EP2252499A2

EP2252499A2 - Transmission having continuously variable gear ratios between an input shaft and an output shaft

Info

Publication number: EP2252499A2
Application number: EP09722071A
Authority: EP
Inventors: Edmund F. Nagel
Original assignee: Individual
Current assignee: Individual
Priority date: 2008-03-21
Filing date: 2009-03-23
Publication date: 2010-11-24
Also published as: WO2009114882A2; AT507482B1; AT507482A1; JP2011514284A; AT507465A1; US20110011192A1; WO2009114882A3

Abstract

The invention relates to a transmission having continuously variable gear ratios between an input shaft (1) and an output shaft (2), said transmission comprising at least two pendulum arms (9) pivotally supported about an axis (10), which are caused to carry out uniform and alternating lifting movements (21), which overlap in the work cycles, by the rotation of the input shaft (1) and the cam disks (7) positively connected thereto, said movements being converted into the longitudinally variable back and forth movements of the two transmission elements (26) by means of two adjusting parts (15), which can be displaced along the pendulum arm adjusting travel (20), or by means of two pendulum arms (15), which can be displaced by the pendulum axis (10) along the pendulum arm adjusting travel (20), said alternate movements being transmitted at the two rotation direction-dependent clutches (27), where they in turn are converted into a continuous and uniform rotation of an output shaft (2), each pendulum arm (15) automatically canting under a work load with respect to the provided canting noses (18) in the pendulum arm pass-through (11).

Description

Transmission with step-variable transmission between an input shaft and an output shaft Il

Transmission with a continuously variable ratio between an input shaft and an output shaft, which has at least two pendulum arms pivotally mounted about an axis, the offset by the rotation of the input shaft and the form-fitting connected cam in a uniform, mutually and mutually overlapping in the working cycles lifting movement which are by means of two adjustment members which are displaceable along the pendulum arm adjustment path in the variable length reciprocating movements of the two transmission elements and this alternating movement is transmitted to the two, spatially remote direction-dependent couplings, where they turn into a continuous and uniform rotation an output shaft converts.

So-called stepping gear with infinite translation adjustment are known and are shown in the patent literature in a variety of versions:

From the patent US 4,112,778 a transmission is known, which performs a continuously variable ratio between an input shaft and an output shaft. The problem of jerky rotation on the output shaft is mitigated in this invention by the fact that a plurality of pendulum levers overlap in their sinusoidal power transmission phases to the output shaft. Thus, only a part of the sine curve of a power transmission is transmitted to the output shaft in order to transmit the force of the next pendulum arm in the same way to the output shaft. As a result, although the jerky rotation of the output shaft is no longer so pronounced and heavy vehicles can be driven by such a transmission. For the drive of a light vehicle, such as a bicycle with its correspondingly low net mass, but it is also unsuitable.

The PCT / EP93 / 01771 patent shows a stepping gear in which a ring is pushed around the input shaft by means of a servo-hydraulic cylinder in a more or less pronounced eccentric position. The stronger the ring is moved into an eccentric position, the more strongly the pendulum arms arranged radially around the ring deflect one after the other in a rotationally offset manner. These partial rotations are transmitted via Überholgetriebe to the individual output shaft. Also in this construction, the difficulty arises that the rotation of the output shaft is not uniform, but takes place jerkily. Therefore, this transmission for driving a light vehicle, such as a bicycle with its correspondingly low net mass, also unsuitable.

In the invention US 2,080,665 addresses the problem of jerky rotation of the output shaft with a uniform increase in the multiple cam flanks. It should be avoided as far as possible the jerky rotation of the output shaft. However, this can only be partially successful, because with the adjustment of the illustrated axis point of the pendulum arm, the angle of the scanning lever to change these cams. As a result, the geometry of the cam flank changes to the scanning lever and the original uniformity of a rotation goes with the change of the gear ratio again in a jerky rotation of the output shaft over. For the drive of a light vehicle, such as a bicycle with its correspondingly low net mass, this stepping gear is unsuitable.

The patent US 4,182,202 shows in addition to the present in all previously mentioned writings problem of jerky rotation of the output shaft, an adjustment of the suspension bearings of the push rods to the pendulum by means of cables. In the illustration shown, the workload on the slope of the pendulum arms acts according to the cables. If now such a stepping gear, for example, has to move a workload of 6000 N (= real work load / bike), so would act on the cables up to 3000 N. This enormous Verstellast can only be mastered in stationary machines on lightweight vehicles such as a bicycle is so much to be overcome on the actuator Verstelllast to many times too high. Also in a variant further proposed adjustment of the suspension point of the push rods by means of racks and Rollengleitteilen is not practical for a Leichfahrzeug. In such vehicles, such as mountain bikes, the weight and the mechanical complexity play a very important role. Weight and technical effort are to be reduced to an absolute minimum. For the drive of a light vehicle, such as a bicycle, with 1.) its low weight, 2.) the required filigree Bowden cables, 3.) the required low weight of the transmission and 4.) the required low technical effort, is the use this gear excluded.

