EP0883761A1

EP0883761A1 - INFINITELY VARIABLE VARIOMATIC$m(3) TRANSMISSION

Info

Publication number: EP0883761A1
Application number: EP97906141A
Authority: EP
Inventors: Edgar Löhr
Original assignee: Individual
Current assignee: Individual
Priority date: 1996-03-13
Filing date: 1997-02-28
Publication date: 1998-12-16
Also published as: DE19609750C2; WO1997034092A1; DE19609750A1

Abstract

The invention concerns an infinitely variable Variomatic® transmission. According to the invention, the coupling force is applied via a plurality of coupling means (4), for example coupling bars (15), disposed radially on the drive plate surfaces, or by the belt (23) itself which expands in the manner of an articulated lever. The coupling force is thus generated in a load-proportional and self-reinforcing manner by the coupling means, utilizing the tensile force of the belt and functionally separate from the application of the coupling force to the belt sides (28). The coupling force is generated by means of mechanisms acting according to known principles, for example with wedge, lever or roller mechanisms operating with very low friction losses. In contrast, the coupling force is applied to the belt by means of surfaces having a positive grip at the highest possible coefficients of friction. In this way, the friction losses are minimized, the torque output is considerably increased, the partial load efficiency is improved and the thermal stress on the belt is greatly reduced. The principle can be applied to known V-belt transmissions and advantageously to a novel belt transmission with a rectangular belt cross-section and flat drive plates.

Description

Infinitely variable vario gearbox

The present invention relates to a continuously variable transmission, preferably for use in muscle power drives and light vehicles, according to the preamble of claim 1.

Belt drives run lubricant-free and quietly, they are also low-maintenance and insensitive to moisture. They therefore have a wide range of applications in general mechanical engineering. For the same reasons, they were predestined for use in the muscle power drive of bicycles or other energy-efficient light vehicles. Continuously variable transmissions (Vario transmissions) are always of particular interest, since they could optimally meet the requirements of travel and process drives , have a relatively poor efficiency due to the required high preload and the type of power transmission and they consume a lot of energy (up to over 10%). They fail in muscle-powered vehicles due to the relatively low transferable torques, their sluggish and sluggish shiftability and their wide design.The deeper reason for the poor efficiency is the principle underlying the V-belt drive of the functional unit of frictional connection between belt and drive pulley and generation of the coupling force due to the wedge shape of the belt and drive pulley cross-section. The generation of a high coupling force is inevitably hindered here by the necessary high coefficients of friction. As a result, belt pretensions of up to 50% of the tensile force to be transmitted are required. This additionally increases the friction losses and also the bearing losses. The losses are unacceptably high, especially in the partial load range, the most common operating condition for vehicles

A load-dependent self-tensioning V-belt drive from Thun, especially for bicycles, has recently become known as GLAD.It has good efficiency, high torque output and automatic, stepless change in gear ratio.However, it has poor concentricity (five-polygon) and unsatisfactory shifting capacity, which is a problem additional hub gearbox required. But especially the connection of transmission and manual transmission in a transmission unit, such as chain shift transmissions, without further downstream transmission, would be ideal for weight, cost and efficiency reasons for use in bicycles and light vehicles Another disadvantage of the above-mentioned transmission is that due to the more or less fluctuating torque during the rotation, it works constantly and leaves a strange feeling of pedaling In DE-GM 18 13 816 a transmission according to the preamble has become known which uses a high number of coupling means arranged in the driving means and actuated by a switching means rotating around the drive pulleys for the frictional coupling of the driving means. The applied coupling force is proportional to the belt load and the efficiency good in all areas of operation A blatant disadvantage of the transmission, however, is its high production costs. Both the drive means and the switching means consist of a high to very high number of components. The costs were allowed to be correspondingly high. Another disadvantage is the large overall width of the drive, switching and Coupling devices are made of metal and must be protected from oxidation and contamination by a gearbox housing.Therefore, it is unsuitable for use in light vehicles or bicycles.DD 257 presents a gearbox that provides rotating coupling devices with the drive pulleys, which, in order to change the practice Ratio, can be adjusted radially by a wedge mechanism Here, too, the coupling force is generated proportional to the load by a wedge mechanism The effort for the radially movable coupling means, for the chain drive means and for the switching means or adjusting device is also high The switching force is, as in known V-belt variators, relative high The overall width is large In US 20 56 844, a transmission has become known which couples the belt-like drive means, which is arched in cross section, by lateral spreading when bending to flat drive pulleys. However, this is not a continuously variable transmission, but rather a device for transmission or Force redirection Means for adjusting the transmission ratio are not specified The lateral coupling force is constant and not dependent on the load.

DE 38 20 517 Cl shows a transmission which uses a chain drive means which can be spread by non-rotating switching means which actuate the wedge mechanisms and can thus be coupled to flat drive pulleys. These wedge mechanisms are located in the drive means themselves and are present in large numbers. However, the generation of the coupling force is constant. The effort for the coupling force is high, the partial load efficiency is poor. Noise and wear and tear could also be significant, since the propellant glides permanently and with considerable force and at full speed over the switching lugs

The state of the art in switchable belt transmissions is unsatisfactory, particularly with regard to use in muscle vehicles or in energy-efficient light vehicles. Simple Vario transmissions have poor efficiency. Transmissions with good efficiency are very expensive to build. In particular, the state of the art knows no Vario transmission with high efficiency on the The basis of a simply constructed propellant. Since transmissions are used for a wide variety of transmission distances, it is very important to be able to use an inexpensive, belt-like propellant The object of the invention is to provide a continuously shiftable power transmission which can be manufactured with little technical effort, in particular for the propellant

This object is achieved by the features specified in the characterizing part of patent claim 1 or in the independent claim 35

Advantageous embodiments and further developments are the subject of the dependent claims

In the Vario gearbox according to the invention, the change in the transmission ratio, as in the case of the infinitely variable V-belt gearbox, is brought about by guiding the drive means, for example a belt, on the secondary / output double pulleys on variable diameters in each case, and the input / output of the drive forces is achieved by the lateral belt flank On An essential basic principle of the invention is to apply the coupling force required for non-positive power transmission within the continuously variable transmission depending on the load (load proportionality), to introduce this coupling force via the lateral belt flanks (lateral coupling) and not directly through the belt flank, but through a separate, low-friction and on to have the drive pulley mechanism, preferably using the belt tension, generated (separation of functions), or - in a second solution of the task according to the invention - by a roof-shaped, self-underneath to have a dozen coupling belts produced When building up the coupling force, sliding processes between the belt flank and coupling means are largely avoided according to the invention. The relative movements required to build up the coupling force required in wedge, lever, or roller body mechanisms are converted into the coupling movement in a low-friction manner

For this purpose, in the first solution of the transmission according to the invention, several coupling means are seated on the drive pulleys, which have a surface on the belt side with high coefficients of friction, but are mounted on the drive pulley side on low-friction sliding surfaces or on roller bodies or even roller bodies they represent from the smallest to the largest possible Running diameter of the belt The load-dependent coupling force can be generated as required, e.g. electrical, hydraulic or mechanical.It is preferably generated using the tangential and radial belt forces by known force-intensifying and force-deflecting mechanisms, e.g. wedge, roller body or lever mechanisms, with as little friction as possible Coupling force proportional to the belt load and, depending on the geometry used, in extreme cases the holding force of a coupling element can be the maximum permissible Exceeding the belt tensile force Very high transmission forces without pretension and even at low wrap angles are possible, but, in order to achieve a good performance-to-weight ratio, the forces should be distributed to as many coupling elements as possible at the same time

The travel of the coupling means required to generate the coupling force is very small and typically amounts to 1-3 mm. The associated friction losses are correspondingly low. The geometry of the wedge, lever or roller body mechanisms allows the ratio of coupling force to belt tensile force to be set

The aim is to safely couple the belt under all operating conditions, but at the same time to limit the coupling force to the lowest possible level in order to keep the loads on the transmission parts and the energy losses as low as possible. Too high power transmission ratios have inevitably destroyed the belt and the drive pulley make it unnecessarily difficult.

