Patent Application
20190061871
The invention relates to a bicycle gearing system with the characteristics listed in the general description in claim 1.
Such gearing assemblies increase the torque of the power generated by the rider. To do this, the gearing system is installed on a bicycle, and a gear wheel, such as a toothed wheel, conveys the torque generated by the rider through a chain or toothed belt to the rear wheel.
The prior art for this is described in DE 10 2010 033 211 B4, with a bicycle gearing system in which the sun gear, planet gear, and drive axle are all contained inside the same axle housing and the drive arm is supported by a guide roller in a guideway that is also contained in the drive housing. An obvious disadvantage of known gearing assemblies is that the feet do not achieve a smooth motion while pedaling, because of differing accelerations during each rotation of the pedal crank, and therefore the rider perceives the pedaling motion as “stomping”.
EP 1 863 699 B1 describes an oval chain sprocket, which has its maximum effective diameter in the area of the highest power generation, i.e., at approximately the 90° position of the pedal crank. That is the position where the maximum torque should be applied by the rider and can be transferred to the chain. In practice, however, the oval chain sprocket also leads to an uneven pedaling feel, with higher and lower foot acceleration phases during one complete rotation of the oval chain sprocket.
The invention is therefore intended to fulfill the objective of improving this type of bicycle gearing system in such a way that the rider experiences a rounder pedaling feel.
According to the invention this goal is achieved by the distinguishing features described in Claim 1. An oval shape is understood to be a closed double convex curve, constantly differentiable in the same plane. Therefore, the oval shape of the toothed wheel is aligned with the spur gear unit in such a way that downward-pressure accelerations of the foot on the four-bar linkage while pedaling are reduced. The position of the pedal crank on the oval chain sprocket changes during constant rotation.
The bicycle gearing system according to the invention makes it possible to achieve maximum torque through the use of a power transmission in which a power-supplying element is guided synchronously in a uniform track. The power-supplying element here is the foot of a bicycle rider. The uniformity results first from the continuous convex shape of the track, and secondly from the reduction of absolute accelerations in the area of the power-supplying element due to the oval gear wheel. During a gear cycle, the components involved in transmitting torque, such as cranks and pedal cranks, do not change their lengths but instead simply deviate from each other.
Preferably, the toothed wheel has a greater main axis diameter and a smaller secondary axis diameter, so that the main axis diameter in the toothed wheel rotation direction is always offset, at an angle of 60-130°, from a connecting line running between the central bearing axis and the planet gear bearing axis. An embodiment in which the angle is 70-120°, and in particular 80-110°, is especially preferred. An even more optimal version calls for the angle to be 90-100°. In these angle ranges, an especially comfortable pedaling feel is achieved without any stomping motion of the weight-bearing foot.
It is desirable for the four-bar linkage to include a carrier plate that pivots on the central bearing axis, and for the planet gear to pivot eccentrically on that carrier plate. Advantageously, a central section of the carrier plate is connected in such a way that it cannot twist to a central shaft located on the central bearing axis. In this configuration, the carrier plate and the central shaft form a single assembly and rotate together around the central bearing axis when the pedal crank(s) is(are) operating. Preferably, the central shaft is placed concentrically inside the first and/or second sun gear. The advantage of this embodiment lies in the fact that the gearing system has especially compact dimensions in the axial direction of the central shaft.
According to a first preferred embodiment, the four-bar linkage has three swivel joints and one sliding joint. As an alternative to that embodiment, the four-bar linkage can have four swivel joints.
Preferably, a first swivel joint is located between the planet gear and the carrier plate.
The first swivel joint allows the planet gear to rotate around its assigned bearing axis.
Advantageously, a second swivel joint is located between the crank and the pedal crank. The second swivel joint allows the crank to rotate relative to the pedal crank.
In addition, the four-bar linkage can have a coupling assembly located between the carrier plate and the pedal crank by means of at least a third swivel joint.
It is advantageous for the coupling assembly to include the sliding joint. The sliding joint can be a linear guide, for example. A linear guide is understood to be a mechanical guiding element used to move one assembly in a straight line with respect to another assembly. The linear guide has a certain degree of freedom. This means that the linear guide must also absorb any pull-out torque that occurs. Preferably, the linear guide includes at least one guideway with a slide that runs in it. A guideway is understood to comprise linear carrying and guiding elements placed individually or in pairs that are parallel to each other. During operation, the slide is connected inseparably to the at least one guideway and runs in it.
Preferably, the linear guide is attached in one permanent spot to the carrier plate, so that the slide travels back and forth in a radial direction with respect to the central bearing axis when the bicycle gearing system is rotating. Advantageously, the third swivel joint is located between the pedal crank and a slide in the linear guide.
Instead of the slide joint, the coupling assembly can include a swing arm supported by the third and a fourth swivel joint. A swing arm is understood to be a rigid assembly, one end of which swings out from a central position in two directions relative to a support point. This results in the advantage that the use of a slide joint, which is kinematically optimal but susceptible to failure in practice, can be avoided and all of the bearings used can be configured as pivot bearings. In this version, the four-bar linkage is driven by the continuously rotating crank. The crank always has the shortest length in the four-bar linkage. The four-bar linkage is driven by the swing arm, which moves with an oscillating motion around the fourth swivel joint. The crank and swing arm are connected to each other by a coupling formed from a section of the pedal crank between its second and third swivel joints. Both the crank and the swing arm pivot on the carrier plate, with the crank connected rigidly to the rotating planet gear. The third swivel joint, instead of the linear motion of a slide joint, simply has a linear motion similar to a circular orbit with a very large radius.
