a control cam and a control surface along which the control cam for adjusting the axial distance between the Traction pulley halves of the second pulley can be performed.
Preferably, at least one projection is provided as a control cam on the axially displaceable Zugmittelscheiben half of the second pulley and preferably, the torque-transmitting portion has at least one thread-like, at least over a portion of the circumference with a defined slope extending ramp as a control surface.
In particular, at least one projection of the axially displaceable traction pulley half of the second pulley can be brought into engagement with at least one ramp of the torque transmission section by a relative rotation of the torque transmission section relative to the axially movable pulley half of the second Zugmittelschelbe such that in another Relative rotation of the torque-transmitting portion of the projection slides on the ramp or is guided along, so that as a result of the slope of the ramp, an axial displacement of the axially displaceable Zugmittelscheiben-half of the second Zugmittelschelbe is effected. The size of the generated axial clamping force results in dependence on the slope of the ramp and a relative angle of rotation between the torque-transmitting portion and the axially displaceable traction pulley half of the second pulley.
In other words, in an advantageous embodiment of the traction mechanism according to the invention on the axially displaceable traction pulley half of the second pulley at least one projection provided as a control cam and the torque transmission section extending in the circumferential direction with a defined slope ramp as a control surface on which the projection along can, wherein a relative rotation of the torque transmission direction relative to the axially displaceably mounted traction pulley half of the second Zugmittelschelbe causes a slipping of the projection on the ramp of the torque transmission section, and wherein the ramp is formed such that a relative rotation of the torque transmission section relative to the axially displaceable Zugmittelscheiben half of the second Zugmittelscheibe an axial displacement of this is effected and consequently the generation of an axial clamping force.
Preferably, the ramp forming the control surface can also be provided on the axially displaceable traction mechanism pulley half of the second pulley and the projection forming the control cam correspondingly on the torque transmission section.
In a further advantageous embodiment of the traction mechanism according to the invention, the clamping force device, in particular in addition, a damping device. In this case, the damping device preferably has a coaxially arranged to the secondary shaft damping sleeve and at least one, with its longitudinal axis parallel to the secondary shaft under tension, on the axially displaceable pulley half of the second pulley and preferably on an inner surface of the damping sleeve supported damping spring.
The damping sleeve is preferably rotatably coupled to the axially displaceable traction pulley half of the second pulley and extends in the axial direction preferably at least partially over an engagement region in which the ramp of the torque transmission section with the projection of the axially displaceable pulley half of the second Zugmittelscheibe can be brought into engagement. By such a damping device occurring Axialkraftschwankungen and thus occurring fluctuations in the axial clamping force can be effectively damped, so that sudden clamping force fluctuations and thus sudden occurrence of slip can be reduced or even avoided altogether, creating a better transmission of the drive power, in particular a more uniform torque Transmission can be achieved.
In a further advantageous embodiment of the traction mechanism according to the invention, the torque-transmitting section at least two thread-like, at least over part of the circumference with a defined slope extending ramps with different pitch, preferably a ramp for adjusting an axial clamping force in the train operation is provided and a ramp to Setting an axial clamping force in overrun mode.
In the context of the invention, the term traction mode describes a driving state in which the traction mechanism according to the invention is driven from the drive side, i. is held in rotational motion by means of the drive power applied to the primary shaft, while the term coasting operation in the sense of the invention describes a driving state in which the traction mechanism according to the invention is driven from the power take-off side, i.e. About the DrehmomentObertragungsabschnitt applied load torque is kept in rotational motion.
In a further advantageous embodiment of a Zugmitteigetriebes invention, the damping sleeve, preferably on its inner surface or on one of its inner surfaces, also on a projection, i. also a kind of control cam, this projection can be brought in particular with a arranged on the torque transmission portion, threaded, extending in the circumferential direction with a defined slope ramp such that during a relative rotation of the torque transmission section relative to the axially movable pulley half the second Zugmiltelscheibe and thus relative to the damping sleeve of the projection of the damping sleeve slides on the ramp of the torque transmission section and is guided, whereby due to the slope of the ramp on the torque transmission section, an axial displacement of the axially movable pulley half of the second Zugmiltelscheibe can be effected.
In other words, the traction mechanism according to the invention in a further advantageous embodiment with a damping device preferably not only a first cam control, which is formed by a cooperating with the ramp of the torque transmission portion projection of the axially displaceably mounted traction pulley half of the second pulley, but In particular, a further cam control, which is formed by a arranged on the damping sleeve projection and another, arranged on the torque transmission portion ramp.
The projection in the damping sleeve can be formed integrally with the damping sleeve, as well as by a separate, fixedly connected to the damping sleeve additional component. Of course, it is also conceivable to provide in the damping sleeve a corresponding control surface in the form of a preferably formed over a portion of the circumference with a defined slope slope and form the projection corresponding to the torque transmission section.