The stepping gear shown in the published patent application DE 34 11 130 AI eliminates the problem of jerky rotation of the output shaft. It is the cam track of a cam on which the pendulum arms run so created that a linear rotation angle course is given. Thus, the uniform rotation of an input shaft is thus also converted into a uniform rotation on the output shaft. The invention shown is missing However, a viable solution to transfer the transmission to a light vehicle. In addition, it is not possible to accommodate the immense amount of components useful on a light vehicle. The construction is unsuitable for its mounting on a bicycle, for example, because of its relatively complicated construction and large number of components, as well as because of the lack of a practicably implementable switching mechanism.

The illustrated in the patent application DE 29 38 013 stepper gear for specially bicycles also has the core problem of this continuously variable transmission: It turns the uniform rotation of an input shaft not in a uniform rotation of an output shaft, but in a jerky rotation. To the input shaft, an eccentric is pushed into a more or less pronounced eccentric position. The more the eccentric disk is moved, the more the pendulum arms arranged radially about it deflect more and more in an angle offset in rotation. These partial rotations are transmitted via a ratchet gear to the single output shaft. Also in this construction, the difficulty arises that the rotation of the output shaft is not uniform, but takes place jerkily. Therefore, this transmission for driving a light vehicle, such as a bicycle with its low intrinsic mass, in itself unsuitable.

The German patent DE 696 02 840 T2 shows a similar transmission for specially bicycles and also has the core problem of most so-called Schrittschalt- Stufenlosgethebe: It turns the uniform rotation of an input shaft not in a uniform rotation of an output shaft, but in a jerky rotation. To the input shaft, an eccentric ring is pushed into a more or less pronounced eccentric position. The stronger the eccentric ring is moved, the more the radially arranged around three pendulum arms deflected angle of rotation successively deflect. These partial rotations are transmitted via a ratchet gear with internal teeth on the single output shaft. Also in this construction, the difficulty arises that the rotation of the output shaft is not uniform, but takes place jerkily. Therefore, this transmission is also for the drive of a light vehicle, such as a bicycle with its correspondingly low net mass, in itself also unsuitable.

Also, from the patent US 5,603,240 a stepping gear is known, which has a cam which prevents a jerky rotation of the output shaft by the corresponding profiling of the cam tracks. By means of the three, overlapping in their action of the duty cycle pendulum arms a uniform and uninterrupted rotation of the drive shaft is achieved. In the illustration shown, however, lacks a viable solution to transfer the transmission to a light vehicle. In addition, several teeth Conclusions in this gear available, which known to reduce the efficiency to the extent that an insert on the bike must be excluded. Again, it is not possible to accommodate the immense amount of components useful on a light vehicle. The design is unsuitable for its adaptability to the bicycle, for example, because of its relatively complicated construction and large number of components as well as because of the lack of practicably implementable switching mechanisms and the reduced mechanical efficiency.

European Patent Specifications EP 0615 587 B1 and EP 0527 864 B1 disclose so-called "automatic transmissions" or "electronic control systems for bicycle transmissions". It is in the titles of inventions gives the impression as if such a transmission without further action by the driver can make an automatic switching of the gear ratio. This impression is fundamentally wrong, since the electrically operated changeover mechanism acts on a conventional bicycle chain transmission. This can in no case automatically switch without the driver's intervention, as a non-driver-friendly, "electronically" controlled switching would have fatal consequences: If the front launcher on the large chainrings were operated under full load, the launcher would jam and be destroyed in the bicycle chain If, on the other hand, the rear gearshift were to be switched off under full load and not intentionally actuated by the driver, the driver on the pedal would suddenly have stomped "into the void". This would probably result in a fall of the driver. The term "electronic" and "automatic" in this context is therefore misleading and not really fulfilled by the inventions.

The object of the invention is to provide a continuously variable transmission of the type mentioned for use especially on bicycles. The basic idea is, however, that the rotation of the input shaft be converted into the rotation of the output shaft in an absolutely uniform manner, and that it is absolutely essential for the transmission of force to be in perfect form, Consequently, any gear lock or, in particular, friction between any components should be avoided and the gear should not be lower in efficiency than that of the conventional derailleur gears.Furthermore, the gearbox must be of a fairly simple construction and must be very simple On the other hand, it must also be very light and space-saving.Translating the translation must go with the usual thin Bowden cables or simple hydraulics vonstatten and - in contrast to the conventional chain gear shift of bicycles - j each time Any change of the translation may be possible. This switching is usually to be done by a small servomotor, which is controlled by the bike computer to preset values in comparison to values of bicycle and driver sensors completely automated and without any immediate action by the driver. The different force vectors for vehicle propulsion, which occur due to the different crank angle position to the load-bearing driver legs are to be compensated by a dynamic translation adjustment within a half turn of the crank

The solution of these tasks was carried out by the fact that each pendulum arm under working load automatically canted to the designated tilting lugs in the pendulum arm implementation. To adjust the transmission ratio, the pendulum arms located in a uniform and mutually overlapping reciprocating motion are axially displaced by the pendulum arm passage. Schraubabenzingen-like canting the Verkantnasen automatically in the power stroke between pendulum and pendulum arm implementation. They tilt with the occurrence of a workload in the working so automatically and immovably fixed in each other. Without any action by the user, therefore, the pendulum arm closes automatically fixed during each cycle by the static friction with the pendulum arm implementation immovable.