Preferably, the third swivel joint is located between the pedal crank and the swing arm, and the fourth swivel joint between the swing arm and the carrier plate.
It has proven to be especially favorable for the crank and the swing arm to be located on the same side of the pedal crank. The pedal crank thereby lies on the outside of the bicycle gearing system in an axial direction from the central shaft, which allows for an exceptionally low Q factor. Advantageously, the crank and the swing arm are then also located in an axial direction from the central shaft, between the carrier plate and the pedal crank.
Preferably, the fourth swivel joint is positioned on a center perpendicular placed vertically on a connecting line running between the bearing axes of the third swivel joint in its 0° and 90° positions. The two bearing axes, when in their end positions, thereby lie on a straight line that goes through the central bearing axis of the bicycle gearing system. The four-bar linkage then represents a central crank rocker mechanism.
Advantageously, the toothed wheel is connected rigidly to the carrier plate and/or central shaft, so that the torque applied by the rider to the bicycle gearing system is transferred to the traction element, in particular a bicycle chain, with as little loss as possible.
The sun gear and the planet gear preferably have a fixed transmission ratio of 1:2. This causes the relative positions of the spur gear unit and the four-bar linkage to remain always constant with respect to each other during one gear rotation.
With the bicycle gearing system installed, the spur gear unit can include a stationary second sun gear, wherein the sun gear and the second sun gear can be mounted on opposite sides of a frame element and have a second planet gear, running from the second sun gear and rotating around a second planet gear axis, which interacts with a second four-bar linkage so that the second four-bar linkage includes a second crank that is connected rigidly to the second planet gear and rotatably to a second pedal crank. This results in a bicycle gearing system that has an outside sun gear and a symmetrical four-bar linkage encircling the sun gear on each side of a centrally placed central shaft. This embodiment corresponds to conventional bottom brackets that have a pedal crank on both sides of the bicycle frame.
Preferably, the second planet gear and the second four-bar linkage are offset by 180° from the planet gear and the four-bar linkage. This makes the four-bar linkage and the second four-bar linkage run symmetrically around the central bearing axis, so that, for example, the pedal crank is at the lower dead point and the second pedal crank is at the upper dead point at the same time.
For better comprehension, the invention is explained in more detail below based on 5 figures. The figures show:
Both
On a first side 61 of the frame element 60, a stationary sun gear 11 can be seen, which together with a planet gear 12 forms a spur gear unit 10, as well as a four-bar linkage 20 interacting with the spur gear unit 10. On a second (covered here) side 62 of the frame element 60 there is a second sun gear 11a that interacts with a second four-bar linkage 20a (see
Both four-bar linkages 20, 20a relate to a central shaft 14, which runs crosswise through the frame element 60, with its front face visible. The central shaft 14 defines a central bearing axis y1 of the bicycle gearing system.
A carrier plate 23, 23a is mounted on each axial end section of the central shaft 14 in such a way that it cannot twist, and it rotates in a circle together with the central shaft 1 when the bicycle gearing system is in operation. The connection between the carrier plate 23 and the central shaft 14 is made in a centrally located section of the carrier plate 23. In a section of the carrier plate 23 lying outside of that, the planet gear 12 is supported against the carrier plate 23 by a first swivel joint 40 in such a way that it can rotate.
A crank 21, 21a is either attached to the planet gear 12, 12a in such a way that it cannot rotate or forms part of a one-piece assembly together with said planet gear. The crank 21, 21a protrudes radially, offset axially, from the planet gear 12, 12a, and engages the pedal crank 22, 22a rotatably by means of a second swivel joint 41 (see
A kinematic coupler 24, 24a in the shape of a swing arm 25, 25a is also connected rotatably to the carrier plate 23. A first end of the swing arm 25, 25a engages the pedal crank 22 on the side related to the frame element 2 by means of a third swivel joint 42. The opposite end of the swing arm 25 is fastened rotatably to the carrier plate 23 by means of a fourth swivel joint 43.
Power is provided by the bicycle rider through pedals (not shown) to the two pedal cranks 22, 22a located axially to the central shaft 14 on the outsides of the bicycle gearing system (see
A toothed wheel 30 engages the carrier plate 23 form the outside and transfers the rotational motion of the bicycle gearing system to a traction element in the form of a chain 31.
The toothed wheel 30 has an oval shape spanned by a main axis diameter DH and a secondary axis diameter DN, with the main axis diameter DH intersecting a connecting line 13 at an angle α of about 90°. The connecting line 13 always intersects the central bearing axis y1 of the central shaft 14 and the planet gear bearing axis y2, y2a of the planet gear 12, 12a, regardless of the orientation of the spur gear unit 10. This orientation of the oval toothed wheel 30 is especially effective in reducing accelerations of the foot, in particular around the area of the 90° position.
The lengthwise view in
The central shaft 14 runs concentrically inside the sun gears 11, 11a, and in the area of the first and second sun gears 11, 11a it is attached to each of them by means of a central shaft bearing 15 that allows it to pivot.
The guideways 53 are fastened permanently to the carrier plate 23 and rotate around the central bearing axis y1 when the bicycle gearing system is operating in rotation direction M. The slide 52 is also connected rotatably to the pedal crank 22 through the third swivel joint 42.
In
In the 90° position of the pedal crank 22 according to
| Number | Date | Country | Kind |
|---|---|---|---|
| 10 2016 001 660.4 | Feb 2016 | DE | national |
| 10 2016 004 888.3 | Apr 2016 | DE | national |
| Filing Document | Filing Date | Country | Kind |
|---|---|---|---|
| PCT/EP2017/053083 | 2/10/2017 | WO | 00 |