In a further advantageous embodiment of the traction mechanism according to the invention, the ramp of the torque transmission section, which is provided for adjusting the clamping force in the train operation, with the projection of the axially displaceable Zugmittelscheiben half of the second pulley engageable and the ramp of the torque transmission section, i. the second control surface, which is provided for adjusting the clamping force in the overrun mode, with the projection of the damping sleeve. That is, the projection of the axially displaceable Zugmittelscheiben half preferably slides on a first ramp, while the projection arranged in the damping sleeve can preferably slide on another ramp. As a result, a quick change between train operation and overrun operation can be made possible due to only a small, required relative rotation, in particular can be switched between train operation and overrun mH little occurring slip, as required for the elimination of the slip axial clamping force sets faster. In a further advantageous embodiment of the traction mechanism according to the invention, the torque transmission section for distributing the generated axial clamping force on both Zugmitteiiben halves of the second pulley is connected via a pull rod with the axially fixed traction pulley half, said to the secondary shaft preferably at least in the region of the second pulley a hollow shaft is and the tension rod is guided in particular within the secondary shaft from the torque transmission section to the axially fixed traction pulley half.
A tension rod In the context of the invention, this is a rod-shaped component with which tensile forces can be transmitted between the components connected to this component.
With the aid of such a tension rod, a very precise adjustment of the required axial clamping force is possible, as a result of which an overpressure associated with increased wear can be largely avoided. In a development of the traction mechanism according to the invention, the tension rod is axially coupled via a friction disk and / or a disk spring to the torque transmission section. As a result, even more even force transmission can be achieved, in particular force peaks can be filtered out. In particular, this can be used to set an advantageous hysteresis of the axial clamping force when switching from pushing operation to traction operation and vice versa.
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 pretension on the axially displaceable pulley half of the second Zugmilteischeibe and in particular on a rotationally fixed is supported to the axially displaceable traction pulley half of the second pulley disc arranged spring plate is. 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 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 applied in response to the torque transmission section load torque clamping force component another, axial clamping force Antell preferably applied to the second traction pulley, wherein the clamping force actuator is preferably mechanically coupled to the clamping force coil spring such that the clamping force coil spring for applying an additional clamping force share using the clamping force actuator can be compressed. For this purpose, the clamping force actuator is preferably coupled to the spring plate on which the clamping force coil spring is supported.
In a further advantageous embodiment of the traction mechanism according to the invention, the clamping force means for applying the generated by the clamping force actuator, further axial Klemmkraftanteils on the second Zugmittelschefbe arranged coaxially to the secondary shaft ball ramp, wherein the clamping force actuator is preferably coupled via a toothing with the ball ramp and over the ball ramp with the
Clamping force coil spring. In this case, the clamping force actuator is in particular an electric motor.
Of course, the actuator may also be a hydraulic motor and / or be coupled via a gear and / or a gear with the ball ramp.
Preferably, the axial force generated in this way can be transmitted from the ball ramp via a thrust bearing and an actuator plate on the spring plate, with which the clamping force coil spring is supported.
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
Flg. 1 is a sectional view of a known from the prior art traction mechanism with continuously adjustable ratio,
2a shows a section of a first embodiment of a traction mechanism according to the invention in the region of the secondary shaft in traction operation with a set transmission ratio <11n plan view,
2b shows the detail from FIG. 2a in a view from below, FIG.
3a shows the detail of FIGS. 2a and 2b in traction, likewise in plan view, but with a set transmission ratio> 1,
3b shows the detail from FIGS. 2a, 2b and 3a, likewise as in FIG. 3a in plan view and with a set transmission ratio> 1, but in overrun mode,
4a is a perspective view of a section of a second embodiment of a traction mechanism according to the invention in the region of the secondary shaft in traction with a set transmission ratio> 1,
4b shows the detail from FIG. 4a in a sectional view,
5 shows the detail of FIGS. 4a and 4b in exploded view,
6 is a perspective view of a section of a third embodiment of a traction mechanism according to the invention in the region of the secondary shaft with a set transmission ratio> 1,
7 shows the detail of FIG. 6 in exploded view,
8a shows the detail of FIGS. 6 and 7 in plan view with a set transmission ratio> 1 in traction,
8b, the detail from FIGS. 6, 7 and 8a, also with a set transmission ratio> 1, but in overrun mode,
9a, the detail from FIGS. 6, 7, 8a and 8b, however, with a set ratio with a transmission ratio <1 in overrun mode,
9b shows the detail from FIGS. 6, 7, 8a, 8b and 9a with a set transmission ratio <1, but in traction mode and without depiction of the damping device, FIG.
10, a section of a fourth embodiment of a traction mechanism according to the invention in the region of the secondary shaft in Schnittdarsteliung with a set transmission ratio> 1 and
11 shows a detail of a fifth exemplary embodiment of a traction mechanism according to the invention in the region of the secondary shaft in a perspective section with an exploded view of the ball ramp with a set transmission ratio> 1.
In Fig. 1 by way of example a generic, known from the prior art traction mechanism 1 with slufenlos adjustable translation is shown in Schnittdarsteliung 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 mounted in each case about not here bezelchnete 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.
Coaxial with the secondary shaft 3 is a second pulley 5 is arranged, which is also formed of two substantially cone-shaped Zugmittelscheiben halves 5a and 5b, wherein also in this pulley 5, the conical surfaces of the two Zugmittelscheiben halves 5a and 5b are arranged such that they facing each other.
