BACKGROUND OF THE INVENTION

1. Field of the Invention

The present invention relates in general to derailleur- type bicycle shifting systems, and more particularly to such a system wherein front and rear derailleur mechanisms are precisely controlled by respective rotatable handgrip shift actuators.

2. Description of the Prior Art

There has been a long-felt but previously unfulfilled need in the art for a bicycle derailleur shifting system which does not require that a hand, or least a thumb, be removed from the handlebar during shifting. Many derailleur shifting devices are actuated by levers mounted on the down tube of the frame, while some are mounted on the top tube and others on the handlebar. Such levers mounted on the down tube or the top tube all require that a hand be completely removed from the handlebar during shifting. Some derailleur shifting levers mounted on the handlebar can be actuated by taking a thumb off the handlebar and pushing the lever with the thumb, but this also diminishes control of the bicycle, and is awkward, so most riders simply take their hand off the handlebar to move the shift lever. For both safety and convenience, it is desirable to be able to shift derailleur mechanisms with both hands right on the handlebars. Despite a long-felt need for such a derailleur shifting system, applicant is not aware of any prior art derailleur shifting system where the shifting events can be accomplished with both hands on the handlebar.

Typical prior art derailleur shifting mechanisms which require removal of the hand, or at least the thumb, from the handlebar are disclosed in the following U.S. patents: Ross 4,055,093; Hedrich 4,194,408; Cira i 4,201,095; Bonnard 4,384,864; and Strong 4,548,092.

There has also been a long-felt but previously unfulfilled need in the art for a bicycle derailleur shifting system which is capable of "overshifting," yet which is not undesirably complicated and expensive. Overshifting is movement of the chain beyond the destination sprocket, and then back into alignment with the destination sprocket. It has long been known in the art that such overshifting is desirable during down-shifting events for earlier and smoother shifts. Most derailleur shifting systems do not have any built-in mechanism for accomplishing such overshifting, and require that the rider deliberately move the shifting lever beyond the location of the destination sprocket and then back to the destination sprocket. This requires two rider inputs, one being a determination of the desired extent of overshift, and the other being the time duration of the overshift. Satisfactory overshifting by this means requires considerable skill.

Applicant is aware of two prior art patents which disclose bicycle derailleur shifting apparatus having a built-in overshift feature. These are Yamasaki U.S. patent 4,267,744 and Bonnard U.S. patent 4,384,864. Both of these are very complicated mechanisms. Each of these devices has a built-in determination of the amount of overshift travel, yet neither of them determines the timing of the overshift. This is left up to the rider, who must first move a lever to the overshift position, and then move the lever back to the normal shift position.

Another problem with the Yamasaki and Bonnard overshift mechanisms is that they each provide the same amount of overshift travel for each one of the sprockets of a rear derailleur freewheel. The problem with this is that in most, if not all derailleur systems, the most advantageous extent of overshift travel varies for different freewheel sprockets. The "chain gap" or chain span between the derailleur guide pulley and a freewheel sprocket is considerably larger for the smaller, higher gear freewheel

sprockets than for the larger, lower gear freewheel sprockets, and a relatively long chain gap generally requires a larger amount of overshift than a relatively short chain gap for optimum shifting. Another problem with the built-in overshift features in both Yamasaki and Bonnard is that an optimum amount of overshift for the other freewheel sprockets is generally too much for the #1, lowest gear sprocket closest to the wheel. An optimum amount of overshift travel for the other freewheel sprockets is likely to cause derailling from the #1 sprocket, which could seriously damage the bicycle. Thus, since the overshift amount is the same for all sprockets, it is inherent that neither of the Yamasaki or Bonnard overshift mechanisms produces sufficient overshift travel for optimum down-shifting.