Alternatively, the solution of the tasks also took place so that displaceable adjusting parts tilt by the occurrence of an applied over the transfer elements work force non-positively to the respective unverschiebaren pendulum and the adjustment are so immovably fixed during the working stroke and automatically to the respective pendulum. Without any intervention by the user, therefore, the adjusting part closes during each working cycle absolutely non-positively and thus loss-free with the pendulum. The greater the load on the transmission element, the stronger this adhesion automatically, canted dynamically.

The frictional connection between the adjusting part and pendulum arm dissolves with elimination of the workload - ie during the return stroke - automatically and without further action at least as far as the respective adjustment part by means of a directed longitudinally to the pendulum arm longitudinal axis, far below the average transmitted by the adjustment traction to shift the lying force. As a rule, and the construction according to the invention already here tensile forces are less than 10 kg. Consequently, the usual thin, conventional Bowden cables can be used and, above all, it will so possible immediately and under load, the transmission ratio - during the Rückstellhubes - arbitrarily adjust.

At each of the adjustment of the suspension point for the transmission element is sufficient - in one of the two directions to the pendulum arm longitudinal axis - removed from that area, within which the adjustment part with the two zugkraftbelasteten and opposite inner edges of the pendulum arm canted. This functional principle can be found in a similar way to the classic screw clamp of the joiner. It verantet the sliding bracket - but in this case the adjustment - by the adjusting obliquely tilting load in a reliable adhesion, which dissolves immediately with elimination of the load again. This tilting and releasing the frictional connection takes place according to the invention on each pendulum arm up to more than 1000 times per minute.

A pendulum is due to a workload occurring, immovable relative to the consequently acting on him force, fixed to the designated tilting lugs in the pendulum arm passage. These forces arise from the more or less pronounced deviation resulting from the pendulum deflection from the rectangular position of the pendulum arm to the tension element. By just this workload of the pendulum is tilted for the duration of the occurrence of a load by just this load immovable against the consequently acting on him force for each pendulum arm implementation and fixed in the Verstellnasen. The greater the load on the transmission element, the stronger the blocking static friction acts on the adjustment lugs or the pendulum arm.

The bicycle control computer detects actual values for driving data of the bicycle or even physiological data of the cyclist via sensors and in comparison to preprogrammed setpoints, he automatically controls fully automatic and without immediate intervention of the cyclist, the adjusting member for the transmission adjustment if necessary. The recorded data of the sensors are on the one hand pedaling frequency and speed, on the other hand detect sensors but z. As well as heart rate, driver's performance, etc. In comparison to given data such. B. target pedal frequency, target heart rate, target power, etc., the computer automatically controls automatically via the adjusting member. A so-called fully automatic bicycle transmission with electronic control system without any restriction was thus created for the first time. Without further intervention of the driver, an automatic switching of the gear ratio is made. This switching depends only on the data that the cycling computer receives from the sensors and can take place immediately and at any transmission load. A single adjustment can the gear ratio by the alternate free movement of the pendulum arms to each pendulum arm passage Adjust in the return stroke in any capacity. The adjusting element adjusts the transmission according to the invention infinitely independently without any direct intervention by the cyclist. An electronics for controlling the adjustment motor can naturally make an adjustment of the transmission much faster and more accurate than any manual switching by the driver.

The adjustment of the pendulum arm length is carried out by means of hydraulic, pneumatic or electromotive or by means of Bowden cables. These adjusting elements generate a force vectors, which is directed against a spring force of the return spring. Basically, various adjustment according to the invention are conceivable such. B .: Acting directly on the pendulum arm or Bowden cable electric adjusting motors, pneumatic or hydraulic adjusting members, wherein the pneumatic adjusting z. B. can be fed from an on-board, manually to be filled compressed air tank. The adjustment Bowden cables can be controlled / adjusted by a servomotor or even by a manually operated adjusting element.

The Rüchstellfeder also has the task of releasing the canting between pendulum and pendulum arm passage during the return stroke actively supported. The spring is spatially arranged to generate a force opposing the spring force to return the clutch and the transmission elements between the components of the pendulum arm passage and the pendulum arm for complete release of the tilt. By this, in the pendulum arm of the spring force to the clutch return opposing spring force, so a force vector is generated which is greater than that which still rests in the return stroke on the transmission elements. As a result, the canting between the pendulum arm and pendulum arm implementation is completely solved in the return stroke and the pendulum arm to the sliding part in the pendulum arm passage towards shifted.

The pendulum arms are each mounted on a separate swing axle. On this pendulum axes sit the Tastarme and thereon the tracer rollers, which are radially offset by half a sine length, or one and a half, or two and a half, etc., a cam plate.

