Bicycle.

The invention relates to a bicycle with a frame that exceeds pedals with crank arms, which are fastened to a rotatably mounted shaft, preferably driven rear wheel is supported on a held in a steering fork, and on a front wheel having a^yhaving a freewheel hub provided.

In the known and currently in use bicycles a remotely located from the hub bottom bracket is provided, which receives the shaft provided with crank arms, which is connected via a chain drive to the rear wheel hub. This chain drive causes often despite an elaborate chain guard a Schmutzbeaufschlagung of the pedals person operating. Also known is the risk that clothing of the pedals person operating between the chain and sprocket are drawn, which will bring a substantial damage, but also an extremely high risk of accidents with them. As a result of this arranged between front and rear bottom bracket also arises in the known arrangements a relatively large length of the vehicle and, consequently, a relatively large vehicle weight. On the other hand, about the axis of the steering fork to fear a relatively large bulk also during folding of the front wheel, as this the front wheel runs on the arranged between front and rear bottom bracket or attached thereto pedals and thus can not be recovered by 180 °. Another disadvantage of the known arrangements is also seen in the fact that the remote of the rear hub pedal arrangement provides a more or less uniform distribution of the load on the rear wheel and the front wheel, which not only requires an equally strong framework through education and thus causes a high weight but at the same time also requires relatively large forces to operate the steering, which can be tiring in the long run. A special disadvantage of the known arrangements is that here the pedals person operating associated saddle for Bewerkstel-actuating an approximately useful load distribution can not be located directly above the bottom bracket so that the pedals serving person is not easy to operate the pedals can come down, which would be expected the highest power and a healthy posture.

On this basis, it is therefore an object of the present invention, while avoiding the disadvantages of the known arrangements to improve a bike the opening paragraph by simple means so that it can be designed as a lightweight bike that works without chain drive and in which not only the. Area between front and rear wheels is not installed, but the same time from the pedals person operating requires a comparatively small effort.

This object is achieved in that the rear hub of the provided with crank arms wave penetrated centrally by and by at least one transmission gear unit is rotationally hereby connected, and that the shaft is mounted to the hub projecting laterally beyond bearing bodies, over which the rear wheel out of the shaft with the bicycle frame is screwed, which has an approximately vertically above the rear wheel hub and arranged saddle approximately vertically extending rear supports.

Here is thus ensured in an advantageous manner that the pedals person operating virtually vertically above the rear wheel hub is seated so that the load is taken up by the rear wheel for the most part, which on the one hand an excellent soil friction in the region of the rear wheel and on the other hand a ieichte steerability in the field of front wheel accomplished. At the same time it is ensured in an advantageous manner that the pedals operator can simply step down when the pedals, which is expected to provide high performance, since in this case the pedals easily be seen actuated by shifting your weight. The inventive measures thus ensure that the normal walking upright posture in which the person can provide a high performance, is also retained during cycling, which thus can be expected Stung not only high Lei, but also enables a healthy posture, because the abdomen is not compressed. Another advantage of the inventive measures can be seen in the fact that the frame can be shortened compared with known arrangements while relatively easily formed in the less heavily used areas. Due to the weight supporting virtually above the rear wheel hub bending stresses of the struts also be largely eliminated, so that can be achieved overall a highly desirable weight savings. Since the area between front and rear is not blocked due to chainless drive the rear wheel, the front wheel can here practically 180⁰ are allocated, which can achieve a high degree of compactness in transport and stop state in connection with the Baulängenverkürzung already reached, which is beneficial to the space requirements.

According to a particularly preferred development of the primary measures the hub and the shaft can be mounted on both sides, each with a bearing on the side provided bearing bodies, which enables a simple structure and thus an economical manufacture and assembly and yet ensures reliable force absorption. Another expedient measure may consist in that the hub shaft passing through the formation of a coaster brake is provided directly to a brake thread or the like, in which engages a brake body, by means of which a cooperating with a cone brake shell for engaging the hub can be brought. As a result, the direct assembly of the brake the thread on the shaft is ensured that a high braking force is achieved, since no puts into effect by the gearbox reduction ratio is taken into account.