Another long-noted problem in the art which is heretofore been unsolved is the provision of an accurate front derailleur system capable of handling not only "parallel riding" but also "cross-over riding. " For example, with a 2-chain wheel front derailleur system, for parallel riding the larger chain wheel will service the smaller rear freewheel sprockets, and the smaller chain wheel will service the larger freewheel sprockets. With cross-over riding, the chain may be crossed over from the larger chain wheel to relatively large freewheel sprockets, or the chain may be crossed over from the smaller chain wheel to relatively small freewheel sprockets. Such crossed-over chain locations have a propensity for causing undesirable "chain rasp," and the prior art solution to this problem was simply to provide a front derailleur chain cage having a relatively wide gap between the cage plates. While this may reduce chain rasp, it causes the further problems of inaccuracy in shifting, and frequent chain derailling. A further problem in the art, which relates primarily to rear bicycle derailleur shifting systems, is that there are numerous points of lost motion in both the derailleur mechanism and its actuating cable which cumulatively add up

to a considerable amount of overall lost motion, as for example from about .040 to about .070 inch. Applicant has found that for accurate index shifting, substantially all of this cumulative lost motion must first be taken up at the shift actuator before the actual shift increment of travel between adjacent sprockets is applied during a down-shifting event. Applicant is not aware of any specific consideration of this problem in the prior art, and in particular of any specific compensation for such cumulative lost motion for each of the various type of derailleur and cable systems currently available.

It has long been recognized in the art that rotary handgrip devices can be useful for controlling vehicle mechanisms, particularly on motorcycles, but also on bicycles. Several of such devices are disclosed in French patent 829,283 to Braumandl. However, applicant is not aware of any such device having previously been employed in cooperation with derailleur bicycle shifting apparatus, and such is not taught or suggested by Braumandl.

SUMMARY OF THE INVENTION

In view of these and other problems in the art, it is a general object of the present invention to solve the problems associated with prior art bicycle derailleur shifting systems.

Another object of the invention is to provide a bicycle derailleur shifting system which embodies a shift actuator that is conveniently rotatably mounted about the handlebar and so located as to not require the rider to remove a hand, or even a thumb, from the handlebar to effect a shifting event, thereby providing improved shifting convenience and safety.

Another object of the invention is to provide a bicycle derailleur shifting system embodying a shift actuator which is particularly simple in construction and economical to manufacture, yet which, in combination with the derailleur

mechanism, has improved performance over prior art derailleur shifting systems in all respects.

Another object of the invention is to provide a bicycle derailleur shifting system having a handgrip shift actuator embodying a generally helical cam which defines the derailleur mechanism movements.

Another object of the invention is to provide a bicycle derailleur shifting system which completely accounts and compensates for numerous lost motions in the derailleur mechanism and its actuating cable, thereby enabling precise index shifting to be accomplished.

A further object of the invention is to provide a bicycle derailleur shifting system wherein cable lost motion factors such as cable housing compressability and warp are minimized and made very predictable to assist in accurately determining and compensating for all cumulative lost motion factors.

Another object of the invention is to provide a bicycle derailleur shifting system in which a rotary handgrip shift actuator cooperates with the derailleur mechanism so as to enable down-shifting to be easily accomplished with substantially uniform twisting effort by the rider for down-shifting through all of the gears, despite progressively increasing derailleur return spring loading for increasingly lower gear ratios.

A further object of the invention is to provide a bicycle derailleur shifting system in which a rotary handgrip shift actuator cooperates with the derailleur mechanism in compensating for variations in chain gap length.

A further object of the invention is to provide a bicycle derailleur shifting system in which a rotary handgrip shift actuator cooperates with the derailleur mechanism in providing an optimum amount of overshift for down-shifting to each of the gears, despite variations that may be present in spacing between different rear freewheel sprockets and variations in chain gap for different

freewheel sprockets.

A further object of the invention is to provide a bicycle derailleur shifting system wherein a rotary handgrip shift actuator has built-in overshift capability, yet is very simple in construction.

A further object of the invention is to provide a bicycle derailleur shifting system which has built-in overshift capability, yet does not require manual input to define all or part of the overshift actuation. A further object of the invention is to provide a bicycle derailleur shifting system wherein a rotary handgrip shift actuator effects overshift increments an optimum amount relative to each rear derailleur freewheel sprocket for the most positive and accurate index shift events possible.

A still further object of the invention is to define optimum and preferred minimum and maximum shifting limits for rear derailleur mechanisms, and to teach how these limits may be achieved by the use of rotary cam actuator means.

A still further object of the invention is to provide a bicycle derailleur shifting system wherein a front derailleur mechanism is actuated by a rotary handgrip shift actuator capable of fine-tuning the shift positions to accommodate cross-over riding.

Another object of the invention is to provide a bicycle derailleur shifting system having built-in overshift, wherein the overshift timing is automatically established by the natural shifting movement, and does not require separate rider input.

Another object of the invention is to provide a bicycle derailleur shifting system having a handgrip shift actuator rotatably mounted over the end of a handlebar.