This half sine-length distance allows the two rollers of the probe arms to ride together on a single cam. Half a sine length means half the length of a cam cam from BDC to TDC and back to the next BDC. The offset by half a sinusoidal length of a cam cam, however, does not necessarily have to be played on a cam, the offset can also be, for example, two cams with 1, 5 sine intervals or 2.5, etc., play, The cam plate has a relatively low cam height relative to the rollers in the region in which the pedal pedal longitudinal axis forms the most unfavorable angle for the force output to the force vector of the driver's load-bearing legs. Conversely, in dynamic climbing, it has a maximum cam height in that region in which the pedal pedal longitudinal axis forms the most favorable angle for power output to the force vector of the driver's load-bearing legs. When loading on the pedal pedals, the driver at the OT or OT, due to the angular position to pedal pedal longitudinal axis to the force vector generated by him, exert the lowest usable driving force. In order to reduce or smooth out the resulting load imbalance, the transmission ratio of wheel revolution to pedal rotation is reduced by the dynamic cam flattening in the area of UT or TDC. This leads ergonomically to a comparatively balanced utilization of the driver.

Those missed during an adjustment adjustment, which is not directly implemented because of the alternate blocking of the pendulum arms on the pendulum in an executable adjustment is cached in a mechanical buffer member and generally caught up in the following reset cycle from the affected pendulum. In a variant according to the invention, the Bowden cable shells have a sufficient resilient compressibility to represent the mechanical buffer member. In a further variant of the invention, the cables have sufficient elasticity to represent the mechanical buffer member Be used for adjusting the pendulum arm length, for example, Bowden cables, the two Bowden cables a buffer member intermediate or upstream, which reversibly absorbs the adjustment during the mutual blocking of an adjustment / stores. As soon as the canting of the pendulum arm releases, it is again movable and the buffer member gives the missed Verstellwegstrecke to the affected pendulum. If the Bowden cable sheaths have sufficient resilient compressibility, these or other mechanical buffering elements can be dispensed with, since the adjustment path which can not be carried out on the pendulum arm temporarily upsets the bowden cable sheath, which releases / overtakes the said adjustment path after the blocked pendulum arm has become free. If the Bowden cables have sufficient resilient elasticity, other mechanical buffer members can be dispensed with, since the adjustment path which can not be performed on the pendulum arm temporarily extends the Bowden cables, which resiliently overtakes said adjustment path after the blocked pendulum arm has become free. As a mechanical buffer member and a star-shaped cable linkage can be used in which the adjusting the traction exercising single actuator centrally and the two leading to the pendulum arm ropes laterally offset to the point of attachment in the star average run to the point. This star-shaped connection of the ropes ensures that the cable connection between the blocked rope and the rope exerting the adjusting motor pulls the crease somewhat smoothly in the middle of the star, and consequently the unblocked pendulum arm is adjusted slightly more quickly.

Each of the transmission elements is a heavy-duty spring element interposed, which begins to stretch dynamically and reversibly from the occurrence of a particular heavy load and thus extends the transmission element lastdynamisch. This device virtually replaces the smallest transmission ratios, as the heavy-duty spring can deliver less travel to the freewheels. The energy then stored in the heavy-duty spring is in each case returned to the next working cycle at the beginning of the retrieval cycle, in a supportive manner.

The load spring is dynamically deformed during the working stroke and the spring tension stored in this way is effec- tively released again in the next return stroke. It still prevails on the affected tension element an effective working train on the direction of rotation-dependent coupling, although on the cam already the provision of the pendulum has begun. A way that was generated in the working stroke on the tension element is therefore not completely delivered to the wheel but stored in the spring to act in the later return stroke as an additional force for vehicle propulsion. In this case, the peculiarity of the steel springs the efficiency of such a device according to the invention is very accommodating, since these feathers release an energy stored as deformation in their relaxation to approximately 100% again, so no loss of energy -. B. heat - produce.

In a variant of the invention, the load-dynamic spring element can be adjusted in the spring force from the outside. Such a spring force adjustment can, for. B. by a hydraulic element which increases or reduces the bias of the spring element, be accomplished. The device of the adjustable in the spring force heavy duty spring could in itself already represent a simple load-dynamic Stufen- losgetriebe. This variant is included in the subject invention and could exist separately at any time. There would be no further adjustment required in this simple step.

The direction of rotation-dependent coupling device consists of a rotationally symmetrical core, which is non-positively connected to the wheel hub and are arranged axially adjacent to each other two Klemmkörperfreilaufe, which are each covered by a rotationally symmetric ring, which in turn externally both of a form-fitting allied a chain sprocket or a toothed belt pulley are surrounded. The use of the known sprag clutches, which are arranged axially next to one another on a rotationally symmetrical freewheel core, avoids a large number of steps in terms of production technology. On the other hand, ratchet freewheels, clamping ball freewheels, etc. do not require rotationally symmetrical components with much greater manufacturing complexity. In addition, the application of the sprag freewheels not only shrinks the manufacturing expense, but the size of the direction of rotation-dependent coupling is minimized to the smallest conceivable degree. Furthermore, these sprag clutches have the advantage that they close immediately on the one hand at the beginning of the power stroke with virtually no idle rotation and on the other hand reopen with Begin the return stroke without so-called "breakout force".