In this example shown a generic Zugmittelgetriebes 1 with continuously adjustable ratio, the two Zugmittelscheiben halves 4a and 4b of the first Zugmlttelscheibe 4 and the two Zugmittelscheiben halves 5a and 5b of the second Zugmittelscheibe 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 Kunstsloff flat belt, the ends of which 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 Zugmitlelgetriebes 1, from there via the first Zugmilteischeibe 4 on the traction means 6 via a drive shaft 9 to which a gear assembly is flanged, which is also unspecified here. 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 β, which is coupled to the secondary shaft in a rotationally fixed manner, 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 pulley halves 4a and 5a thereto are formed integrally with the associated shaft, i. with the primary shaft 2 and the secondary shaft. 3
The other Zugmlttelscheiben half 4b and 5b is usually axially displaceably mounted in such a generic Zugmittelgetriebe that in each case a defined axial distance between the pulley halves 4a and 4b of the first pulley 4 and between the pulley halves 5a and 5b of second Zugmittelscheibe 5 can be adjusted without slippage 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
Oie 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 displaceably mounted pulley hubs 5a and 5b is of course constant in the circumferential direction over the entire circumference of a pulley hubs, i. Of course, the traction pulley hubs 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 shafts 4b, wherein the electric motor 7 is operatively connected to the axially displaceably mounted traction pulleys 4b that by means of the adjusting Actuator 7 an axial displacement of the axially displaceably mounted traction pulley hubs 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 sheaves 4b mounted in an axially displaceable manner can be detected and adjusted.
The axially displaceably mounted traction pulley shafts 4b has for this purpose a sleeve-shaped, unspecified portion which is arranged coaxially to the primary shaft 2 around this outside and with which the axially displaceably mounted traction pulley shafts 4b rotatably coupled to the primary shaft 2. About a ball bearing 12 is mounted on this sleeve-shaped portion of the axially displaceable
Zugmittelschelben half 4b a gear axially fixed, but rotatably mounted relative to the axially displaceably mounted Zugmittelschelben 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 the traction means 6 moves further inwards, i. 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, respectively 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 second 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 Zugmittelschelbe 4, in the embodiment shown due to the thereby 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 to 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 axiaie 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 traction pulley halves 5a and 5b of the second Zugmitteischeibe 5 in addition to the set by the set distance between the pulley halves 4a and 4b and 5a and 5b respectively adjusting, axial Kiemmkraft 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. Here, the clamping force coil spring 11 is truncated 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 Klemmkraft-
Coil spring 11 and the other of the current axial distance between the traction 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 traction pulley 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 pulley halves of the first pulley and / or the second pulley is also axially fixed in the Zugmittelgelriebe invention and the other pulley half axially within certain limits axially displaceable, 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 actuating 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 desired, 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 can be applied to the second traction pulley, wherein in particular a clamping force component is generated mechanically in a self-controlled manner can.
The components 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 FIGS. 2a and 2b, which show a section of a first exemplary embodiment of a traction mechanism according to the invention for a vehicle with infinitely variable transmission in the region of the secondary shaft 103 with a set transmission ratio <1 with a smallest possible, by means of the clamping force device 140 according to the invention additionally generated axial clamping force.
As described above, a traction mechanism according to the invention, and thus also this embodiment, a second traction pulley 105 arranged coaxially to a secondary 103, which is formed of two respectively substantially conical traction pulley halves 105a and 105b, which rotates about a rotation axis 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 also wrapped by a guided respectively between the pulley halves 105a and 105b of the second pulley 105 traction means 106 in the form of a plastic flat belt, which is clearly visible in Fig. 2a, wherein the traction means 106 for transmitting the Drive power is provided from the primary shaft, not shown, to the secondary shaft 103.
In this embodiment, the in Flg. 2a right traction pulley half 105a axially fixed and the left pulley half 105a axially slidably mounted so 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 106 steplessly can be adjusted and thus a defined translation of the traction mechanism according to the invention.
According to the invention, the axially displaceably mounted Zugmittelscheiben half 105b is rotatably coupled to the secondary shaft 103, wherein in this embodiment, the rotationally fixed coupling with the secondary shaft 103 is realized by three circumferentially distributed connectors 116 which are each rotatably connected to the secondary shaft 103 and Over the circumference each have a radially outwardly extending projection which is guided in each case by a kind of elongated hole in the axially displaceably mounted Zugmittelscheiben half 105b, so that the axially displaceably mounted traction pulley half 105b rotatably connected to the secondary shaft 103 is, but remains axially displaceable.
Furthermore, the clamping force device 140 according to the invention has a torque transmission section 108 arranged coaxially with the secondary shaft 103 and rotationally movable relative to the secondary shaft 103. which forms an output side of the traction mechanism according to the invention and is provided for discharging the drive power from the traction mechanism and, for example, can be coupled to an output shaft of a vehicle. The torque transmission section 108 is coupled by means of a kind of cam control with the axially displaceable Zugmittelscheiben half 105b of the second Zugmittelscheibe 105, wherein the cam control is designed such that by a Relalivdrehung between the torque transmission section 108 and the axially displaceable Zugmittelscheiben half 105b 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 cam control is formed by a plurality of finger-like projections 120 which are arranged on the axially displaceable traction pulley half 105b and which each form a kind of control cam, in connection with a plurality of ramps 121 arranged on the torque transmission section 108 in the circumferential direction, each with a defined pitch. which each form a kind of control surface on which the projections 120 of the axially displaceably mounted traction pulley half 105b can slide on a relative rotation between the torque transmission section 108 and the axially displaceable pulley half 105b of the second pulley 105 and be guided, whereby an axial displacement of the axially movable Zugmittelscheiben half is effected 105b and consequently a change in the axial clamping force on the structural design of the ramps 121. In particular their slope, the change of the axial clamping force in Dependent on the rotation angle of the relative rotation can be adjusted.