Yet a further object of the invention is to provide a bicycle derailleur shifting system having a handgrip shift actuator rotatably mounted on a handlebar inboard of the handlebar en .

According to the invention, a bicycle equipped with front and rear derailleurs has front and rear handgrip shift actuators rotatably mounted over the handlebar, the front handgrip shift actuator being operatively associated with the front derailleur mechanism for shifting the front derailleur, and the rear shift actuator being operatively associated with the rear derailleur mechanism for shifting the rear derailleur. The rear handgrip shift actuator is preferably mounted on the right side of the handlebar and the front front handgrip shift actuator mounted on the left side of the handlebar to accommodate most riders, since the rear derailleur is shifted more frequently than the front derailleur. Each handgrip shift actuator contains a generally cylindrical cam member having a generally helical operating face configured with a plurality of spaced detents or valleys with a cam peak or lobe between each pair of adjacent detents. A housing covers and is keyed to the cam member. Thus, a front handgrip actuator which cooperates with a front derailleur having two chain rings will have two primary detents and one intervening peak. Similarly, a rear handgrip shift actuator for cooperation with a rear derailleur having a 6-sproσket freewheel will have a cam operating face with six successive detents and five intervening peaks. One form of handgrip shift actuator according to the invention is conveniently mounted over an end of the handlebar, as for example over an end of a traditional drop bar-type handlebar. In this type of handgrip shift actuator, the cam operating face faces inwardly away from the handlebar end, and engages a cam pin which is rigidly diametrically affixed to the handlebar with an operating end projecting outwardly from the handlebar. The derailleur actuating cable and cable jacket enter the inside of the handlebar through a suitable opening, and the cable passes through a ^" hole in the pin and thence through a generally flat outer end portion of the cam member, with an enlargement crimped or cast on the end of the cable which

bears against an outwardly facing surface on the end portion of the cam member. The cable jacket terminates in a counterbore of the pin hole. The other end of the cable is attached to the parallelogram of the derailleur mechanism and the cable is tensioned by the derailleur return spring associated with the parallelogram. Rotation of the handgrip actuator in one direction causes the cam face to ride upwardly, i.e., outwardly relative to the handlebar end, so as to pull the cable in down-shifting increments from detent to detent on the cam face. Rotation of the handgrip actuator in the opposite direction releases cable tension causing the derailleur mechanism to up-shift from detent to detent on the cam face.

Another form of handgrip shift actuator according to the invention which is particularly suitable for mountain bikes is mounted over the handlebar inboard of the handlebar end so as to leave room for a fixed handgrip proximate the end of the handlebar. In this form of grip shift actuator, a tubular support body is slipped over the outside of the handlebar and keyed to the handlebar. A cam follower plate slides in a slot in the tubular support body, and supports a cam follower pin. The generally cylindrical cam member is rotatably mounted over the support body, but does not move axially relative to the support body and handlebar; instead, the generally helical cam operating face, which faces outwardly toward the handlebar end, engages the cam follower pin and causes the pin and its plate to shift generally axially relative to the shift actuator and handlebar according to the cam face configuration. The derailleur actuator cable is connected to the cam follower, biasing the follower against the cam operating face because of tension on the cable from the derailleur mechanism return spring. The cable jacket end seats in a recess in the actuator support body. A generally cylindrical housing encompasses the cam member and a portion of the support body, being keyed to the cam member but being rotatable relative to the support body. Rotation of the housing and cam member in one

direction will cause the cam follower to ride upwardly on the cam operating face or toward the end of the handlebar, pulling the cable in successive down-shifting increments from detent to detent along the cam face, and rotation of the actuator in the opposite direction will cause the cam follower to\ release the cable in up-shifting increments from detent to detent along the cam face.