A technically particularly simple solution according to the invention provides for the coupling means to be designed as more or less radially arranged coupling strips and to be mounted on the driving pulleys on tangential and radially inclined sliding surfaces relative to the drive pulley axis - hereinafter referred to as inclined surfaces - via the inclined surfaces, the force transmission between the coupling means and Drive pulley predominantly form-fitting The alignment of the inclined surfaces and their incline is matched to the belt and the coefficients of friction between the belt and coupling means as well as between coupling means and sliding surface on the drive pulley. The angle between the intersection of the inclined surface and the drive pulley plane on the one hand and the radius beam on the other hand is referred to here as the clearance angle (C) and is usually between 20 ° and 60 °. The greater the radial pitch angle relative to the tangential pitch angle is - measured to the plane of the pulley - the more The smaller the two are, the higher the ratio of the coupling force to the belt force, the more securely the belt is coupled, but the greater the belt stress caused by lateral deformation

The coupling process takes place as follows after the first contact of the belt with the surface of the coupling strip, the belt takes the coupling strip, due to the high static friction between the belt flank and coupling strip on the one hand and the low friction between coupling means and inclined compartment on the drive pulley on the other hand, along its insertion path, with which it slides of the inclined surface, increasingly emerges from the belt pulley level and couples the belt proportionally to the load over the belt flank. Disengagement takes place in opposite directions. The belt moves the dome ledge along its outlet path to a lower level until it is released A double arrangement of the spreading elements, acting in each load direction, makes it possible to operate the brake and brake, forward and reverse, provided that at least one shift or positioning device is provided for each direction of rotation and each drive pulley. The principle of such a transmission with load-proportional, low-friction generation of the coupling force is transferable according to the invention to all positive belt transmissions with lateral introduction of the coupling force

With wedge gears, especially wedge variators, a significant increase in efficiency and torque output can be achieved

According to the invention, it is proposed to attach the coupling means, preferably in a larger number and regularly distributed, to the conical surfaces of the drive pulleys.The coupling means are so far above the conical surface that the belt comes to rest on them. Because of the conical shape, the running circle diameter is determined by the conical pulley distance cuts the cone surface at an angle of preferably 10-30 ° The resulting cutting line is preferably parallel to the cone axis or the radius beam.This is how the tangential, but also the radial belt tension is used to generate the contact pressure due to the cone pitch. The coupling takes place by the straight on a coupling means wide V-belts the coupling means takes a small piece with the action of the belt pull and this slides on with the generation of a load-dependent contact pressure

The travel of the coupling means is only approx. 1 mm with the usual belt dimensions, since the belt comes to rest on the coupling means anyway due to the wedge shape, so that only a certain belt compression has to be achieved and the infeed distance is omitted. As coupling means, sliding coupling strips mounted on sloping surfaces or themselves can be used Dome rod rolling or tipping in the circumferential direction with a round oval or polygonal cross-section in question The latter can be raised further from the cone surface both by the shape of the radial groove in which they roll and by their shape with their belt-facing surface when rolling or tipping Couple the straps on their side flanks depending on the load

Return springs return the coupling means to their starting position after lifting off the belt, i.e. the position with the least protrusion over the conical surface.This always ensures the same travel path and good concentricity.Coupling strips made of plastic can have molded-on plastic webs 31 or resilient holding elements 50 perform this function These plastic webs can connect the individual coupling strips to a single part, the coupling strip star, which brings advantages in terms of assembly technology. The coupling surfaces of the coupling means do not have to be rectangular, but can also be designed, for example, trapezoidal The coupling means can also act in the other direction of force by means of an oppositely directed slide-on or roll-up or tilt-up path, so that operation in any direction of force and in any direction of rotation is possible

It makes sense to use materials with the highest possible coefficients of friction on the belt side and the lowest possible coefficients of friction on the pulley side of the coupling means

The use of such side-engaging, self-supporting and low-friction coupling means in V-belt drives has the following advantages

1 The load-dependent coupling force achieves good efficiency, in particular also partial load efficiency and high torque output. Belt pretensioning is not necessary for this purpose

2 The friction losses are greatly reduced by several effects

- Due to the higher torque power, the speed can be greatly reduced with the same power output, which leads to less flex power loss

- The low friction coefficients of the coupling means on the conical pulleys greatly reduce the sliding friction losses of the belt

- Due to the minimal preload, the bearings are relieved and there are significantly lower bearing losses

3 Frequently, the thermal load caused by friction is the limiting factor in the power throughput of belt transmissions, so that with the present invention, the mechanical performance of the belt can be exploited far better due to the much lower friction losses

4 Due to the high coupling force of the coupling means, it can be operated with smaller wrap angles, which enables larger ratios in one step

Overall, this results in significant improvements in the area of V-belt transmissions

Another variant of the transmission according to the invention, which is particularly advantageous for muscle power drives, provides for the use of a belt, the flanks of which are arranged parallel to one another

The known wedge shape of the driving means, e.g. a belt, is replaced according to the invention by a rather rectangular shape, more precisely a shape with parallel flanks. Accordingly, the conical double disks or V-groove disks used in other gears are replaced according to the invention by facing double disks, the mutually facing inner surfaces of which are roughly parallel The running radius of the belt is not brought about by a complicated and forceful change in the pulley spacing - which would be pointless with flat pulleys - but by controlling the lateral coupling of the drive means between The discs The position of the coupling point (E) determines the running radius.For this purpose, the coupling means can be switched at a defined point by switching means. Coupling means are provided for coupling the driving means with the face plates, which either on the face plates - according to claim 1 - or - according to auxiliary claim 35 - On, preferably in the propellant itself They are designed to achieve load-dependent power transmission under load self-supporting or self-locking and disconnect at the outlet point, preferably automatically

Accordingly, according to the invention, depending on the embodiment, a disc-coupled (claim 1) or a belt-coupled (claim 2) transmission can be distinguished. In the following, the term "belt" is used analogously to the term driving means. In both embodiments, the coupling means or the belt itself reacts switching on by switching elements (e.g. cams, control rollers), on relative movements during the insertion or coasting process between the belt and its / its support points on the drive pulleys and set the tangential and / or radial belt movements and belt forces in axial spreading movements and thus in lateral pressure forces on the Belt flanks around. For a good concentricity, the coupling means are preferably available in larger numbers (e.g. 10 pieces per pulley or 100 pieces per meter on the belt). The coupling force is generated either by mounting the coupling means on expansion elements, e.g. on inclined surfaces, on diagonal levers or on rolling elements or - in the case of dome belts - due to a flat roof shape of the belt cross-section that spreads under the load in a self-locking manner under load (toggle lever principle) To avoid overloading the gear parts, the force ratio of all these mechanisms is geometrically limited.