Characterized in that the torque-transmitting portion 108 is rotatably supported relative to the secondary shaft 103, while the axially displaceably mounted Zugmitteischeiben half 105b is rotatably connected to the secondary shaft 103, can in a simple way and catfish through between the torque transmission section 108 and the Zugmittelscheiben- Half 105b occurring slip, ie by an occurring difference in the rotational speeds of the torque transmission section 108 and the traction pulley half 105b, which is required to generate the relative rotation between the torque transmission section 108 and the axially displaceably mounted traction pulley half 105b required for axial displacement of the axially displaceably mounted traction pulley half 105b be relieved.
Slippage between the torque transmission section and the Zugmittelscheiben half 105b occurs, for example, when an acting on the traction means 106 axial clamping force between the Zugmlttelscheiben halves 105a and 105b is not sufficient to a sufficient frictional force between the traction means 106 and the Zugmittelscheiben halves 105a and 105b, so that only a smaller torque can be transmitted to traction sheave 105 by traction means 106 than a load torque applied to torque transmitting portion 108 or if torque transmitted from traction means 106 to second traction shifter 105 is greater than that at the torque transmitting portion 108 is applied load torque.
In the former case, a relative rotation between the torque transmission section 108 and the Zugmittelscheiben half 105 b is caused by the applied torque difference, in which the projection 120 of the axially displaceably mounted Zugmittelscheiben half 105 b Slides each on one of the ramps 121, whereby the axially displaceable traction pulley half 105b is moved in the direction of the other pulley half 105a and consequently increases the axial clamping force, in particular so far until the transferable from the traction means 106 to the second pulley 105 torque corresponds to the load torque or a maximum axial displacement of the axial displaceable Zugmittelscheiben half 105b is reached for the set axial distance between the Zugmittelscheiben halves 105a and 105b of the second pulley 105th
In the second case, i. If the torque transmitted by the traction means 106 to the second pulley 105 is greater than the load torque applied to the torque transmission section 108, a relative rotation is effected by the torque difference or slip occurring as a result, in which the projection 120 of the axially displaceably mounted Traction pulley half 105b each slide down on one of the ramps 121, whereby the axially displaceable Zugmittelscheiben half 105b is shifted away from the other Zugmittelscheiben half 105a and consequently reduces the axial clamping force, in particular so far, that from the traction means 106 to the second Zugmittelscheibe 105 transmissible torque corresponds to the Lastmomenl or reaches a maximum possible axial displacement of the axially displaceable Zugmittelscheiben half 105b is for the set axial distance between the Zugmitlelscheiben halves 105a and 105b of the second pulley 105, As in the state shown in Figs. 2a and 2b, in this state, the projections 120 are respectively at the lowest point of the ramps 121, i. The traction pulley halves 105a and 105b are as far as possible by means of the clamping force device 140 according to the invention possible away from each other. Thus, an additional axial clamping force generated by means of the clamping force device 140 according to the invention is minimal.
When the traction mechanism according to the invention is in the traction mode, the projections 120 slide in each case on the lower ramps 121, i. on the respective lower part of the V-shaped ramps 121, up or down, while the projections 120 slide in the overrun mode due to the opposite direction of rotation of the relative rotation respectively on the upper ramps 120 along.
The above-described sliding along the projections 120 on the respective lower ramps 121 in the pulling operation can be clearly seen in Fig. 3a, which shows the detail of Figs. 2a and 2b, but with a set transmission ratio> 1, while in Fig. 3b, the detail from Fig. 3a is shown for comparison in overrun mode.
In the states shown in FIGS. 3a and 3b, the projections 120 are in each case almost at the highest point of the ramps 121, i. the traction pulley halves 105a and 105b are almost as far as possible by means of the clamping force device 140 according to the invention, pushed together. Thus, the additionally generated axial clamping force by means of the clamping force device 140 according to the invention is almost maximum, i. by a further relative rotation only a small increase of the axial clamping force can be effected.
With the above-described Ausführungsbeispie) a clamping force device 140 according to the invention can thus be generated mechanically in a simple manner, the axial clamping force both in traction and overrun in response to a voltage applied to the torque transmission section 108 load torque, in particular self-controlled.
FIG. 4a shows a perspective view of a section of a second embodiment of a traction mechanism according to the invention with an alternative clamping force device 240 according to the invention in the area of rotation about the rotation axis 115
Secondary shaft 103 in traction with a set transmission ratio> 1, this second embodiment of a tension mechanism according to the invention also has a second pulley 105 which is formed of two cone-shaped traction pulley halves 105a and 105b between which a plastic belt is guided as traction means. The pulley half 105a is also integral with the secondary shaft 103, as in the previous embodiment described above, i. rotatably with this and axially fixed to this, while the second Zugmittelscheiben half 105b is axially displaceably mounted on the secondary shaft 103 and by means of the connecting pieces 116 rotatably coupled thereto. Also, as in the previously shown embodiment, a rotationally movable with respect to the secondary shaft 103 mounted torque transmission portion 108 is provided, which is also arranged coaxially to the secondary shaft 103. The torque-transmitting section 108 also has a sleeve-shaped region with which it is virtually inverted over one end of the secondary shaft 103.