An important aspect of the present invention is the coaction between the rotary handgrip shift actuator and any one of a number of different derailleur systems. Each of the various derailleur systems has its own special operating characteristics which must be accounted for in a handgrip cam of the invention, these characteristics including a variety of lost motions in both the derailleur mechanism and its cable system, varying chain gap for the different freewheel sprockets, varying spacings between the freewheel sprockets, derailleur return spring force and the rate of variation of that force as the derailleur mechanism shifts the chain either downwardly toward larger freewheel sprockets or upwardly toward smaller freewheel sprockets, and the like. Applicant preferably provides a special handgrip cam with a cam face specially configured to account and/or compensate for all of these special characteristics of any particular derailleur system, to the end that each shift from one freewheel sprocket to another is an early, positive, and accurately aligned index shift. Thus, applicant's rear shift actuator cam cooperates with the rear derailleur system in compensating for the sum of all of the •lost motions in the derailleur system and its cable system, in compensating for variations in chain gap length, and in providing an optimum amount of overshift for down-shifting to each of the gears. The operating characteristics of front derailleur mechanisms are similarly accounted and compensated for. Built-in overshift is programmed on applicant's handgrip shift actuator cams so as to provide optimum overshift for each down-shift event. Such overshift does

not require separate manual input for the timing of the overshift; the natural rotational movement of the handlebar shift actuator automatically times the overshift.

Another important part of the invention is the definition of optimum and preferred minimum and maximum shifting limits for rear derailleur mechanisms, and the programming of the cam operating faces of the handgrip shift actuators of the invention to accurately achieve such shifting limits for each available derailleur system. The front handgrip shift actuator cam has respective primary detents for chain alignment with each front derailleur chain wheel. A form of the front actuator cam also embodies secondary, fine-tune detents to fine-tune the chain alignment for accommodation of cross-over riding. This allows a relatively narrow chain cage to be employed, for accurate shifting and for avoidance of chain derailling.

BRIEF DESCRIPTION OF THE DRAWINGS

These and other objects of the invention will become more apparent in refernce to the following description and the accompanying drawings, wherein:

Figure 1 is an elevational view of a bicycle embodying the present invention; Figure 2 is a plan view partially broken away along the line 2-2 in Figure 1;

Figure 3 is a cross-sectional view taken on the line 3-3 in Figure 2;

Figure 4 is a cross-sectional view taken on the line 4-4 in Figure 2;

Figure 5 is a cross-sectional view taken on the line 5-5 in Figure 3;

Figure 6 is a cross-sectional view taken on the line 6-6 in Figure 3; Figure 7 is a plan sectional view taken on the ine 7-7 in Figure 5;

Figure 8 is a developed view indicated at line 8-8 in Figure 4 illustrating one cam profile of the present invention;

Figure 9 is a cross-sectional view taken on the line 9-9 in Figure 5;

Figure 10 is an exploded, perspective view of a handgrip shift actuator according to the invention;

Figure 11 is an exploded, perspective view illustrating installation of a handgrip shift actuator according to the invention;

Figure 12 is a cross-sectional view taken on the line 12-12 in Figure 2 showing a front handgrip shift actuator of the invention;

Figure 13 is a developed view indicated at line 13-13 in Figure 12 illustrating a simple 2-position cam profile for the front shift actuator;

Figure 14 is a cross-sectional view similar to Figure 12 showing an alternative cam having fine-tune detents;

Figure 15 is a developed view indicated at line 15-15 in Figure 14 illustrating the cam profile;

Figure 16 is a cross-sectional view similar to Figure 4 illustrating an alternative embodiment with the cam and cam housing combined;

Figure 17 is a cross-sectional view taken on the line 17-17 of Figure 16;

Figure 18 is a cros-sectional view taken on the line 18-18 in Figure 16;

Figure 19 is a developed view indicated at line 19-19 in Figure 16 illustrating another cam profile; Figure 20 is a fragmentary side elevational view of another bicycle embodying front and rear derailleurs;

Figure 21 is an enlarged fragmentary elevational view of the rear derailleur system of Figure 20;

Figure 22 is a further enlarged, fragmentary view taken on the line 22-22 in Figure 20;

Figure 23 is a fragmentary view taken on the line 23-23 in Figure 22;

Figure 24 is a fragmentary view, partly in section and partly in elevation, taken on the line 24-24 in Figure 21;

Figure 25 is an elevational view with portions broken away taken on the line 25-25 in Figure 21; Figure 26 is a cross-sectional view taken on the line 26-26 in Figure 25;

Figure 27 is a fragmentary elevational view, with portions broken away, taken on the line 27-27 in Figure 21;

Figure 28 is an enlarged fragmentary elevational view illustrating an adjustment feature of the rear derailleur mechanism of Figure 21;

Figure 29 is a fragmentary sectional view taken on the line 29-29 in Figure 21;

Figure 30 is a perspective view of a portion of the derailleur mechanism shown in Figure 21 indicating various points of lost motion;