In the case of a disk-coupled gear, the direction of movement of the coupling means is matched to the running-in movement of the belt to avoid frictional losses.With the short travel distances of a few millimeters required here, this corresponds approximately to the angular value - measured with the radius beam - of I80 number of coupling elements per drive pulley corresponds to sliding along this travel path the coupling means by means of their inclined surfaces on assigned inclined surfaces of the drive pulley or are raised axially in the direction of the belt flank by inclined levers or roller bodies (spreading elements), which leads to a lateral contact force on the flanks which is proportional to the belt tensile force. The spreading elements usually also transmit the tensile force from the belt to the Drive disks and vice versa The transmission ratio of tensile force to contact pressure can be adjusted and limited within a wide range to the requirements by appropriate geometries or pitch angles of the expansion elements the gradient ratio between 1 2 and 1 6 is also through the alignment of the inclined surfaces (clearance angle (X) of the load portion taken over by the respective coupling means in the total load can be adjusted and optimized for the respective number of coupling means that are simultaneously engaged) A slight pretensioning of the empty run of the drive belt 1 can be helpful in order to achieve a more even load distribution An arrangement of additional spreading elements mirrored to the radius beam enables universal four-quadrant operation (e.g. stepping backwards)

When designing the expansion elements, it must be taken into account that the movement path of the belt 1 is mirrored relative to the radius beam relative to the drive pulley at the entry point (entry angle / j) to the path at the exit point (exit angle Y), so that the movement of the expansion elements requires a second degree of freedom . The clearance angle (Dt) must be at least slightly larger than the inlet (ß) or outlet angle), both of which can be calculated from the formula 360 / 2n, where n is the number of coupling elements per drive pulley. This is particularly easy due to sliding surfaces to be achieved, which achieve a high degree of efficiency with good sliding pairing.

The angle of inclination of the inclined surfaces in relation to this plane of the pulley is matched to the coefficient of friction of the material pairing belt / coupling bar and to the coefficient of friction between the coupling bar and the drive double pulley. It is preferably between 10 and 30 ° to the drive double disc plane

In their rest position, the coupling strips are preferably embedded in the drive pulleys slightly below the pulley level, so that you cannot touch the belt in the rest position and cannot engage prematurely. They are engaged at the desired switch-on point of the belt on the double pulley by a mechanical, electromagnetic, pneumatic or hydraulic switching device and at the exit point A by a switching device or automatically. The position of the engagement point E in relation to the synchronous point G (FIG. 1) determines whether the belt is shifted to a larger - switch-on point E is opposite to the direction of rotation compared to the synchronous point G - or a smaller - switch-on point G is displaced in the running direction - diameter, which results in a continuous variation of the barrel radii. The synchronous point results geometrically as the corner point of the isosceles triangle K-M-G, where M is the center of the running circle, K is the coupling point of the leading coupling bar and G is the switch-on point for the same running diameter.

Since there is a change in the belt inclination when the running radius changes, there is an automatic shift of the synchronization point G which stabilizes the currently set running radius. This effect is with very long belts and small drive pulleys 2 weak and may have to be reinforced by one or two auxiliary rollers in the vicinity of the drive double disk 2.Therefore, each running circuit diameter also corresponds to a certain other synchronous point G, which means that the gear ratio is represented by a shift in the switch-on points E by shifting the switching point S, represented by the shift of S in Fig. 1, can be checked and regulated

It is important that the switch-on points E on the input and output are changed simultaneously and in opposite directions, so that the belt does not run slack in the empty run or comes under inadmissible pretension. Likewise, the outlet point A of the coupling means must be at the right point. Switching off serves, for example, the belt tension and inclination or the radial movement or radial position of the belt at the entry point E or exit point A, as well as the switching positions of the other switching devices, which must be recorded accordingly and implemented in terms of control technology (mechanical or electronic)

With fully switchable four-quadrant operation, four controlled switch-on devices must be provided, but fixed switching points for reverse operation are also possible. Depending on the design, e.g. the use of switch-on springs or switch-off springs or one or two switching devices per drive double disk, various requirements can be met a) Single-quadrant operation with reverse freewheel (Couplings acting in one direction only) b) Two-quadrant operation with withdrawal or kicking backwards (double-acting coupling means and spreading elements, two further, fixed switching devices) c) Four-quadrant operation (double-acting coupling means and spreading elements, four adjustable switching devices in total) d) Switching on the mountain gear after briefly kicking backwards (switch-off springs)

With d), when coupling back for a short time, all the coupling bars are released and the belt falls to a small inlet diameter on the drive side.This means that a usable starting gear can also be engaged when the vehicle is at a standstill. Spring springs acting on the belt (not shown) can support this process

Withdrawal brakes according to b) (also reversing) is possible if the terminal strips near the entry point E are also switched on during the brief exit step through the cam, preferably, seen in the drive in the reverse direction of rotation clearly after the synchronization point G, with the output clearly before this, with what there is a more leverage ratio (mountain gear) instead of disengaging springs, too engaging possible and advantageous, the cam disc must act accordingly opposite and is preferably placed on the inside near the axis (Fig. 4,5)

By limiting the path of movement of the coupling means, e.g. via stops, or by limiting the pretension of the empty span in conjunction with a correspondingly large clearance angle (CX), the maximum transferable force can be limited, which prevents self-destruction of the gearbox if the control unit malfunctions and protects other drive parts

The shifting capacity that can be achieved is only dependent on the space available for the drive pulleys and can easily exceed 400% given the conditions in the bicycle. The gear ratio can be controlled independently of the load that occurs. Pulsating, strongly fluctuating torques (as with the pedal drive) do not have an automatic one Influence on the gear ratio The coupling means can basically be actuated by any switching devices, for example also electromagnetic, hydraulic or pneumatic. Mechanical switching devices are particularly simple and preferable for muscle power drives.

The mechanical switching of the engagement point (and thus the gear ratio) is carried out by means of a shift cable or a shift servo motor.

Curve segments or control roles

By coupling the switching devices to one another or by checking the

Belt tension or the belt length of the empty strand with a corresponding effect on the

Control elements ensure that the belt does not run limp or under impermissible

Preload device

As a rule, a complete translation change is within just one or two

Revolutions can be realized, which even surpasses the switching speed of derailleurs

All elements are protected from water and dirt or by appropriate

Material choice insensitive to these media

In the embodiment as a belt-coupled transmission, the coupling elements are attached to, preferably in the belt. The facing double discs in this embodiment have no coupling means as described in the previous exemplary embodiment. Switching means exerts a force spreading the belt on the roof-shaped belt, so that the belt and coupling to the double discs takes place The belt can be designed as a textile-reinforced rubber belt or as a steel belt. The transmission of tractive force is provided in the middle of the belt. The belt can be flexed by a few angular degrees in its long center.The side areas of the belt thus act as the legs of a toggle joint which, when coupled, spreads even further under the radial belt load and thereby presses the belt flanks against the drive pulleys. The belt areas acting as lever legs are pressure-resistant executed and are supported on each other via the joint-like belt center. Belt width and drive pulley spacing (= ring groove width) are dimensioned in such a way that the knee lever joint is not completely pressed through. The roof shape of the belt is therefore always retained to a certain extent. For industrial use or in motor vehicles, an effect with every direction of force and rotation is necessary ( Engine brake / reverse drive). Switching on takes place via switching devices that act mechanically, electromagnetically, hydraulically, pneumatically or via another method. The switch-on devices of both drive double pulleys must be precisely coupled to each other in terms of control technology so that the belt does not run limp in the empty strand or get under unduly high tension. For this purpose, the running radii must be determined repeatedly, depending on the position of the switch-on point, and taken into account when coupling the switching devices. Alternatively, it is possible to measure the belt tension permanently and use it as a controlled variable.

To achieve a compact design with high transmission capacity, several belts can run in parallel, the double pulleys being able to support one another in some cases. At higher speeds, a larger number of coupling means is useful to avoid polygonal vibrations. In high-speed motors, the high speed on the drive side can be used to actuate the coupling means by centrifugal forces, which at the same time integrates a centrifugal clutch

Advantages of the invention over known Vario transmissions.