Further expedient refinements and advantageous developments of the primary measures arising from the remaining dependent claims in conjunction with the following description of some embodiments.

In the drawings described below show:<ul><li>Figure 1 shows an overall view of a bicycle according to the invention,</li><li>Illustrative embodiments with input gear ² and 3, and _Rü_ckt_ritt_bRemse basis of a longitudinal section through the through put of the pedal crankshaft rear hub,</li><li>Figure 4 shows an embodiment with a multi-speed transmission in Figures 2 and 3 corre-sponding representation,</li><li>Figure 5 shows an embodiment of a continuously variable transmission in Figures 2 and 3 and a corresponding representation</li><li>Figures are variants of switching devices for ⁶ to 8 different gearbox version in Figures 2 and 3 corresponding representation.</li></ul>

The bicycle shown in Figure 1 consists of a designated as a whole by 1 frame, which is on a front wheel 2 and a rear wheel supported 3rd The front wheel 2 is accommodated in a steering fork fourth The rear wheel 3 is directly above attached to the crank arms 5 pedals 6, that can be driven without a chain drive. For this purpose the crank arms 5 are connected via an indicated at 7 shaft, which passes through the position indicated at 8 rear hub and rotationally hereby be coupled, is performed as described below in more detail. The frame 1 is supported on the rear wheel with fork-mounted rear supports 9, radiating from the shaft 7 receiving hub 8 approximately vertically upward and at the upper end a saddle 10 is arranged on which the pedals may 6 person operating sit , Since the saddle 10 above which the crank arms is practically vertically arranged 5 connecting shaft seated on the saddle 10 person, the pedals 6 operate in virtually upright position, which simply can be done by shifting your weight. The front wheel 2 is relatively lightly loaded, allowing easy steering. It is sufficient if only the case virtually claimed to buckling rear supports 9 are correspondingly strongly by formed. The remaining frame parts can be relatively easily performed.

The rear wheel 3 is, as best seen in Figures 2 and 3 can be seen outside of the hub 8 passing through the shaft 7 bolted to the rear supports 9 or having attached thereto receiving rings 11, where further frame parts, such as crossbars can attack etc.. The holding rings 11 are rear side, the front sides of the hub 8 via projecting bearing body 12 or 13 associated, which are provided with corresponding holes for receiving the connecting screws 14 shown in FIG. 2 The bearing bodies 12 and 13 are provided with an aligned central bore in which the shaft 7 is freely rotatably supported by ball bearings. Preferable is a bearing assembly according to Figure 3, in which each side only is provided a bearing. In order to accomplish a simple adjustability of this shaft bearing the shaft 7 on the one hand be provided with a fixed bearing ring 15 and the other with an adjustable as by a thread bearing ring, as Figure 2 shows. In the embodiment illustrated in Figure 3, both bearing rings are 15 or 16 adjustable and fixable by means of a locknut.

The crank arms 5 interconnecting shaft 7 is connected via a here by a whole with 17 designated transmission unit, which is to effect a speed ratio with the hub. 8 For this simple can be provided a gear transmission. In the embodiment shown in Figure 2 or 3, a planetary gear is provided to form the catchy gear formed by the transmission unit 17, the same results without further action directions of rotation of the shaft 7 and hub 8 advantageously. The shaft 7 is this centrally located in the hub 8 and provided with a here expediently designed as radial planetary gear holder 18 which is to be equipped on the periphery with three planet gears of indicated at 19 Art. The planet gears 19 are rotatably mounted on the associated pins 20 and are on the one hand with a frame-mounted, ie held outer ring gear 21 and secondly to a freely rotatably mounted inner tooth wreath 22 engaged. The outer ring gear 21 is formed both in Figure 2 and in Figure 3 simply to a laterally projecting collar 23 of the adjacent, bolted to the bicycle frame bearing body 12th The inner, driven gear 22 is integrally formed on a ring body designated as a whole with 31, which in turn is freely rotatably mounted on the shaft. 7 For this purpose, appropriate, as best seen in Figure 3 can be seen, find a needle bearing use.