In order to achieve the best possible distribution of the axial clamping force on both Zugmittelscheiben halves 105a and 105b, the torque-Überertragungsabschnitt 108 is in this embodiment of a Zugmitteigetriebes invention or in this Klemmkralteinrichtung invention 240 Uber a relation to the secondary shaft 103 axially fixed tension rod 117 with the Zugmittelscheiben half 105 a coupled, the tension rod 117 dabai inside is passed through the formed as a hollow shaft secondary shaft 103 and is connected by means of corresponding retaining rings 122, 125 and a spacer 124 with the secondary shaft 103 and the torque transmission section 108.
To dampen occurring force peaks, which can occur in particular when changing from traction to overrun, the tension rod 117 is further connected via a friction plate 119 and a prestressed plate spring 118 to the torque transmission section 108, which is particularly evident in Fig. 4b For a possible low-friction guidance of the tension rod 117 within the torque transmission section 108, a bearing bush 123 is provided for a space-saving storage instead of a corresponding rolling bearing.
Furthermore, this clamping force device 240 has a clamping force coil spring 111 for applying a prestressed additional axial clamping force component, which is stiffened on the axially displaceably mounted traction pulley half 105b and on a spring plate 113, the spring plate 113 in this exemplary embodiment Clamping device 240 is axially fixed to the non-rotatably connected to the secondary shaft 103 connecting pieces 116, so that the spring plate 113 a rotational movement of the secondary shaft 103 and thus a rotational movement of the axially displaceably mounted traction pulley half 105b follows. As a result, relative rotation between the clamping force coil spring 111 and the axially displaceably mounted traction pulley half 105 b or the spring plate 113, which promotes wear and is associated with friction, can be avoided.
In FIG. 5, the detail from FIGS. 4a and 4b is additionally shown in an exploded view for better understanding.
Fig. 6 shows a perspective view of a section of a third embodiment of a traction mechanism according to the invention in the region of the secondary shaft 103 with a set ratio> 1 with a third embodiment of a clamping force device 340 according to the invention, wherein in this clamping force device 340 in addition to the reference to FIGS. 4a, 4b and 5 described damping device is provided with a coaxial with the secondary shaft 103 arranged damping sleeve 126 and a plurality of circumferentially distributed, disposed within the damping sleeve 126, parallel to the rotation axis 115 extending damping springs 127th
The damping springs 127 are supported on the axially displaceably mounted traction pulley half 205b and on the damping sleeve 126. For this purpose, the axially displaceable traction pulley half 205b for guiding the damping springs 127 has a plurality of grooves distributed in the circumferential direction, which can be clearly seen in the exploded view of the detail from FIG. 6 shown in FIG. In Fig. 7, the ih circumferential direction distributed damping springs 127 and the design of the damping sleeve 126 are also clearly visible.
By such a damping device occurring, axial
Clamping force fluctuations are better damped, especially when changing from the train operation in the overrun mode and due to a change in the load torque or the drive torque, whereby a special harmonic power output of a traction mechanism according to the invention can be realized.
As can also be clearly seen with reference to FIG. 7, the clamping force device 340 of this embodiment also differs from the previously described clamping force devices 140 and 240 in that the torque-transmitting section 208 has ramps 221 with different pitches for the traction operation and the overrun operation.
Further, the finger-shaped projections 220 of the axially displaceable Zugmittelscheiben half 205b of the second pulley 205 in the third embodiment of a clamping force device according to the invention 340 or the associated Zugmittelgeometrie invention another geometry at its top, in particular, the projections 220 are not arrow-shaped but wedge-shaped each form only one kind of control cam for train operation.
As a kind of control cam for the overrun operation, however, a second, arranged on an inner side of the damping sleeve 126 projection 128 is provided in this clamping force device 340. This can be seen particularly well with reference to FIGS. 8a and 8b, wherein FIG. 8a shows the detail from FIGS. 6 and 7 in plan view with a set transmission ratio> 1 in traction, but without the clamping force coil spring and the spring plate, and FIG. 8b shows the detail from FIG. 8a in overrun mode.
8a and 8b show different gradients of the ramps 221a and 221b of the torque transmission section 208 as well as the wedge-shaped projection 220 of the axially displaceable traction pulley half 205b and the second projection arranged on the damping sleeve 126, wherein, as can be seen with reference to FIG. 8a, for setting an axial clamping force in the traction mode, the wedge-shaped
The protrusion 220 slides along the upper ramp 221a and the second protrusion 128 slides on the lower ramp 221b, the protrusion 220 preferably not abutting the upper ramp 221a during overrun.
By such a configuration of the clamping force device with two projections 220 and 128 and two ramps 221a and 221b, in particular by two ramps 221a and 221b with different gradients, due to the only small required relative rotation between the torque Übertragungsabschnilt 208 and the axially movable Zugmittelschelben half 205b of the second Zugmittelschelbe 205 for generating an axial clamping force a very fast switching from train operation to overrun operation without having to pass through a large area with occurring slip or with occurring Überanpressung, ie without having to drive through a large area with too little or too much axial clamping force. Furthermore, different axial clamping forces can be realized in this way for train operation and overrun operation.
FIGS. 9a and 9b show the detail from FIGS. 8a and 8b in overrun mode and with a set transmission ratio <1, wherein the set axial distance between the traction pulley halves 105a and 205b is almost maximum. Thus, the grooves for guiding the damping springs 127 in the axially displaceable Zugmitlelscheiben half 205b and the different slopes of the ramps 221a and 221b of the torque-transmitting portion 208 and the wedge-shaped projection 220 are better recognizable, the section in Fig. 9b without Damping sleeve 126 and damping springs 127 shown.