- Low manufacturing costs due to the small number of different components that are also inexpensive

- Power shiftable due to permanent engagement of several coupling elements

- Practically slip-free thanks to the self-locking mechanism with short coupling paths

- High efficiency through load-dependent coupling forces and reduced friction

- Extreme switching capacity possible due to large circuit differences

- minimal switching force through automatic coupling means

- Quiet running at low to medium speeds due to the short travel of the coupling means

- relatively narrow construction due to the use of face plates with constant, small mutual distance - Good roundness with a higher number of coupling agents

- High switching speed due to rapid shifting of the coupling points

- Relatively low weight due to rubber straps, especially with long transmission lengths

- largely maintenance-free and low wear with low glide paths

- Once set, no further adjustment work necessary due to the lack of switching stages

- Reliable due to simple kinematics

- It is insensitive to a rotation of the drive axles about the longitudinal axis of the transmission with a corresponding belt length, which means that it can also be used for front-wheel drive on recumbent bikes

- Suitable for one to four quadrant operation, depending on the number and orientation of the expansion elements and the number of switching devices

- Suitable for machines and vehicle drives, due to controlled adjustable translation - Infinitely variable adjustment of the ratio by controllable shifting of the coupling point

- It is, as a four-quadrant transmission installed several times in a vehicle and controlled by a central vehicle computer, can be used both as a differential replacement and as an anti-slip control.

The Vario transmission according to the invention thus has a number of essential advantages over the prior art and is particularly suitable for single-quadrant operation (one direction of travel, one direction of force) of a bicycle drive because it is technically simple to implement

In the following, the invention is based on several embodiments and

Drawings illustrating the functional principles are explained in more detail here

Drawings and their description further essential features and advantages of the invention

Invention.

Show it

Fig.1 Representation of the switching principle and the stabilization of the running circuit

Fig. 2 Representation of the basic principle of the change in setting of variable belt transmissions

(Unit of switching and transmission); Fig. 3 sectional view of the basic body of a disk-coupled transmission

Drive double pulleys and flat belts, Fig 4 View with partial section of the drive double pulley with coupling strips and

Cam; 5 view and partial section of the output double disk with coupling strips,

Cam, feeler roller and facing belt, Fig. 6 Representation of the entry and exit angle of the belt on the coupling strip polygon; Fig. 7 sectional view of the basic body of a belt-coupled transmission

Rubber textile belts; Fig. 8 sectional view of the base body of a belt-coupled transmission with steel band; Fig.9 representation of a belt-coupled transmission with steel belt and shift rollers; Fig.10 sectional view of a roof-shaped dome belt; Figure 1 1 partial section of a dome belt reinforced by Spreizköφer; Fig.12 side view of a corrugated steel strip, Fig.13 cross section of a corrugated steel strip

Fig. 14 View of a conical drive pulley in the radial direction Fig. 15 View of a conical drive pulley in the axial direction Fig. 16 Partial cross section of a drive pulley with coupling strips Fig. 17 Partial cross section of a drive pulley with coupling bars Fig. 18 Partial view of a coupling strip star Fig. 19 Cross section of a coupling strip with spring Sheet metal plate and slightly lying

Belt Fig. 20 Cross-sectional view of a dome strip with resilient sheet metal plate and fully coupled strap Fig. 21 Cross-sectional view of a dome strip with female strips and slightly attached belt Fig. 22 Cross-sectional view of a dome strip with female strips and fully coupled belt Fig. 23 Cross-sectional view of a dome strip with steel spring clips and a slightly overlaid strap Fig. 24 Cross-sectional view of a coupling strip with brush spring strips and slightly flying belt Fig. 25 Representation of the four functional phases of a driven pulley with positioning elements Fig. 26 Representation of the interaction between the pocket roller and adjusting ring Fig. 27 Partial cross-section through a drive pulley made from formed sheet metal Fig. 28 Partial cross-section through a drive double pulley with overload protection and Dirt deflector Fig. 29 Partial cross section through a drive pulley with brushes as a positioning element Fig. 30 Partial cross section through a drive pulley with steel spring clips as a positioning element Fig. 31 Partial cross section through a double drive pulley with sloping steps

Sliding surfaces Fig. 32 Top and side view of a dome strip with inclined steps

Sliding surfaces

14 to 17, the embodiment of a pulley-coupled V-belt variable transmission is shown. Eight radially arranged coupling strips 15 are arranged on the conical drive pulleys 5. They sit in flat V-shaped grooves that the Function of the swash plates The distance between the drive pulleys is variable to control the barrel diameter according to known systems. The coupling strips 15 are made of plastic and have a surface with a high coefficient of friction to the rubber belt. On the drive pulley side, they have a very low coefficient of friction to the swash plates 6. Toothed wide V-belt 48 used Due to its relative movement to the drive pulley, it takes the coupling bars somewhat in the tangential and radial direction, which forces them to slide onto the inclined surfaces and thus to the lateral coupling of the belt. The coupling bars are secured by molded-on resilient holding elements 50, which snap into fastening openings, held and always pulled back to its rest position The V-shaped arrangement of the inclined surfaces enables operation in any load and direction of rotation. Instead of coupling strips 15, it is also possible to use rolling elements, such as coupling rods 52, which are seated in radial grooves 53. The groove base is also V-shaped, so that the coupling rods increasingly come out of the drive pulley surface when they are offset and couple the belts. They are - not shown - in by return springs pulled their rest position. The coupling rods can slide a short distance radially in the grooves so that the radial belt tension can also be implemented

3 to 6, a second variant of the pulley-coupled transmission with flat pulleys and parallel belt flanks is described. Here, an essentially rectangular belt 1, which is dimensioned in its length to the bottom bracket / wheel bearing distance, runs in the gap between the halves or drive pulleys 5 of the input 2 and driven double disks 3. This gap, that is to say the distance between the disks to one another, is somewhat larger than the belt width so that the belt 1 does not come into direct contact with the pulleys. The coupling means 4 are designed as coupling strips 15 and are preferably seated in pairs opposite one another on the inner sides of the 5. The belt 1 has at least approximately parallel belt flanks and, for simplicity, is rectangular / square in cross section and laterally very pressure-resistant, but soft in the bending direction, which by corresponding deep bending notches, as with V-belts, can be achieved. The coupling force is generated by a whole number (in the example, 12 or 8 pairs per double pulley) of switchable, laterally acting in the axial direction, self-supporting or self-locking coupling strips 15 which, in the rough shape of the belt flank 27, drive / driven double pulleys ( 2; 3) sit, which do not touch the belt 1 itself. These coupling strips 15 are switched by switching devices, preferably mechanically via cam disks, cam disk segments 8 or control rollers

It is preferably switched on mechanically and by means of an axially or radially acting cam plate 8 or a cam plate segment, against which the control pins 9 of the Start up coupling strips 15 or separate intermediate lever or control tappet.This cam is actuated on the drive side directly by the shift cable 18 or shift servo (= active control), on the output side preferably via a feeler roller 10 (Fig. 5), the changes in the empty span length in corresponding displacements of the switch-on time by adjusting the cam disc 8 , for example via a lever gear 16, 19, 21, 22 (= reactive controller). The spring-loaded feeler roller 10 can push the belt 1 outwards or inwards. When the feeler roller 10 is pressed outwards, the control arm 19 must cause the cam plate 8 or the cam plate segment to move against the direction of travel when swiveling outwards (= extension of the empty run); if the feeler roller 10 is pressed inwards, it causes a shift in the direction of rotation when swiveling the outside out the individual case can be optimized in order to avoid control vibrations on the one hand and to allow a correspondingly rapid readjustment on the other hand