Figures 31 and 32 are diagrammatic views illustrating variations in chain gap;

Figure 33 is a diagrammatic view illustrating overshift;

Figure 34 is a diagrammatic view illustrating a cam face configuration which compensates for variations in derailleur return spring force;

Figure 35 is a diagrammatic illustration of a single down-shift event;

Figure 36 is a diagrammatic illustration of a single up-shift event;

Figure 37 is a fragmentary elevational view illustrating an elongated, undercut cam for accommodating an unusually large number of gear ratios;

Figure 38 is a developed view illustrating fine-tune detents for a cam of the invention adapted to control front derailleur shifting for a 3-chain wheel cluster.

Figure 39 is a fragmentary elevational view of a front derailleur mechanism;

Figure 40 is a diagrammatic view illustrating parallel riding;

Figure 41 is a diagrammatic view illustrating cross-over riding;

Figure 42 is a fragmentary plan view illustrating parallel riding; Figure 43 is a view similar to Figure 42 illustrating cross-over riding;

Figure 44 is a view similar to Figures 42 and 43 illustrating correction of the cross-over of Figure 43 by means of a fine-tune cam detent; Figure 45 is a fragmentary elevational view of the front end of the mountain bike;

Figure 46 is a cross-sectional view taken on line 46-46 in Figure 5;

Figure 47 is a fragmentary longitudinal sectional view taken on the line 47-47 in Figure 46;

Figure 48 is a cross-sectional view taken on the line 48-48 in Figure 47;

Figure 49 is a view similar, to Figure 47, but with the cam rotated to a different position; and Figure 50 is a view taken on the line 50-50 in Figure 49.

DETAILED DESCRIPTION

Figures 1 and 2 illustrate a 12-speed bicycle, generally designated 10, in which a 6-sprocket rear derailleur mechanism is actuated by a rear handgrip shift actuator according to the invention, and a 2-chain wheel front derailleur mechanism is actuated by a front handgrip shift actuator according to the invention. It is to be understood, however, that the principles of the present invention are equally applicable to any multi-speed bicycle embodying derailleur-type shifting, including three, five, six, seven, ten, twelve, fourteen, and eighteen-speed bicycles, and the like. Bicycle 10 has a primary frame which is generally triangle-shaped, including a head tube 14, a generally horizontal top tube 16 connected at its front end to head tube 14, a main down tube 18 extending downwardly and rearwardly from head tube 14, and a seat tube 20 connected to the rear end of top tube 16 and extending downwardly and forwardly therefrom. Main down tube 18 and seat tube 20 are joined at their lower ends to bottom bracket 22, shown in phantom, within which the pedal crank is horizontally journalled.

A front fork 24 defines the axis 26 of front wheel 27. A steering tube (not shown) at the upper end of front fork 24 extends upwardly into head tube 14, and is wedge-clamped to a handlebar stem generally designated 28 which extends down into the steering tube within head tube 14. Handlebar stem 28 includes a handle bar clamp 30 at its upper end for gripping handlebar 32. The handlebar 32 which is illustrated in Figures 1 and 2 is of the traditional drop bar type, although it is to be understood that the invention is equally applicable to any type of bicycle handlebar.

A down fork 34 consisting of left and right seat stays extends downwardly and rearwardly from the upper portion of seat tube 20, and a bottom fork 36 consisting of left and right chain stays extends rearwardly from bottom bracket 22. The left sides of down fork 34 and bottom fork 36 are

connected at their rear ends, and similarly the right sides of down fork 34 and bottom fork 36 are connected at their rear ends, and these rear end connections support rear wheel dropouts which define the axis 38 of rear wheel 40. Seat stem 42 is engaged in the upper end of seat tube 20 and is releaseably secured by seat clamp 44. The pedal crank, generally designated 46, is rotatably journalled in bottom bracket 22, and includes right and left crank arms 48 A chain wheel cluster generally designated 50 is rigidly supported on pedal crank 46, and constitutes the sprocket cluster of the front derailleur assembly. Most commonly, the chain wheel cluster will embody two chain wheels, although it is also common to have chain wheel clusters with three chain wheels. The front handgrip shift actuator shown in Figures 2, 12, and 13, and the front handgrip shift actuator shown in Figures 14 and 15, are both adapted for utilization with a chain wheel cluster 50 embodying two chain wheels. An endless drive chain 52 transmits power from the chain wheel cluster 50 to a multiple freewheel 54 that is operatively connected to the rear wheel hub mechanism in a conventional manner.