10 shows a section of a fourth embodiment of a traction mechanism according to the invention with a fourth embodiment of a clamping force device 440 according to the invention in the region of the secondary shaft 103 in sectional view with a set transmission ratio> 1, wherein in this clamping force device 440 in contrast to the reference to FIGS. 4a, 4b and clamping force device 240 described in each case two clamping force coil springs 111i and 111a are provided and a ball ramp 129, which via a roller bearing 134 in the form of a ball bearing with an actuator plate 135 and a plurality of circumferentially distributed guide rods 136 each with the inner Klemmkraft- Coil spring 111i is coupled so that by means of the ball ramp 129 a axiaies compression of the inner clamping force coil spring 111i can be effected and in this way an axial clamping force portion can be generated. Oie supporting the axial forces occurring takes place via the ball bearings 137 and 139, with which the torque-transmitting portion 108 and the secondary shaft 103 are mounted in the transmission housing, not shown here.
The ball ramp 129 in this case has two disc halves 131 and 133, between which are arranged in a plurality of circumferentially extending grooves 132, each variable in length over their depth depths 138 balls, which in the exploded view of the ball ramp 129 in Flg. 11 is clearly visible.
The annular disc half 133 further has an external toothing 130, above which the ball ramp 129 can be coupled with a clamping force actuator, for example an electric motor, such that a rotational movement can be applied to the annular disc half 133, which changes the position of the balls 138 in FIG causes the grooves 132 and thus due to the non-constant groove depth a change in the axial distance of the two Ringscheibenhäiften 131 and 133 to each other. The first ring half 131 is axially fixed in the gear housing, and the second ring half 133 of the ball ramp 129 is firmly connected in the axial direction with the actuator plate 135, so that an applied by means of a clamping force actuator rotational movement of the annular disc half 133 an axial displacement of the actuator Plate 135 causes.
The guide rods 136 fixedly connected to the actuator plate are in this case coupled to the inner clamping force coil spring 111i. If the rotational movement applied to the ball ramp 129 causes the two annular disc halves 131 and 133 to slide apart, the inner clamping force coil spring 111i is compressed and the axial clamping force acting on the traction means 106 increases, while collapsing the two annular disc halves 131 and 133 reduces the number of annular disc halves 131 and 133 axial clamping force causes. Of course, only one clamping force coil spring can be provided.
11 shows a section of a fifth embodiment of a traction mechanism according to the invention in the region of the secondary shaft 103 in perspective section with an exploded view of the ball ramp 129 with a set transmission ratio> 1, wherein the clamping force 540 of this embodiment on the one hand as in the reference to FIG cam clamping mechanism constructed as described with reference to FIG. 9 and a corresponding damping device and a ball ramp 129, as described with reference to FIG. 10, via a ball bearing 134, an actuator plate 135 and guide rods 136 with an internal clamping force coil spring 111i, whereby for explanation the function of the individual components is referred to the above-described embodiments.
Of course, a variety of modifications is possible, in particular of structural modifications, without departing from the content of the claims and thus the scope.
Bezugszahlenllste 1 Zugmittelgetriebe from the prior art 2 primary shaft 3,103 secondary shaft 4 first pulley 4a axially fixed Zugmittelschelben half of the first pulley 4b axially displaceably mounted traction pulley half of the first
Pulley 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 pulley 6,106 traction means 7 actuator 8,108, 20Θ Torque-Obertragungsabschnitt 9 drive shaft with gear assembly 10 gear housing 11,111 Klemmkraft- Coil spring 111a outer clamping force coil spring 111 i Inner clamping force coil spring 12 Rolling bearings 13,113 Spring plate 14 Rotation axis of the primary shaft 15,115 Rotation axis of the secondary shaft 40 Clamping device of the prior art 116 Connecting piece 117 Tension rod 118 Belleville spring 119 Friction disc 120,220 on the axially displaceably mounted traction pulley half of the second Zugmittelscheibe angeordheter projection 121.221 ramp with a defined slope at the torque transmission section 121a, 221a ramp with a defined slope for train operation 121 b, 221 b ramp with a defined Steigu for overrun 122 Circlip 123 Bushing 124 Spacer 125 Circlip 126 Damping sleeve 127 Damping spring 128 Projection in the damping sleeve 129 Ball ramp 130 Gearing second half-disc 131 first half-disc 132 Groove with variable depth in the circumferential direction 133 Second half-disc 134 Rolling bearing 135 Actuator Plate 136 Guide rod 137 Rolling bearing 138 Ball 139 Rolling bearing 140, 240, clamping force device 340, 440, 540 according to the invention

权利要求:
Claims (14)
[1]
claims