The drive pulleys are e.g. Made of high-strength light metal investment casting and have on the belt side a number of radially extending recesses for receiving and mounting the coupling strips 15 These are mounted on four inclined surfaces 6 - two on the outside, two on the inside - and have the inclined surfaces 6 'and are assigned by an annular wire spring 17 is pulled into the coupling switching position. The inclined surfaces 6, measured both radially and tangentially, have a pitch angle to the drive pulley plane of e.g. 20 °. The coupling strips 15 have control pins 9 on the axle side which slide along the cam plate 8 in the inlet area over a section of approximately 45 ° arc angle and are raised radially by approximately 3 mm and lowered again relatively quickly at the switch-on point, the belt 1 having an axial vertical offset of about 0.5-1 mm is coupled immediately

The cam disc 8 is made of plastic and does not rotate itself. However, it is adjustable around the center of the drive axis and coaxially rotatably supported on the drive disc on the frame side. However, the cam disc 8 has a radial play of 3 mm compared to the drive disc 5 and is centered by a corrugated wire spring for overload protection

In front of the switch-on point, the coupling strips 15 for the insertion of the belt 1 are in the low position up to the current barrel diameter, then in a self-locking and self-supporting engagement with the belt. The belt is switched off automatically. The cam disc 8 is actuated directly on the drive side by the shift cable 18, on the output side by the feeler roller 10 and a translating coupling by means of a driving pin 22. The feeler roller 10 has a guide collar on each side, which prevents the control arm 19 from jumping off under rough conditions around a joint the support plate 16, which is connected to the bicycle frame in a rotationally fixed manner in a threaded eye. The control arm 19 is pressed against the belt 1 with relatively little force by a spring (not shown). The sliding surfaces of the drive pulleys 5 are covered, for example, with thin steel plates, the corresponding counter surfaces of the clamping strips 15 made of polyamide coated with sliding plastic The clearance angle of these inclined surfaces is approximately 45 °, which may require a slight pretension in the empty strand 28 via the resilient feeler roller 10. The bearing strips / clamping body 15 or rollers are preferably stored in high-strength light metal cast discs or deep-drawn or injection-molded carbon fiber plastic disks, which are shaped with appropriate bevels or joint grooves and stops. They have openings, holes or pocket holes for the control lugs or control tappets, connecting screws and return springs. These input / output double disks 2, 3 can be made in one piece or in several parts. In their rough shape they are largely flat towards the belt. On the outside they are for better absorption of the Spreading forces are preferably flat-tapered The coupling strip grooves are preferably embedded in reinforcing ribs 29 has a cassette holder for cassette hubs in the middle or a corresponding freewheel thread, which can be used to attach it as standard

The control of the coupling strips 15 can alternatively take place on both sides by means of two synchronously actuated cams 8 or curve segments or, if the coupling strip pairs are coupled to one another by a driver, on one side. This coupling takes place on the base of the disc groove

To reduce frictional losses when bending the belt 1 during the coupling process, especially with very wide coupling strips and / or a large number of coupling strips, the long centers of which are somewhat raised. The belt begins to flex at this point before the full contact pressure is reached

The smallest running radius of belt 1 is determined by its maximum permissible bend, the largest barrel diameter is almost arbitrary. Depending on the available space, extreme reduction ratios can be achieved. The belt is designed to be highly tensile and very flexible and has corresponding notches on the underside ( not shown)

For the bicycle transmission, the diameter of the drive double disks is approx. 22-26 cm, that of the driven double disks about 60% thereof. With the racing bike, the downforce will be smaller, with the mountain bike or cargo bike it will be correspondingly larger For conventional bicycle frames, the strap must be divisible via a strap lock or glued together. However, it is better to adapt the frame in such a way that an undivided strap is possible. In any case, guiding the chainstays of the bicycle above the belt level would be ideal, since then there is more space available for the transmission itself.

As a further improvement, it is proposed according to the invention to produce the coupling strips 15 from plastic, the side facing the belt being e.g. through embedded fibers and / or a rough structure of the surface or through a coating or planking with appropriate ceramic or metallic materials - e.g. a wear-resistant, possibly corrugated sheet metal plate 35 has a high wet friction value on the belt material, while the inclined surfaces 6 'facing the drive pulley are smooth and have the lowest possible coefficient of friction compared to the material of the inclined surfaces 6 located on the drive pulley - preferably polished stainless steel - drive pulley . If necessary, this can be achieved by an appropriate coating with Teflon or other sliding plastics. Good friction values towards the belt are e.g. possible with fiber-reinforced polyamide, whereby at least the sliding surfaces should consist of special sliding plastics with a coefficient of friction of less than 0.2. These should also be able to inkoφorieren smaller dirt particles without greatly affecting the coefficient of friction.

It is particularly advantageous in terms of manufacturing and assembly technology to combine the individual coupling strips 15 of a drive pulley in a single, star-shaped, permanently elastic plastic injection-molded part, the coupling strip star 30, by molding plastic webs 31 onto the individual coupling strips (FIG. 18). These plastic webs are preferably designed as return and retaining springs, e.g. through multiple curvature. They also carry snap pins 32 with which they snap into recesses in the drive pulley 5. In this way, manufacture and assembly are extremely simple and the number of components is greatly reduced. The effect of these plastic return springs can, if necessary, be supported by metallic return springs.

In addition to the production of the drive pulleys using casting technology, deep-drawn or pressure-formed drive pulleys made of sheet metal 47 are also advantageous in terms of cost (FIG. 27). The inclined surfaces arranged in a step-like manner to reduce the overall width, like the reinforcing ribs 29, are formed in one piece. The starting form is a sheet metal cone, which enables the deep folds necessary for the reinforcing ribs in the interior. The drive pulley made of sheet metal 47 is pressed onto an axle tube 46 and connected in a rotationally fixed manner. To save weight, material cutouts can be provided in the fields between the coupling strips.

To protect the sliding surfaces from small foreign bodies, it is advantageous to provide clearing lips 36 on the edges of the sliding surfaces and hollow-shaped dirt deposits or Through holes 44 to be provided in the corners (FIG. 31), which receive the dirt particles which have been cleared away or lead them to the outside

For difficult operating conditions, it is proposed according to the invention that resilient or elastic, ring-shaped dirt deflectors 41 are attached to the outer edge of each drive pulley, which stand somewhat in the pulley groove in their rest position and whose mutual spacing is less than the belt width, so that its flanks when entering and exiting that slide past or out of the disc groove past the dirt deflectors and are freed of adhering dirt (FIG. 28). These dirt deflectors can also take over the function of positioning elements that make it possible to dispense with the belt locating roller 10. For sprung vehicles in which lengthways changes in the empty strand due to the deflection and thus influences the unevenness of the road surface on the translation, we proposed according to the invention to mount the bearing journal 21 of the control arm 19 on a displaceable adjusting ring 40 (FIG. 26). A push rod attached to the vehicle frame at a suitable point pivots this La pinch when deflecting so that the resulting change in the running circle radius largely compensates for the gear adjustment caused by the change in length of the empty run

In the case of unsprung vehicles, this addition mechanism can be used in order to achieve a high rapid shifting capability. For this purpose, the shifting cable 18, which also effects the drive-side transmission adjustment, is also used to turn the adjusting ring