In the method of operating a transmission with a continuously variable ratio between an input shaft and an output shaft, it is described that to reduce the weight and size of such a bicycle transmission, each of the pendulum arms is to make multiple but most likely a plurality of rashes within one crank revolution. This is achieved by providing on the driving cam as possible a plurality of cams are provided. If, for example, a dozen cams are provided, an average camming height of less than 2 cm is sufficient to produce such a stroke of the scanning arms that, according to the invention, they travel sufficiently and, vice versa, no excessive load is applied to them.

The method for operating a transmission further describes that rotational direction-dependent clutches are used, which can cope with the invention-specific high switching frequencies of possibly up to about fifty Hz. (50 opening and closing operations / second) and can cope with a closing distance of less than 3 ° of the rotation of the outer rings to the freewheel core. This high switching frequency is a prerequisite that the transmission can be reduced in weight. In fact, doubling the switching frequency means halving the load and thus almost halving the weight.

In particular, are suitable as according to the invention functioning direction of rotation-dependent couplings, which solve losbrechkraftfrei the frictional connection between the outer ring and the freewheel core. The occurrence of breakaway forces would often require strong, if not impossible, restoring forces for the freewheel transmissions. So there would be a risk that in the application of certain freewheel designs, the function of the transmission disturbing blockage occurred for the provision. To cope with the requirements according to the invention and to prevent blocking in the reset cycle, as well as with the required high switching frequency of direction-dependent couplings, the so-called sprag clutches are suitable. These sprag clutches fulfill the only known design all requirements of the invention excellent.

Further advantages and details of the invention are explained below with reference to the embodiment of the invention shown in the drawings. These show:

Fig. 1 shows a schematic representation of a side view of the transmission with its individual cam and the two radially offset by half a sinusoidal cam cam oscillating pendulum and the adjustment with Bowsenzügen and the associated electronic control.

FIG. 2 shows the schematic section A - A / plan view from FIG. 1.

Fig. 3 shows an alternative construction to Fig. 1 with a schematic representation of a side view of the transmission with double cam.

Fig. 4 shows the section through the pendulum in its longest possible setting and also the return spring for the pendulum and the heavy duty spring is shown. In this illustration, the adjustment of the pendulum arm is carried out by way of example by means of Bowden.

Fig. 5 also shows a section through the pendulum arm in an adjustment in which it is extended in about halfway. In this illustration, the adjustment of the pendulum arm is carried out by way of example by means of hydraulic adjusting members.

Fig. 6 shows the two pendulum arms in conjunction with an adjustment in which the alternately temporary Verstell-blocking a pendulum arm is intercepted / stored by the star-shaped interconnection of the cables as a buffer member.

Fig. 7 shows a special application of the heavy duty spring with an adjustment, which can change the bias of the dynamic load spring from the outside while driving. Fig. 8 shows a section through the direction of rotation-dependent coupling with the two sprag freewheels and the section through the wheel hub.

9 shows a schematic side view of the cam disc and the pedal pedals for the dynamic flattening or elevation of the cam discs for reducing the gear ratios in the range UT / OT in dependence on the pedal position.

In Fig.1 a multi cam cam 7 is shown, as well as the pendulum axes 10 with the displaceable pendulum arms 15. Further, the control of Pendelarmverstellung via Bowles 25 is shown and their electromotive 30 adjustment and its control of an on-board computer 31, compared to a default setting the adjusted by the sensors 33, 34 actual value readjusted by adjusting the gear ratio.

The number of cams 8 is shown in the drawing with four. As a rule, however, more than a dozen of these cams 8 are arranged in order to limit the individual stroke of the Abtastarmes 13 to a reasonable level (<20 mm) at the same time mechanically manageable load on the Abtastarm 13 or the Abtastarm roller 14. If this remains Load, as solved according to the invention, small, the smallest standard load rolling bearings 14 can be used.

The shape of the cam 8 also shows that the rising ramp of the power stroke is much longer than the falling ramp of the reset clock - the working stroke 21 occupies a larger angular segment than the Rückholakt 22. The cause for this is that the power strokes 21 for Continuous action on the impeller 3 and the backstops 27 must overlap - the one stroke 21 so Gerate is still active when the other 21 is just starting to be active.

In the arrangement of the pendulum arm 10 it can be seen that these are offset radially to each other. The distance is in the illustration shown half a sinusoidal length of a cam 8. This can be dispensed with a second cam 7 because the Abtastarme 13 activating cam 8 is always at the correct distance from the next Abtastarm 13 and the next Abtastarmlaufrolle 14.

The pendulum arms 15 shown in the position of the fastest gear can be pulled out of this position by the Bowden cables 25 - downwards. The provision of the pendulum arms 15 is reversed by a return spring 28th The Bowden cables 25 are adjusted in parallel in case of need by the electric servomotor 30. Of course, this servomotor 30 could of course also be replaced by, for example, a pneumatic actuator or by a simple manual adjustment mechanism.