1. A traction drive with an adjustable ratio for a vehicle, in particular for a quad, Sktdoo or the like, 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, In each case rotationally fixed to the primary shaft coupled, substantially conical Zugmittelscheiben halves is formed, - a second pulley (105, 205) which is coaxial with the secondary shaft (103) and of two, each rotates with the secondary shaft (103) coupled in the essentially conical pulley halves (105a, 105b, 205b) is formed, one the first pulley and the second pulley (105, 205) and in each case between the pulley halves (105a, 105b, 205b) of the first pulley and the second Zugmittelschelbe (105, 205) guided traction means (106) for transmitting a drive power from the Primary shaft on the secondary shaft (103), wherein one of the two Zugmittelscheiben halves (105a, 205a) of the first pulley and / or the second Zugmiltelscheibe (105, 205) is fixed axially and the other Zugmlttelscheiben half (105b, 205b) such is axially displaceable, that a defined axial distance between the Zugmittelscheiben halves (105a, 105b, 205b) of the first Zugmittelschelbe and / or the second Zugmittelscheibe (105, 205), in particular continuously, is adjustable to an effective radius of wrap of the traction means (106 ), - 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 pulley halves (105a, 105b, 205b) of the second pulley (105,205), - a clamping force device ( 140,240,340,440, 540) at least for adjusting a, between the two Zugmittelschelben halves (105a, 105 b, 205b) of the second pulley (105, 205) acting on the traction means (106) axial clamping force, wherein the clamping force means (140, 240, 340, 440, 540) is adapted to mechanically generate at least a portion of the axial clamping force, wherein the clamping force device (140, 240, 340, 440, 540) has a coaxially to the secondary shaft (103) arranged with the secondary shaft (103) coupled, an output side of the traction mechanism forming and axially fixed torque transmission section (108, 208) the torque Übertragungsabschnitl (108, 208) rotatably relative to the rotatably coupled to the secondary shaft (103), axially displaceable Zugmittelscheiben half (105b, 205b) of the second pulley (105, 205) is mounted and formed in such a way and with the axially displaceable Zugmlttelscheiben -Häffte (105b, 205b) of the second pulley (105, 205) is coupled, that by a relative rotation between the Drehmomentübertragu Ngsabschnitt (108, 208) and the axially displaceable Zugmittelscheiben half (105b, 205b) of the second Zugmittelscheibe (105, 205) an axial displacement of the axially movable Zugmittelscheiben half (105b, 205b) is effected to change the axial clamping force.
[2]
2. Zugmitteigetriebe according to claim 1, characterized in that the clamping force device (140, 240, 340, 440, 540) is designed such that the clamping force can be generated at least partially in response to a load torque applied to the torque transmission section (108,208).
[3]
3. Zugmilteigetriebe according to claim 1 or 2, characterized in that the Klemmkraftelnrichtung (140, 240, 340, 440, 540) is designed such that a relative rotation between the torque-transmitting portion (108, 208) and the axially displaceable Zugmittelscheiben half (105b, 205b) of the second pulley (105, 205) causes an axial displacement of the axially displaceable pulley half (105b, 205b) of the second pulley (105, 205) and consequently a change in the axial clamping force when between the torque transmission section ( 108, 208) and the axially displaceable traction pulley half (105b, 205b) of the second traction pulley (105, 205) slip occurs, provided that the maximum transmissible by the traction mechanism torque has not yet been reached, wherein slip occurs when the current rotational speed of the torque Transmission portion (108, 208) of the current rotational speed of the axially displaceable Zugmittelscheiben half (105b, 205b) of the second pulley (105, 205) deviates.
[4]
4. Zugmiltelgetriebe according to claim 3, characterized in that the clamping force device (140, 240, 340, 440, 540) is designed such that at the Drehmomentübertragabschnitl (108, 208) applied load torque, which is smaller than one due to the current between the traction means (106) and the Zugmittelscheiben halves (105a, 105b, 205b) of the second Zugmittelscheibe (105, 205) acting friction force currently transmissible torque, an increase in the distance of the Zugmittelscheiben halves (105a, 105b, 205b) of the second pulley (105, 205) and thus a decrease in the clamping force, and / or in such a way that a torque applied to the torque transmission section (108, 208) load torque which is greater than one due to the currently between the traction means (106) and the Zugmittelscheiben- Halves (105a, 105b, 205b) of the second pulley (105,205) acting friction force currently transmissible torque, reducing the distance of the pulley half n (105a, 105b, 205b) of the second Zugmittelschelbe (105, 205) causes and thus an increase in the clamping force.
[5]
5. traction mechanism according to one of the preceding claims, characterized in that the torque-transmitting portion (108, 208) with the axially displaceable Zugmittelscheiben half (105b, 205b) of the second pulley (105, 205) forms a kind of cam control, wherein preferably at least one projection (120, 220) is provided on the axially displaceable Zugmittelscheiben half (105b, 205b) of the second pulley (105, 205) and the torque transmission portion (108, 208) at least one thread-like, at least over part of the circumference With a defined slope extending ramp (121, 221, 221a, 221b) AufWeist, wherein in particular at least one projection (120, 220) of the axially displaceable Zugmittelscheiben half (105b, 205b) of the second pulley (105, 205) with at least one ramp ( 121, 221, 221a, 221b) of the torque transmission section (108, 208) by relative rotation of the torque transmission section (108, 208) g egenüber the axially displaceable Zugmittelscheiben half (105b, 205b) of the second pulley (105, 205) is engageable such that in a further relative rotation of the projection (120, 220) on the ramp (121, 221, 221a, 221b) slips off and due to the slope of the ramp (121, 221, 221a, 221b), an axial displacement of the axially displaceable Zugmittelscheiben half (105b, 205b) of the second pulley (105,205) is effected.