To limit the loads acting on the drive parts, it is often sensible to provide an overload safety device. According to the invention, it is proposed that the individual drive disks be axially displaceable relative to one another by 1-2 mm on the connecting bolts 43 and their tensioning force via disk springs 42 or elastic rings or the like on the drive disc body (Fig. 28) By appropriately limiting the travel of the coupling means 4 by means of stops, it is possible to regulate the maximum coupling force by preloading the disc springs. The maximum axial stroke of the coupling means above the drive pulley level must be less than the difference between the driving means width and the maximum Drive pulley distance This is determined by the available spring travel. It is sufficient to carry out this overload protection on only one side, preferably on the drive double pulley. The advantage is that the gearbox does not reach the maximum expected force of a user ers must be designed, but can be calculated according to precisely definable maximum forces, which can save a lot of weight. To minimize the frictional losses when inserting the belt is provided according to the invention, the belt by spring bars 37 located on the coupling means or by a resilient over a narrow gap gripping wear-resistant sheet metal plate 35 with limited force and flexing in bending zones 33 before the full coupling force begins (Fig. 19-24) One variant of the invention provides that the feeler roller 10 be dispensed with entirely and that positioning elements 37, 38, 39 (FIGS. 19-24, 28-30) located on the driven side between or on the coupling strips 15 are used to control the belt running circuit that guide the belt to the maximum possible circle radius specified by the running circle on the drive side. These positioning elements consist of resilient or elastic sliding surfaces, which each want to keep the incoming belt at the greatest possible radius with a small force, since they come along from the inside along the belt flank. Only when the empty strand 28 of the belt tightens is it pulled into position and held there. On the output side, the engagement point E is located approximately at the synchronous point for the smallest running circle diameter and always remains in this position. The positioning elements can be designed as steel spring clips 39 or spring strips 37 made of plastic, or as brushes 38 in the most wear-resistant quality. The above-mentioned dirt deflectors 41 can also perform the same function, since they always want to guide the belt to the maximum radius.

It is important here that a flexible belt is used in order to make the holding forces of the positioning elements and thus the resulting friction losses as low as possible.

On the driven pulley, four phases can be distinguished during the rotation (Fig. 25): In the Positionieφhase I, the belt slides onto the positioning elements coming from below until the empty strand 28 has tensed slightly. At the end of this first phase, he is in the maximum radial position specified by the running circle on the drive pulley. At the beginning of coupling phase II, the coupling strips couple the belt after passing coupling point E, which is close to the synchronization point for the smallest barrel diameter or even further in the direction of travel. In the disengaging phase III, the dome bars release the belt automatically. In the lifting phase, the coupling strips are raised radially by the cam 8 in order to be able to accommodate the belt in the subsequent phase I between them.

In a further embodiment of the transmission according to the invention, also referred to as a belt-coupled transmission (FIGS. 7-13), the coupling means are located, preferably in the belt 23 or drive means 24; 25. The propellant is also a coupling agent. The facing double discs 2; 3 in this embodiment have no coupling elements as described in the previous embodiment. In the relatively wide dome belt 23, expansion bodies 1 1 made of hard rubber, plastic or metal are flatly embedded in a V-shape. The "tip" of the V-shape points to the outside (top of the belt), the outer belt flanks 27 point slightly to the inside (bottom). The belt cord 12 preferably runs in the middle above the spreader body 11, whereby the radial component of its tensile force on the center the Klemmkoφer 1 1 prints and this, as soon as the flanks of the belt have coupled to the pulley wall of the pulleys 2, 3, spreads like a toggle lever, whereby a high, force-proportional contact pressure arises. The tip angle of the V-shape must not be too close to 180 ° be printed, otherwise the "toggle lever" jumps over and disengages The belt 23 is somewhat narrower in its basic form than the distance between the face plates, so that it cannot be non-positively coupled by it. It can have recesses 26 between the expansion bodies for better flexing in the side area (Fig 11) The coupling process is carried out by two control grippers, but preferably control rollers 13, 13 ', which deform the belt from below 13, optionally additionally from above 13', on the pulley side and in such a way that the belt 23 and thus the coupling are spread as an alternative for this purpose the belt 23 or a steel belt 24 used as a "drive belt" can be shaped so that it is at m Coupling into the running circle, then the time of coupling is determined by the position of control rollers 13, 13 'or fingers, which prevent the belt 23 or the steel band 24, 25 from being coupled by counter-bending. The radial position of the switch-on point is decisive for the running radius E The control rollers 13, 13 '(FIG. 9) are inserted from above or below on the inlet side of the belt on a, possibly fork-shaped, support arm 14 between the double pulleys, the double support arm being adjusted radially by the shifting cable and on the housing on a bearing pin 21 is rotatably mounted

After switching on, the belt 23 remains at the coupled point on the pulley 5 until it automatically uncouples by unloading or pulling upwards at the outlet point A. On the driven side, however, the belt 23 does not come under load immediately when it is engaged, but only gradually in the direction of its path to the disengagement point A so that it still remains at the coupled point, the bending stiffness of the belt 23, which contains a radial and thus coupling force component, is not chosen too low and, if necessary, increased by a steel band spring insert. This steel band insert preferably forms at the same time die Spreizkoφer The support arm of the pulleys on the output is regulated via the belt length of the empty strand or via the position of the active shifting regulator. It must be avoided that the empty strand gets under high tension. The efficiency of the embodiment of the invention as a nominally coupled gear is with rubber belts because of the clear Wa lk work in the belt deformation may not be quite as good as in the embodiment a disk-coupled transmission, but the concentricity is high and the noise development is very low

A special form is the steel belt dome belt transmission (Fig. 8), which has a very good efficiency, but less torque. It uses a slightly roof-shaped, rolled and hardened steel belt 24, which can also be corrugated or folded on the side, steel belt 25, ( Fig. 12, Fig. 13) The control rollers 13, 13 'may have to be adapted in shape to this corrugated steel strip 25 List of reference numbers

Exit point A empty strand 28

Coupling point E reinforcing rib 29

Synchronization point G dome strip star 30

Switching point S plastic webs 31

Center point M snap pins 32

Coupling point of the current element K

Clearance angle or bending zone 33

Entry angle ß spring gap 34

Outlet angle ϊ sheet metal plate 35

Belt 1 space lips 36

Double drive disc 2 female connectors 37

Output double disk 3 brushes 38

Coupling means 4 steel spring clip 39

Washer 5 collar 40

Sloping 6.6 "dirt deflector 41

Spacer ring 7 disc springs 42

Cam 8 connecting bolts 43

Control pins 9 through holes 44

Belt traction roller 10 falling lines of the inclined surfaces 45

Expanding body 1 1 axle tube 46

Belt cord 12 drive pulley made of sheet metal 47

Timing pulleys 13.13 'V-belt 48

Lever arm 14 conical surface of the drive pulley 49

Dome strips 15 resilient holding element 50

Carrying plate 16 fastening opening 51

Ruckholfeder 17 coupling rod 52

Shift cable 18 radial groove 53

Control arm 19 Positionieφhase I

Auxiliary role 20 dome phase II

Bearing journal 21 disengagement phase III

Driving pin 22 Lifting phase IV

Dome strap 23

Steel band 24 corrugated steel band 25

Belt cutouts 26

Belt flank 27

Claims

claims

1. Infinitely switchable Vario gearbox with a drive and drive double disk and a drive means connecting both drive double disks for the transmission of the rotary power, wherein a continuous change in the gear ratio is given by a continuous change in the drive medium radius on at least one of the drive double disks, characterized in that the power transmission between the drive means and the drive double disks (2; 3) takes place through coupling means (4; 15; 52) which engage laterally on the drive means and are seated on the drive double disks (2; 3) and which are defined by a part of the which defines the smallest to the largest possible running radius Extend drive pulley radius.

2. Transmission according to claim 1, characterized in that the introduction of force from the drive double disks (2; 3) to the drive means and vice versa by self-supporting coupling means (4; 15; 52).

3. Transmission according to claim 1 or 2, characterized in that the drive means is a belt (1) and that the coupling means (4; 15; 52) are attached in greater numbers and at regular intervals on the drive pulleys, the coupling process preferably non-positively via a lateral introduction of the coupling forces onto the belt flanks (27) with the highest possible coefficient of friction.