In the embodiment of Figure 2, the annular body 31 to transmit torque to the hub 8 with a on the side opposite the gear unit 17 side projecting bushing 24 is provided having a circumferential thread 30 and is screwed onto the freewheeling clamp body 25, the hub side, a drive flange is associated with 26th the freewheel body 25 and the driving flange 26 may be provided with opposing inclined surfaces In order to accomplish a large-scale plant. By operation of the pedals 6 during the normal driving operation, the shaft 7 and thus of the planet carrier 18 are rotated. The planet gears 19 thereby roll off on the frame-side outer sprocket 21 and drive the inner ring gear 22, which in an advantageous manner, the rotation of shaft 7 and ring gear 22 match. As a result of thereby brought about rotary movement of the coupled via the thread 30 with the freewheel clamp body 25 sleeve 24 of the freewheel clamping body is brought to rest on the hub-side driving flange 26, thereby driving the hub 8 in a direction of rotation of the shaft is 7 corresponding direction of rotation. To form a coaster brake, the annular clamping freewheel body 25 is surrounded by a casing brake 27, which is associated with a frame 28 fixed meeting cone in the embodiment of FIG. 2 The run-up cone 28 here is simply formed on the lateral bearing body. 13 Once the brake shell 27 runs 25 by corresponding movement of the standing in threaded engagement with the driven sleeve 24 freewheel body on the run-up cone 28, there is a radial expansion and thus a corresponding abutment on the hub to be braked eighth

In the embodiment shown in Figure 3 to the annular body 31 through peripherally arranged freewheel members 32 as idlers or pawls be coupled, resulting in a very simple and compact construction allows a conventional type with the hub. 8 This freewheel members 31 accomplish that no torque is transmitted to the shaft 7 of the hub 8 and on the other also takes place when receding and when turning back the shaft 7 about for the purpose of braking any entrainment in the range of the freewheeling rollers or pawls. To form a coaster brake can-shaft 7 may be provided in one embodiment of this kind in a particularly advantageous manner with a directly molded thread 67 or similar guide surfaces, into and engages an annular brake body 68 which in a known manner a brake shell 69 actuated, the runs in the reverse rotation of the shaft 7 on one here also is integrally formed on the bearing body 13 cone, thereby expanded and is brought to the braking-system to the hub eighth For rotation of the brake casing 69 can here unspecified but Darge presented to provide pin-slot connection in the region of the bearing body. 13 Direct absorption of the brake body 68 on the central driven shaft 7 here yields seen a high braking force, since no reduction takes place, which would be the case with a current via a transmission unit 17 power flow.

The hub 8 is, as shown in FIGS 2 and 3 can be seen particularly well, each supported on two ball bearings. In the embodiment shown in Figure 3, the hub 8 is supported by two ball bearings directly on the fixed bearing members 12 and 13 respectively. In the embodiment of Figure 2, the hub 8 is supported on the one hand on the bearing body 13 and the other part on a radial support flange 29 of the driven annular body 31, which gives an excellent support in the vicinity of the driver flange needed here 26th The support flange 29 may be supported in turn on the adjacent collar 23 of the bearing body 12, which simultaneously results in an exact axial fixation of the driven inner ring gear 22 receiving the annular body 31 in an advantageous manner.