The wheel computer 31, which controls the servomotor 30, is programmed by the driver to a specific desired value. Such a desired value can be, for example, the pedaling frequency. At the sensor 33, the wheel computer 31 constantly measures the actual value; if, for example, the desired value is not reached, the cycling computer 31 regulates the transmission ratio of the transmission via the servomotor 30 until the actual value and the desired value are again covered.

Fig. 2 shows the section A-A and the basic structure of the pendulum axes 10 with the scanning arms 13 connected thereto and their spatial position to the bicycle frame 4 and the cam 7. The view shown is to be understood from a bird's eye view. In the illustration, the implementation of the two radially and in the depth offset pendulum arms 15 is shown. The pendulum arm 10 open into a bearing block, which in turn is rigidly connected to the bicycle frame 4.

In the illustration, the mechanical point of attachment of the transmission elements 26 to the pendulum arms 15 is not visible.

As an alternative to FIG. 1, the same transmission is shown in FIG. 3 with the difference that it is not possible to displace a pendulum arm, but rather an adjusting part 108, which canted to the non-displaceable pendulum arm 104. In principle, the same happens when a workload occurs, as in Fig. 1: It we by this load an automatic tilting of an adjustment 108 to Hubgeber - made in this case the pendulum 104. In the illustration, it can be seen that a separate cam 105 is provided for each of these non-displaceable pendulum arms 104. This second cam 105 is shown by dashed lines, on the representation of the second pendulum 104 and transmission element 109 has been omitted because these parts cover almost completely in the side view.

All other functions with regard to adjusting the adjusting part 108, driving the adjusting Bowden cables, the cycling computer control, overload spring 35, etc. coincide with the variant according to FIG. 1 FIG. 4 shows a pendulum arm 15 which is moved via Bowden cables 25 and which generates the highest possible stroke on the transmission element 26 in the position shown. The Bowden cable 25 brings the pendulum arm 15 via the cable 25 down - thus reducing the ratio infinitely. Conversely, the return spring 28, the pendulum arm 15 back up - as far as this is left by the rope 25.

However, this return spring 28 shown exercises not only a restoring force on the pendulum arm 15 due to their geometric shape and reason of the suspension points on the pendulum arm 10 and the pendulum arm 15. Rather, it also exerts a force which the restoring force of freewheel 27 - and thus the transmission element 26 is directed opposite. This ensures that the pendulum arm 15 is actually released in the restoring cycle 22 from the cant to the pendulum arm 10 and, if necessary, can be adjusted at any time during each reset clock 22.

FIG. 5 shows a pendulum arm 15 which is moved via a hydraulic cylinder / piston / connecting rod 24 and which produces a central stroke 20 on the transmission element 26 in the position shown. The connecting rod brings down the pendulum arm 15 - thus reducing the transmission ratio steplessly. Conversely, the return spring 28, the pendulum arm 15 back up - as far as this is left by the rope 25.

This shape of the return spring 28 exerts ground of the suspension points on the pendulum arm 10 and the pendulum arm 15 not only a restoring force on the pendulum arm 15. Rather, it also exerts a force which the restoring force of freewheel 27 - and thus also transmission element 26 is directed opposite. This ensures that the pendulum arm 15 is actually released in the reset cycle from the cant to the pendulum arm 10 and, if necessary, can be adjusted at any time during each reset clock 22.

In Fig. 6 it is shown with what simple link 41 of the cables 25 a compensating "spring action" is achieved to be adjusted pendulum arms 15. Such a spring buffer is required because one of the two pendulum arms 15 during operation - ie during the power stroke 21 - unadjustable Now, if an adjustment is made at a blocked pendulum arm 15, the star means 42 of the cable link 41 shifts towards the blocked pendulum 15. In the power stroke 21 of the corresponding pendulum arm 15 is released again, the pendulum arm 15 opens its tilting to Pendelarmachse 10 and the "missed adjustment" is made up - the link 41 searches automatically against the star center 42, is reset there. In this Fig. 6 is also clearly the arrangement of the heavy duty springs 35 can be seen. These heavy duty springs 35 virtually replace the "small gears" of a gearbox and begin to expand beyond a certain heavy load, which no longer transfers the entire stroke of the transmission element 26 to the freewheels 27. The lost path stored in the heavy duty spring 35 becomes the following one Reset clock 22 is forwarded via the ramps of the reset clock 22 on the cam disk 7 to the adjacent transmission element 26 as additional traction force.This staggered delivery of the work output by means of intermediate storage in a metallic spring 35 is known to work loss-free.

In Fig. 7 we show a specific application of the invention, in which the adjustability of the pendulum arm 15 is completely dispensed with and only the dynamic load extensibility of a heavy duty spring 35 is used for the adjustment of the transmission ratio from the transmission. For this purpose, a device was created, which allows an adjustment of the spring force from the outside. In the illustration shown, this adjustment of the spring force by means of a hydraulic cylinder 39. Other, whatever kind of methods for adjusting the spring force are conceivable and thus do not leave the subject invention.