4. Transmission according to one of claims 1 to 3, characterized in that the belt (1) in the area of the loop through several coupling means (4; 15; 52) is gripped simultaneously, which the belt (1) at the switch-on point (E) laterally and preferably couple over a large area and release at the outlet point (A), it being possible for the coupling means (4; 15; 52) to be switched on and off automatically or by any type of switching means (mechanical, electromagnetic, hydraulic, etc.).

5 Transmission according to one of claims 1 to 4, characterized in that the coupling means (4) are designed as, preferably radially arranged, coupling strips (15) or plates which are somewhat displaceable radially and tangentially relative to the drive double plate (2, 3) and are supported on sliding surfaces which are radially and tangentially inclined relative to the disc axis, the inclined surfaces (6, 6 ') on the discs for transmitting the torque and for generating the coupling force, the coupling means (4, 15) being displaced on the insertion path to the first coupling point and then further to the end position due to the belt pull through these inclined surfaces (6; 6 ') to be forced to a small axial displacement on the belt and thereby press against the flanks (27) of the belt (1) with load-dependent force.

6 Gearbox according to one of claims 1 to 5, characterized in that the intersection of the plane of the inclined surfaces (6; 6 ') with an imaginary, plane perpendicular to the pulley axis results in an angular value of 20 ° -60 ° to the radius beam, this as Clearance angle (£ designated angle is matched to the number of coupling strips (15) per drive double pulley (2, 3) and the smaller the higher this number, and the angle of inclination of the inclined surfaces with respect to this plane of the pulley depends on the coefficient of friction of the material pairing belt coupling means ( 1; 4, 15; 52) and the coefficient of friction between the coupling strip (15) and the drive double disc (2; 3), the pitch angle of the inclined surfaces to the drive double disc plane preferably being between 10 and 30 °

7 Transmission according to one of claims 1 to 7, characterized in that the coupling strips (15) of a drive pulley consist of plastic and are injection molded in one piece as coupling strip star (30) and that the coupling strips on the belt side have a high coefficient of friction due to their material properties or surface structure and have high wear resistance to the belt, but their sliding surfaces on the drive pulley side have the lowest possible coefficient of friction with the inclined surfaces, the plastic webs (31) connecting the individual coupling means preferably being designed as return springs and preferably also as retaining elements which snap into the drive pulleys, these Return springs compensate both radial, tangential and axial displacement of the coupling means.

8 Transmission according to one of claims 1 to 7, characterized in that a commercially available V-belt or wide V-belt (48) is used and the coupling means sit on the conical pulleys of V-belt drives or V-belt variator gears and preferably over the entire possible radius range parallel to the cone surface (49) Drive pulleys extend

9 transmission according to claim 8, characterized in that the coupling means are designed as coupling strips (15) which protrude somewhat beyond the conical disk surface, and in that the coupling strips (15) are mounted on the conical surface (49) of the drive pulley obliquely arranged sliding surfaces and on these are radially and / or tangentially displaceable over a certain distance and that the coupling strips increasingly come out of the conical surface during the displacement by the incoming belt and couple the overlying belt, the slope of the inclined surfaces preferably being 1 2 to 1 6

10 Gearbox according to one of claims 8 or 9, characterized in that the cutting lines between the inclined surfaces (6,6 ') and the conical surface (49) of the drive pulley are arranged approximately parallel to the radius beam of the conical pulley and that the coupling strips under belt load predominantly in Shift circumferential direction and press against the belt flank depending on the load

11 Transmission according to one of claims 8 to 10, characterized in that the coupling means (4) consist of coupling rods (52) of round, oval or polygonal cross-section and are preferably arranged radially, said rod in radial grooves (53) in the conical surface (49 ) of the drive pulley are mounted and in their rest position they protrude slightly over the cone surface and can roll or tilt under belt load over a certain distance in the circumferential direction or in the radial direction and thus increase their projection over the cone surface and press onto the belt flank depending on the load

12 Transmission according to one of claims 1 to 11, characterized in that the coupling means (4) are retracted into their rest position by restoring springs, that is the position with the least protrusion over the surface of the conical disk

13 Transmission according to claim 1 to 7, characterized in that the drive means is designed as a rectangular or square belt (1), and that the lateral flanks (27) of the belt (1) provided for the introduction of force are approximately parallel to one another at least in the coupled state on the inner surfaces of the drive double disks (2, 3) or the coupling means (4, 15)

14 Transmission according to claim 13, characterized in that the mutually facing inner surfaces of the drive double pulleys (2, 3) are essentially plan and arranged parallel to each other and that their mutual distance is greater than the width of the unloaded belt (1), the Belt (1) with its side flanks (27) by switchable coupling means (4, 15) between a coupling point (E) and an exit point (A) can be coupled to the drive double disks (2, 3) on a predeterminable running circle radius and is held on this determined running circle radius by the acting clutch force e

15 Gearbox according to one of claims 13 or 14, characterized in that the change in the running circle radius takes place by coupling the belt (1) on different running circle radii, specifically via a controlled displacement of the switch-on points of the coupling means (4) or the coupling point (E) , based on the current synchronous point (G), in or against the running direction of the belt (1)

16 Gearbox according to one of claims 13 to 15, characterized in that the

Controls of the engagement points (E) on the input and output double pulleys (2, 3) are preferably coupled in opposite directions and avoiding impermissible tensions of the belt (1) or that the control of the switch-on point (E) on the output depends on the length or the tension of the Empty run (28) of the belt (1) is dependent and is controlled by the control system so that, with a shortening or tensioning empty run, the coupling point (E) is shifted in the running direction or the belt (1) is shifted in the direction of the drive axis and thus there is a reduction in the running radius at the output and vice versa

17 Transmission according to one of claims 13 to 16, characterized in that only one of the drive double pulleys (2, 3) is switchable and the maintenance of a defined tension or length of the empty run (28) of the belt (1) via a tension roller or a change in Axis distance between drive and output takes place

18 Transmission according to one of claims 13 to 17, characterized in that when disengaging a displacement of the coupling means (4, 15) caused by the lifting belt (1) itself on the inclined sliding surfaces (6, 6 ') along the outlet path and thus due to the clearance angle (CX) takes place to an axially lower level and the belt is freed from the belt flank (27) by axially removing the coupling means

19 Transmission according to one of claims 13 to 18, characterized in that the switching on of the coupling means (4, 15) to the desired switching point (S) is preferably carried out mechanically by parts of the coupling means (4, 15) or corresponding intermediate elements with each revolution of the drive double disks (2, 3) are moved radially by a switching means in the switching area, the coupling means (4, 15) preferably only in by the switching means one direction of travel are actuated and the return to the starting position takes place via return springs (17)

20 Gearbox according to one of claims 13 to 19, characterized in that the switching means is designed as an adjustable cam (8) on which the coupling means (4, 15) or intermediate elements slide at least in the switching area, and thus the switch-on point in or

can be adjusted against the running direction of the belt (1) by a switching device acting on the switching means, e.g. by a shift cable (18), the cam disc preferably being rotatable about the drive axis as the center of movement, but not rotating with the drive pulleys (5), but with the gearbox or frame via an adjusting device, e.g. a shift cable (18) is connected

21 Transmission according to one of claims 13 to 20, characterized in that the length of the belt (1) or the tension of the empty strand (28) is preferably detected via a feeler roller (10) and by a transmission in a corresponding control movement of the cam control disc (8) is implemented on the output (3), a reduction in the empty strand length or an increase in the tension relocating the coupling point (E) in the running direction of the belt (1) and thus reducing the running radius and vice versa

22 Gear according to one of claims 13 to 21, characterized in that the cam disc (8) or the cam segment on the output double disc (3) from one, preferably from the inside, with a sensing roller (10) and by spring force against the empty strand (28) of the belt (1) printing control arm (14), the fulcrum (21) of which is located on the transmission housing or frame or a frame-fixed support plate (16), is driven by a driving pin (22), with the spring force at the same time prestressing the empty strand of the belt (1) is brought, which ensures a reliable coupling to the coupling means (4, 15) of the output double disks (3) and a better load distribution among the clutches on the drive side