In the embodiment shown in Figure 4, the drivable via the pedals 6 shaft 7 is drivingly connected via a three-course, as a whole with 47 designated transmission to the wheel hub. 8 At the output of said transmission a wave is again 7 surrounding, freely rotatably disposed thereon bearing ring body 31 which cooperates via freewheel members 32, about idler rollers or pawls etc. to the hub. 8 Said gearbox 47 has an approximately perpendicular to the shaft 7 disposed a hollow shaft 43 which is freely rotatable in a housing-fixed component, here advantageously the lateral bearing body 12, stored. The hollow shaft 33 may be cantilevered. In the illustrated embodiment the hollow shaft 33 is supported on two sides, for which purpose the bearing body 12 has a suitable, cross-sectionally approximately U-shaped profiling. The hollow shaft 33 is equipped at its end of the shaft 7 facing to a bevel gear 34 which cooperates with a seat on the shaft 7 Helical 35th On the hollow shaft 33 a plurality of, here three wheels 36 are arranged side by side at different distances from the axis of the shaft 7 and thus also from the axis of the shaft 7 concentrically surrounding the annular body 31 to form a plurality of passages. The wheels 36 are freely rotatably mounted on the hollow shaft and provided in the region of its bearing bore each having a groove 37th These wheels 36 are individually connected to the hollow shaft 33 rotationally connectable. For this purpose, the hollow shaft 33 is penetrated by a outward guided shift rod 38, which is connected at its projecting into the hollow shaft 33 end via a rotating joint with a displacement member 39th This sliding member 39 is provided with a nose 40, which engages through a slot-shaped recess 41 of the hollow shaft 33 and into the groove 37 in each of a wheel 36th The shift rod 38 can here easily by means of a not shown control cable, which is about out to bike handlebars, against the force of a return spring indicated at 42 are operated. Since the hollow shaft is mounted in a frame-mounted component 33, the Schaltungszug readily fixed to the frame can be embarrassed. With the help of displacement member 39 can be seen in each one of the wheels 36 rotationally connected to the hollow shaft 33rd

The wheels 36 are in the region of its periphery to the annular body 31 above already mentioned in the engagement. The annular body 31 expediently has an approximately hollow shaft parallel flange 43 which can be advantageous supported on the adjacent ring body 12 and to which the torque delivered by the hollow shaft, whichever of the wheels 36 is activated, can be initiated in tracks of different diameters. The wheels 36 can be designed as friction wheels. In this case, the drive flange 43 of the annular body 31 is suitably provided with suitable friction surfaces. In the illustrated embodiment, the wheels 36 are formed as gear wheels. In this case, the flange 43 of the annular body 31 with three wheels 36 associated sprockets 44 is provided. The spacing of the wheels 36 is chosen in this case expediently such that in every position of displacement member 39 in each case only one wheel is enabled. The annular body 31 is, as has already been explained above, coupled with the hub 8 via a freewheel.

Once the shaft 7 is driven by means of the pedals 6, the hollow shaft 33 is rotated via the bevel gear 34, 35 in rotation. The wheel with the hollow shaft 33 are rotationally connected by means of the displacement member 36 of the gear set 39 transmits the rotary motion to the ring body 31, which in turn transfers the rotational movement to the hub eighth Depending on the switch position has the displacement member 39, so depending on which of the wheels 36 is activated, the torque is introduced to a greater or lesser distance from the axis of the annular body 31 in this one, bringing apparent difference Liche ratios result. In the embodiment shown in Figure 4, only one set of wheels on the circumference of the shaft 7 is provided. It would also readily conceivable, for example to provide two opposing or more identical sets of wheels, if this should be desirable to force share.

The annular body 31 may in this case similar to the embodiment shown in Figure 2 on the side opposite the drive flange 43 side having a projecting sleeve which is provided at its periphery with a brake thread 30 or similar guide surfaces, in the or a screwed, not shown here braking body engages which is brought postponed at a reversal of the direction of rotation of the shaft 7 on one here provided in the area of ​​the adjacent bearing body 13 starting cone, expanded in this way and to engage the braked hub. 8 It would also readily conceivable, similar to the embodiment shown in Figure 3, the shaft 7 to be provided directly to a brake thread or similar guide surfaces.