[6]
6. traction mechanism according to claim 5, characterized in that the Klemmkrafleinrichtung (340, 540) comprises a damping device, wherein the damping device preferably coaxial with the secondary shaft (103) arranged rotatably with the axially displaceable pulley half (205b) of the second pulley ( 205) coupled and in the axial direction at least partially over an engagement region in which the ramp (221,221a, 221b) of the torque Überiragungsabschnitts (208) with the projection (220) of the axially displaceable Zugmittelscheiben half (205b) of the second pulley ( 205), extending damping sleeve (126) and at least one, with its longitudinal axis parallel to the secondary shaft (103) arranged under prestress, on the axially displaceable pulley half (205b) of the second pulley (205) and preferably at an attenuating spring (127) supported on an inner surface of the damping sleeve (126) ) having.
[7]
7. traction mechanism according to one of the preceding claims, characterized in that the torque-transmitting portion (20Θ) has at least two thread-like, at least over part of the circumference with a defined slope extending ramps (221a, 221b) with different pitch, preferably a ramp (20 221a) is provided for adjusting an axial clamping force in the traction mode and a ramp (221b) for setting an axial clamping force in overrun mode.
[8]
8. traction mechanism according to one of claims 5 to 7, characterized in that the damping sleeve (126), preferably on its inner surface, also has a projection (128) provided with a at the torque transmission portion (208) provided, thread-like, in the circumferential direction with a defined slope extending ramp (221b) is engageable such that upon relative rotation of the torque transmission portion (208) relative to the axially movable pulley half (205b) of the second pulley (205) of the projection (128) Damper sleeve (126) on the ramp (221b) of the torque transmission section (208) slides, whereby due to the slope of the ramp (221b) an axial displacement of the axially displaceable Zugmittelscheiben half (205b) of the second pulley (205) is effected.
[9]
9. traction mechanism according to claim 7 and 8, characterized in that the ramp (221 a) of the torque-transmitting portion (208), which is provided for adjusting the clamping force in traction, with the projection (220) of the axially displaceable pulley half (105 b , 205b) of the second pulley (105, 205) is engageable and the ramp (221b) of the torque transmission section (208), which is provided for adjusting the clamping force in overrun, with the projection (128) of the damping sleeve ( 128)
[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 Zugmittelschelben halves (105a, 105b, 205b) of the second pulley (105, 205) via a tie rod (105 117) is connected to the axially fixed traction pulley half (105a), wherein preferably the secondary shaft (103) at least in the region of the second pulley (105,205) is a hollow shaft and the tension rod (117) within the secondary shaft (103) from the torque transmission section (108, 208) to the axially fixed pulley half (105 a) is guided. 11 traction mechanism according to claim 10, characterized in that the tension rod (117) via a friction disc (119) and / or a plate spring (118) with the torque-transmitting portion (108,208) is axially coupled.
[12]
12. Zugmittelgetriebe according to one of the preceding claims, characterized in that the Klemmkraftelnrichtung (240, 340, 440, 540) for increasing the axial clamping force at least one, coaxial with the secondary shaft (103) arranged clamping force coil spring (111, 111 a, 1111) wherein the clamping force coil spring (111, 111a, 111i) under pretension on the axially displaceable Zugmittelscheiben half (105b, 205b) of the second pulley (105, 205) and preferably on a rotationally fixed to axially displaceable Zugmittelscheiben half (105b, 205b ) of the second pulley (105, 205) arranged spring plate (113) is supported.
[13]
13. traction mechanism according to one of the preceding claims, characterized in that the clamping force device (440, 540) has a clamping force actuator and is adapted to, by means of the clamping force actuator in addition to, in dependence on the torque transmission section (108, 208 ) applied load torque applied clamping force share a further, axial clamping force share on the second pulley (105, 205), wherein the clamping force actuator is preferably mechanically so coupled to the clamping force coil spring (111, 111a, 111i) that the Clamping force coil spring (111, 111a, 111i) for applying an additional clamping force share by means of the clamping force actuator is compressible, wherein the clamping force actuator in particular with the spring plate (113) is coupled to which the clamping force coil spring (111,111a , 111 i) is supported.
[14]
14. Zugmittelgetriebe according to claim 13, characterized in that the clamping force device (440, 540) for applying the generated by the clamping force actuator, further, axial clamping force share on the second pulley (105, 205) arranged coaxially with the secondary shaft (103) Ball ramp (129), wherein the clamping force actuator is preferably coupled via a toothing (130) with the ball ramp (129) and the ball ramp (129) with the clamping force coil spring (111, 111 a, 1111), wherein the clamping force Actuator In particular, an electric motor.
[15]
15. Vehicle with a traction mechanism with continuously variable transmission, characterized in that the traction mechanism according to one of claims 1 to 14 is formed.

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同族专利:

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公开号 | 公开日

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AT517594B1|2017-03-15|

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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DE3623116A1|1985-07-10|1987-01-15|Aisin Warner|CONTINUOUSLY CHANGEABLE V-BELT TRANSMISSION|

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US5057061A|1988-12-30|1991-10-15|Aisin Aw Kabushiki Kaisha|Continuously variable speed transmission|US10557541B2|2016-09-19|2020-02-11|Deere & Company|Dry variable speed drive mechanism|

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法律状态:

优先权:

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申请号 | 申请日 | 专利标题

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ATA447/2015A|AT517594B1|2015-07-09|2015-07-09|Traction mechanism with infinitely adjustable transmission|ATA447/2015A| AT517594B1|2015-07-09|2015-07-09|Traction mechanism with infinitely adjustable transmission|