23 Transmission according to one of claims 13 to 22, characterized in that a flexible, deeply serrated but side pressure-resistant belt is used to reduce the friction when the belt flexes during the insertion process and that the surfaces of the coupling means (4) preferably slightly raised in the long center are

24 Transmission according to one of claims 13 to 23, characterized in that preferably to reduce frictional losses between the coupling means (4, 15) and the drive double disks (2, 3) low-friction material pairings (e.g. steel / plastic or sliding alloys) with sliding coatings if necessary the inclined surfaces (6, 6 ') or rolling elements between the coupling means (4) and the drive double plates (2, 3) are used, preferably the sliding surfaces or the rolling elements being protected by sealing elements against the ingress of dirt, possibly also water, or even are largely insensitive to these media

25 Gearbox according to one of claims 13 to 25, characterized in that preferably with a long length of the belt (1), the belt (1) in the traction strand near the drive double pulley (2, 3) is guided over at least one guide roller (20) , which increases the effect of the radius stabilization due to the changing inclination of the belt (1)

26 Transmission according to one of claims 13 to 25, characterized in that the cam discs (8) or the cam segment, the coupling means (4, 15) for the necessary opening of the clutch when the belt runs in, initially radially against the spring force of the return springs (17) or the plastic webs Raise (31) and snap it back radially at the coupling point and thus initiate the automatic coupling process

27 Transmission according to one of claims 13 to 26, characterized in that the bearing point of the control arm (14) is arranged pivotably and this pivoting of a coupled to the shift cable of the drive side second shift cable or by a push rod attached to the frame or the like in the chassis movements compensating manner is operated

28 Gearbox according to one of claims 13 to 27, characterized in that female connectors

(37) on the coupling strips or a slightly curved, wear-resistant sheet metal plate (35) resilient over a spring gap (34), grasp and flex the belt in a narrow area before the coupling force is fully applied

29 Gearbox according to one of claims 13 to 28, characterized in that a control roller (10) is dispensed with to control the running radius of the output double disk (3) and instead resilient or elastic positioning elements, such as spring strips (37), brushes

(38) or steel spring clip (39) can be used, which keep the incoming belt with relatively little force on the maximum running radius given by the respective running radius on the drive double pulley (2), these positioning elements exceeding that of extend the smallest and largest possible running circle defined part of the drive pulley and the belt on these positioning elements can move when the weak holding force is overcome and the switching point of the coupling means is at the synchronous point for the smallest running circuit diameter or is shifted further in the running direction

30 Gearbox according to one of claims 13 to 29, characterized in that on the outer edge of the drive pulleys, left and right of the pulley groove, towards the belt, ring-shaped, elastic or resilient dirt deflectors (41) are attached, which in the rest position so far into the pulley groove protrude that the remaining distance from each other is slightly narrower than the belt width and the incoming and outgoing belt has to push the dirt deflector to the side, the flank of the belt sliding past the cleaning edge of the dirt deflector as it enters and exits, preferably the elastic or resilient dirt deflector ( 41) of the output double pulley take over the function of the positioning elements and always guide the belt to the maximum possible barrel diameter by running from below onto the belt flank

31 Gear according to one of claims 1 to 30, characterized in that the coupling strips have at the edges of the sliding surfaces space lips (36) which keep the sliding surfaces free of contamination and that hollow dirt deposits or through holes (44) are provided in the corners of the inclined surfaces

32 Gearbox according to one of claims 1 to 31, characterized in that for overload protection, the heads of the connecting bolts (43) which connect the drive pulleys to one another are prestressed by springs - preferably disc springs (42) or elastic elements, and that the drive pulleys are exceeded diverge a certain load and that a stop is provided for the coupling means that limits their path of movement, the free space between the coupling means in the stop position is greater than the sum of the belt width and available travel

33 Gear according to one of claims 21 to 32, characterized gekennzeichr ^Λ t, that the bearing journal (21) of the control arm (19) mounted on a Stellπng (40) is which passes through the shift cable (18) or - with sprung vehicles - one at the Vehicle frame attached to a suitable point is turned

34 (24) gearbox according to one of claims 1 to 33, characterized in that preferably in the case of fast rotating drive units which are connected to the coupling means (4, 15, 52) centrifugal forces that occur are used or used to couple or disengage the driving means

35 steplessly switchable vario gearbox with a drive and drive double disk and a drive means connecting both drive double disks for the transmission of the torque, whereby a continuous change of the gear ratio is given by a stepless change of the drive medium running radius on at least one of the drive double disks, characterized in that the Coupling means in the form of spreader bodies (11) are integrated in the tapping means (23, 24, 25) and the belt-like or belt-like drive means can be expanded

36 Transmission according to claim 35, characterized in that these coupling means or the belt itself are continuously operated or spread by external switching elements (13, 13 ') mounted on the transmission housing / frame, and in that the double pulleys (2, 3) themselves do not have any further coupling means wear and are preferably even in their entire running surface and provided with a grippy surface structure, the change in the running circle radius by raising or lowering the drive means (1, 23; 24, 25) shortly before the engagement point (E) by switching elements (13, 13 ' ) he follows

37 gearbox according to claim 35 or 36, characterized in that the coupling-capable drive means (23) is preferably roof-shaped in cross-section, laterally in its legs, for example by means of a number of stiffening bodies embedded in the drive means, in the transverse direction pressure-resistant, in the longitudinal direction but for small running radii is sufficiently flexible and is articulated or flexible in its center in the longitudinal axis and rigid in the longitudinal direction

38 Transmission according to one of claims 35 to 37, characterized in that a tension cord (12) preferably runs in the middle in the region of the "roof ridge" and the ridge angle and thus the effective width of the drive means due to the action of the switching elements (13, 13 '), which grasp and spread the propellant preferably from above and below, close to the edge and possibly in the middle, possibly also bend and / or prevent premature spreading, as far as can be enlarged by spreading, so that the propellant flank (27) directly on the inner surfaces of the double discs (2 , 3) couples and automatically disengages at the exit point (A) by lifting the pull cord, the support arms (14) of these shifting elements, for engaging the driving means to different running radii, mounted on the gearbox housing or frame and displaceable or pivotable for shifting the gearbox

39 Gearbox according to one of claims 35 to 38, characterized in that to change the running radius, the switching elements (13, 13 '), which can be designed as rollers or double rollers, which are opposite to the drive pulleys (2, 3) radially with each other by a movable Carrier arm (14) or double carrier arm can be moved or pivoted

40 Gearbox according to one of claims 35 to 39, characterized in that the drive means in the region of its flanks (27) has a reduced compressive rigidity in the longitudinal direction, which allows bending even by small running circle diameter, this reduction in compressive rigidity by a flank-side shaft or W-structure of the pressure-resistant material of the drive means (25) or by means of hard and soft short sections of the drive means which alternate in the longitudinal direction or by recesses (26) or in another way

41. Transmission according to one of claims 35 to 40, characterized in that the drive means (1) consists of a spring steel band (24; 25) which is bent roof-shaped in cross-section, the coupling by the flexing of the curved steel band (24th ; 25) and the automatic expansion caused by the remaining longitudinal stiffness of the flank area (27), which is possible after passing through two control rollers (13) pressing from below in the flank area after a short running distance, the coupling process being carried out by two more, a little further rollers (13 ') which run from the top against the flank region and are counter to the direction of travel of the steel strip can be supported

42 Gearbox according to one of claims 35 to 41, characterized in that the steel strip (25) is corrugated or folded in the flank region in the longitudinal direction.