In the FIG 5 underlying embodiment, instead of several, axially on the hollow shaft 33 secured wheels that can be individually activated by the displacement member, that are rotationally connected to the hollow shaft 7, but otherwise in the unactivated state simply can rotate freely, only one wheel 45, suitably a friction wheel is provided which is mounted to move axially on the hollow shaft 33 and fixed to the displacement member 39, that can be moved along the axis of the hollow shaft 33 therewith. Upon actuation of the shift rod 38 in this case, the distance of the wheel 45 from the axis of the annular body 31 is continuously changed, thereby making them practically achieve a stepless variation of the transmission ratio. The wheel 45 should be as already mentioned, is formed as a friction wheel. The drive flange 43 of the annular body 31 may be expediently provided with an annular friction lining 46th Otherwise, the construction of this embodiment corresponds to the arrangement shown in Figure 4. If instead of the friction wheel 45 a gear is provided, the drive flange 43 is provided for each course, each with a sprocket.

When the 6 to 8 underlying embodiment, to form a multi-course, two popular here gearbox two designated as a whole with 50, simplified for reasons of space represented as a box penetrated by the shaft 7 gear units arranged side by side, which is about the related figure 3 described in the individual gear unit 17 may correspond. Also the other construction is similar to the arrangement shown in FIG 3. The following remarks are therefore limited mainly to the contrast existing developments, wherein for identical parts or parts of identical function for clarity, see the same reference numerals used.

For activating the here penetrated by the shaft 7 of transmission units 50, an axially on the shaft 7 slidably disposed clutch ring 52 is provided, which in form-locking engagement with a corresponding member of the gear units 50 is appropriately brought. In the illustrated embodiment, the coupling ring 52 is provided for this with frontally arranged claws 53rd It is conceivable rotationally coupling with the aid of this coupling ring about the rest in here towards the shaft 7 rotate freely arranged planet with the shaft. The coupling ring 52 is axially movable by means of a received in the shaft 7 shift rod 54 and can be brought into or out of engagement with each of the flank him gear units 50th To accommodate the shift rod 54, the shaft 7 is formed as a hollow shaft. In the illustrated embodiment, the shaft 7 this is simply provided with a continuous central bore 55th The hole 55 may be closed in the region of the shaft ends by suitable cover etc.. In the embodiment shown in Figure 6 are 50 simply provided for closing the hole in this screwed-threaded plug 56 and 57th The push rod 54 is provided with a radially projecting drive lug 58 which extends through a slot-shaped recess 59 of the shaft 7 and is fixedly connected to the coupling ring 52nd In the area of ​​its driving projection of the opposite end 58, the shift rod 54 is connected to a pulling cable 60 which is only indicated here by its centerline. The pulling cable 6O is led out of the shaft 7 and connected in the region of its outer end with a 61 indicated, arranged in the region of the pedal 6 footswitch 61st The foot switch 61 may be formed approximately as a knee lever which can be latched in different positions.

The shift rod 54 is by means of the shift pedal 61 against the force of a return spring indicated at 62 is axially adjustable and can be brought so in or disengaged from the transmission units 50th In the illustrated embodiment, the return spring 62 is constructed as the shifting rod 54 surrounding pressure spring which is supported at one end on a thickened portion 63 of the shift rod 54 and the other hand to the penetrated by the pulling cable 60 threaded plug 57th The thickening 63 ensures this same sufficient guidance of the switch rod 54. However, it would also be possible readily to form the return spring as a tension that might be appropriate arranged in the not penetrated by the shift rod 54 portion of the bore 55th In.diesem case could be the diameter of the shift rod 54 along its entire length to the diameter of the bore 55 match, which could allow einfache.Herstellung, a compact design and excellent large-scale management. For the axial adjustment of the driving projection 58, the shift rod 54 and the nose-side thickening can be performed 63 as separate, threaded engagement .Bauteile. In the illustrated psführungsbeispiel this one indicated at 64 adjustment is provided.