In Fig. 8, the basic structure of the entire freewheel 27 and the hub 2 is shown in section. Because of the application of sprag freewheels 46, the freewheel core 45 consists of a simple rotationally symmetrical tube. The two outer rings 47 with their form-fitting circumferential pinions 48 consist of simple rotationally symmetrical rings 47. This is technically highly advantageous. The wheel hub 2 is positively connected along a common center axis to the freewheel core 45 with this. Freewheel core 45 and hub 2 are ball-mounted for outer termination on the wheel axle 49.

FIG. 9 shows that the revolving cams 8 are not the same, but are lower 53 in the position 51 in which the pedals are in the OT / UT to the driver. This ensures that the UT / OT passage of the pedals 6 is faster than that in which the pedals 6 can accommodate the maximum pedal load 52. This device is advantageous for the driver, since its utilization is more complete and uniform even within one pedal turn. This provides ergonomic massive benefits. Legend:

1. Input shaft / pedal crankshaft 32. Hand operable. adjusting

2. Output shaft / hub 33. Cadence sensor /

3rd impeller torque sensor

4. Bicycle frame with the pedestal 34. Heart rate sensor / other for the pendulum arm axes 10 sensors for physiological data

5. Bottom bracket 35. Lastdynamic spring element

6th treadle (load spring)

7. Cam 36th force vector of the return spring for

8. Cam cam Release the pendulum arm tilt

9. Total pendulum arm (including 13 + 14) 37. Half sine length (1/2 sinus angle)

10. Pendulum arm axis of a cam cam

11 pendulum arm passage 38. Einschubbohrung for the spring 28th

12. Swivel bearing of the pendulum arms 39. Hydraulically adjustable element

13. Abtastarm on the pendulum arm axis for biasing the spring 35th

14. Scanning arm rollers for the 40th return spring for the return stroke Cam disc (for transmission elements,

15. Sliding pendulum arms or overrunning clutches + pendulum arms) Adjustment parts 41. Buffer element / star-shaped

16. Changeable length of the rope link pendulum arm 42. Link point in

17. Transmitter element center point Suspension point on pendulum arm 43. Bowden cable sheath (end points on

18. Verkantnasen fixed in the pendulum arm vehicle) implementation 44th Single Bowden cable from

19. sliding flanks for preventing an adjusting member 30 for tilting in the return stroke connecting point 42

20. Pendulum arm adjustment path 45. Rotation symmetric

21. Arbeitshub freewheel core

22. Return stroke 46. Clamp body freewheels

23. Longitudinal axis of Verstellweges 47. rotationally symmetrical Außenvom Pendelarm rings to sprag freewheels

24. Hydraulic or pneumatic 48th sprocket or timing belt adjuster disc on the outer rings 47

25. Adjustment Bowden cable to the individual 49. Impeller axle Pendulum arm 15 50. Pedal pedal longitudinal axis

26. Flexible transmission elements 51. least favorable angle between

27. Direction-dependent load-bearing driver leg and clutch mechanism Pedal longitudinal axis

28. Pendulum arm return spring 52. Cheapest angle between

29. spring element between the auflastendem driver leg and Verstellzügen 25 Pedal longitudinal axis

30. Electromotive, hydraulic 53. Minimum cam height or pneumatic servomotor 54. Maximum cam height

31. Bicycle Control Computer 103 pendulum arm axles

104 pendulum arm

105 cam

106 cam cam

108 adjustment part

109 transmission elements

110 direction-dependent couplings

112 Suspension point of the transmission element on the adjustment part

125 pedal

128 bicycle frames

130 pendulum arm rollers

138 stroke of the pendulum arm

144 Center position of the pendulum arm

Claims

claims:

1. Transmission with a continuously variable ratio between an input shaft (1) and an output shaft (2) having at least two about an axis (10) pivotally mounted pendulum arms (9) by the rotation of the input shaft (1) and the thus positively connected cam discs (7) in a uniform, mutually and mutually overlapping in the working cycles lifting movement (21) are offset by means of two adjustment parts (15) along the pendulum arm adjustment (20) are displaceable or by means of two pendulum arms ( 15), which are displaceable by the pendulum axis (10) along the pendulum arm adjustment path (20), in the so variable variable reciprocating movements of the two transmission elements (26) converts and this alternating movement of the two directions of rotation dependent couplings (27) is transmitted , where it in turn converts into a continuous and uniform rotation of an output shaft (2), characterized gekennz eichnet that each pendulum arm (15) under working load automatically canted to the designated Verkantnasen (18) in the pendulum arm passage (11).

2. A transmission according to claim 1, characterized in that the adjusting parts (108) tilt by the occurrence of a via the transmission elements (109) applied work load frictionally to the respective pendulum arm (104) and the adjusting parts (108) so much during the working stroke (140) dynamically and automatically fixed immovably to the respective pendulum arm (104).

3. A transmission according to claim 2, characterized in that the force or positive engagement between the adjusting part (108) and pendulum (104) with elimination of the workload during Rückstellhubes (141) automatically at least as far as dissolves when the respective adjustment part (108 ) if necessary by means of a longitudinally to the pendulum arm longitudinal axis (142) directed, far below the average of the adjustment (108) transmitted tensile force, move.