For guiding the control cable 60 in the region of the crank arm 5 that is provided with an external bottom inwardly upwardly extending oblique bore 65, in which the control cable 60 is laid. The bore 65 can extend approximately from the region 5 of the shaft 7 associated hub of the pedal crank up to the range of the shift pedal 61st In the illustrated embodiment, the bore 65 opens out in the region of their ends in grooves 66, in which the pulling cable 60 protected outside the bore 65 is conducted.

In the embodiment shown in Figure 7 is the accommodated in the shaft 7 shift rod 54, which is equipped with a round cross through a slot-shaped recess 59 of the shaft 7 driving lug 58, with a freely rotatable here against mounted via an indicated at 70 rotary joint, as a whole 61 designated pedal connected. This pedal 61 is provided in the present embodiment with two at their ends pedal-like bent arms 71, extending in an approximately the level of the adjacent pedal crank arm 5 parallel plane. To effect an axial displacement of the shift rod 54 a sampled from the opposite of the shift rod 54 rotatable lever 61 space curve 63 is provided with a corresponding elevation or depression in the axial direction. In the illustrated embodiment, the cam 63 is formed directly on an end side of the shaft 7, which is a simple and compact design results. The arms 71 of the shift pedal 61 may be provided with locking teeth the direction indicated at 72 type, which may be assigned to define the desired switching positions suitable latching hollows 73rd In the illustrated embodiment, the locking recesses 73 are easily provided in the region of Tretkurbelarme. 5 But it would also readily conceivable to provide a larger segment for receiving the latching hollows. To adjust the drive lug 58, which may be simply pushed the other by means of a suitable sleeve on the shift rod 54, a screw is also 64, at which the driving lug 58 ge through the power of indicated at 62 return spring to the plant is introduced. Upon rotation of the curve here 63 scanning shift pedal 61 that is axially displaced in accordance with the slope of the curve 63 and concurrently herewith the axially fixed hereby coupled shift rod 54. For scanning the curve 63 71 appropriate styli or may in the field of arms - roll the seino provided 74 kind indicated

In the embodiment shown in Figure 8 of the here also designated again as a whole with 61, two pedal-like cranked arms 71 having pedal is keyed on a pivot 75, but which is rotatably fixed mounted by means of an integrally formed collar 76 in the axial direction to the shaft. 7 For this purpose, the shaft 7 is frontally simply provided with the collar 76 receiving recess and capped off by a cover 77th The pivot pin 75 is provided with a threaded bore 78 which is engaged by an integrally formed on the shift rod 54 threaded pin 79th The shift rod 54 is due to its fixed connection non-rotatably with the round cross through a slot-shaped recess 59 of the shaft 7 driving lug 58 relative to the shaft. 7 Upon rotation of the shift pedal 61 thus the threaded pin screwed 79 of the shift rod 54 more or less far into the associated threaded bore 78 of the keyed with the shift pedal 61 pin 75, whereby a. axial displacement of the shift rod 54 and thus the drive lug 58 is accomplished. For the axial adjustment of the driving projection 58 can again be 64 provided a set screw. A return spring is practically not required in one embodiment of this type. The bore 55 of the shaft 7 may therefore be readily carried out as a blind hole. In the illustrated embodiment, the bore 55 for simplicity designed as a continuous means of a Gewindepfropfens 56 closed hole. To define the desired switching positions a locking device with locking teeth 72 and locking recesses 73 may be also provided in an embodiment of the present kind here.

Above, although some particularly preferred embodiments of the invention are explained in more detail, but without hereby should be connected a limitation. Rather, the expert has a number of options available to customize the general idea of ​​the inventive solution to the circumstances of the individual case.

So it would be readily possible to provide no freewheel between shaft 7 and hub 8, which may be desirable in racing bikes in particular to move from Halle race. Such racing bikes also do not require pedaling brake normally. The achievable with the inventive measures weight savings compared to conventional bicycles is in racing bikes of very particular advantage.