4. Transmission according to claims 2 and 3, characterized in that on the adjusting part (108) of the suspension point (112) for the transmission element (109) sufficiently - in one of the two directions to the pendulum arm longitudinal axis (142) - removed from that area ( 13) is mounted, within which the adjusting part (108) with the two traction loaded and opposite inner edges (114) on the pendulum arm (104) tilted.

5. A transmission according to claim 1, characterized in that a pendulum arm (15) due to an occurring workload immovable from the consequently acting on him force to the provided tilting lugs (18) in the pendulum arm implementation (11) tilted.

6. Transmission according to claims 1 to 5, characterized in that via sensors (33, 34) data detecting bicycle control computer (31) the transmission automatically automatically adjusted by motorized adjusting member (30) the pendulum arms (15)

7. Transmission according to claims 1 to 6, characterized in that the adjustment of the pendulum arm length (16) or the adjusting parts (108) by means of hydraulic, pneumatic, electromotive adjusting mechanisms (24) or by Bowden cables (25).

8. Transmission according to claims 1 to 7, characterized in that from the pendulum arm-return spring and a force vector (36) for releasing the jam between pendulum arm-passage (11) and pendulum arm (15) is generated.

9. Transmission according to claims 1 to 7, characterized in that the two pendulum arms (11 or 104) are each on a separate pendulum axis (10 or 103) which are by half a sinusoidal length or one and a half, two and a half, etc. Sinuslängen (37) of a cam plate (8 or 106) are radially offset from each other.

10. Transmission according to claims 1 to 9, characterized in that the two rollers (14 or 130) of the scanning arms (13) together on a single cam (7 or 105) run.

1 1. A transmission according to at 1 to 10, characterized in that the cam disc (7 or 105) with their plurality of cams (8 or 106) in the region in which the pedal pedal longitudinal axis (50) has a most unfavorable force vector angle ( 51) to the overburden leg having the lowest cam heights (53) and, conversely, in the region of the most favorable force vector angle (52), the maximum cam heights (54).

12. A transmission according to claims 1 to 11, characterized in that during an adjustment of the alternate Verstellblockiertheit the pendulum arms (15) and the adjusting parts (108) resulted, not directly on the pendulum arm (15) or on the adjusting part (108) executable adjustment (8) cached in a mechanical buffer member (41) and this mechanical buffer member (41) consists for example of a star-shaped cable connection or the Bowden cable sheaths (43) or the Bowden cables (25), which have a resilient elasticity.

13. Transmission according to claims 1 to 13, characterized in that each transmission element (26 or 109), a spring element (35) is interposed, which extends from the occurrence of a given load lastdynamisch reversible.

14. A transmission according to claim 14, characterized in that the respective load spring (35) is dynamically deformed in the working stroke (21) and the spring tension so stored in the next return stroke (22) labor-efficient, the vehicle propulsion is additionally supported again.

15. A transmission according to claims 15 and 16, characterized in that the dynamic load-spring element (35) in a variant according to the invention in its spring force from the outside is adjustable and such a spring force adjustment, for example, by a hydraulic element (39), which the bias of Spring element (35) increases or decreases, is accomplished.

16. Transmission according to claims 1 to 16, characterized in that the direction of rotation dependent coupling device (27 or 110) has a rotationally symmetrical freewheel core (45) on which two sprag free running (46) are arranged, each of a rotationally symmetrical ring (47 ) are sheathed.

17. A method for operating a transmission with a continuously variable ratio between an input shaft (1) and an output shaft (2) having at least two about an axis (10) pivotally mounted pendulum arms (9) by the rotation of the input shaft (1 ) and the thus positively connected cam discs (7) in a uniform, mutually and mutually overlapping in the working cycles lifting movement (21) are offset, which by means of two adjustment parts (15) along the pendulum arm-adjustment (20) are displaceable by means of two pendulum arms (15), which are displaceable by the pendulum axis (10) along the pendulum arm adjustment path (20), in which so variable variable reciprocating movements of the two transmission elements (26) converts and this alternately movement of the two directions of rotation dependent couplings ( 27), where they turn into a continuous and uniform rotation of a Ausgangswe (2) converts, characterized in that for weight and size reduction of such a bicycle transmission each of the pendulum arms (9) within a crank rotation several, but possible a plurality of rashes makes by on the, the or the pendulum (e) ( 9) driving (s) cam (7) a plurality, but if possible a plurality of cams (8) are provided.

18. A method for operating a transmission according to claim 14, characterized in that direction of rotation dependent couplings (27 or 110) are used, which the fiction, specifically high switching frequencies of up to about fifty Hz (50 opening and closing operations / second) and with a closing distance of less than 3 ° of the rotation of the outer rings (47) to the freewheel core (45) can handle.

19. A method for operating a transmission according to claims 14 and 15, characterized in that direction of rotation dependent couplings (27 or 110) are used, which losbrechbrechfrei the frictional connection between the outer ring (47) and freewheel core (45) solve.

20. A method for operating a transmission according to claims 14 to 16, characterized in that to cope with the requirements of the invention according to the direction of rotation dependent couplings (27 or 110) sprag clutches (46) are used.