A front derailleur mechanism generally designated 56 cooperates with chain wheel cluster 50 to shift chain 52 laterally between the two chain wheels of cluster 50, down-shifting from the smaller chain wheel to the larger chain wheel, or up-shifting from the larger chain wheel to the smaller chain wheel. A rear derailleur mechanism 58 is pivotally connected to the frame proximate the confluence of the right side portions of down fork 34 and bottom fork 36 for shifting chain 52 laterally from sprocket to sprocket of the multiple freewheel 54, either down-shifting from a smaller sprocket to a larger sprocket or up-shifting from a larger sprocket to a smaller sprocket. A front control cable 60 operatively connects a front handgrip shift actuator 62 to the front derailleur mechanism 56 such that the front handgrip shift actuator 62 cooperates with and controls the shifting of front derailleur mechanism 56.

Similarly, a rear control cable 64 operatively connects a rear handgrip shift actuator 66 to the rear derailleur mechanism 56 such that the rear handgrip shift actuator 66 cooperates with and controls the shifting of the rear derailleur mechanism 58.

The handgrip shift actuators of the invention illustrated in Figures 1-19 are all adapted for mounting over the ends of the bicycle handlebar 32, with each of the respective cables 60 and 64 being operatively connected to the respective shift actuators 62 and 66 through respective end portions of handlebar 32. Accordingly, each of the cables 60 and 64 is threaded through a respective aperture 68 in the wall of handlebar 32 from the outside to the inside of the wall of handlebar 32 for coupling with the respective shift actuators 62 and 66.

The traditional drop bar-type handlebar 32 shown in Figures 1 and 2 consists of a generally straight transverse portion 70 with down-turned U-shape side portions having generally straight rearwardly directed end portions 72 over which handgrip shift actuators 62 and 66 of the invention are mounted. In the normal operation of a bicycle equipped with both front and rear derailleurs, the rear derailleur mechanism is shifted more frequently than the front derailleur mechanism. Accordingly, as a convenience to most riders, rear shift actuator 66 is preferably mounted on the right-hand end portion 72 of the handle bar, and front shift actuator 62 is mounted on the left-hand end portion 72 of the handlebar.

During cycling while not shifting, a cyclist will normally grip the lower, end portions 72 of handlebar 32 forward of the handgrip shift actuators 62 and 66. Since shift actuators 62 and 66 occupy a portion of the normal grip space on the handle bar end portions 72, it is preferable to provide a handlebar 32 which has end portions 72 somewhat longer than those found on a conventional drop bar-type handlebar.

Rear handgrip shift actuator 66 will next be described in detail in connection with Figures 3-11. A rotary cam member 74 having a generally helical operating face is the heart of the rear handgrip shift actuator 66 and cooperates with the rear derailleur mechanism 58 for positive, smooth, and easy shifting in both the down-shift direction and the up-shift direction. There are currently approximately ten different derailleur mechanisms available on the market, and each one has different shifting characteristics, both in general for down-shifting and up-shifting through all of the rear gears, and specifically for down-shifting and up-shifting in each individual gear. For positive index shifting of each type of rear derailleur currently available, it is preferred to have a cam member 74 the operating face of which is specifically contoured to cooperate with that type derailleur for positive index down-shifting and up-shifting to each gear. Accordingly, for the approximately ten different rear derailleur mechanisms available, it is preferred to have approximately ten respective differently contoured cam members 74 of the invention. Nevertheless, because of the way rear handgrip shift actuator 66 is constructed, all of the other parts of shift actuator 66 may be the same for the various types of rear derailleur mechanisms. Similarly, the approximately ten different front derailleur mechanisms currently available also have different operating characteristics, and for positive and easy front derailleur index shifting it is preferred to have a separate cam contoured for cooperation with each different front derailleur mechanism, one type cam for the front handgrip shift actuator 62 being shown in Figures 12 and 13, and another type cam for the front shift actuator 62 being shown in Figures 14 and 15.

As described in detail hereinafter, the close cooperation between front and rear shift actuators 62 and 66 and respective front and rear derailleur mechanisms 56 and 58 is such that the present invention resides in the

combination of a handgrip shift actuator 62 or 66 and a respective derailleur mechanism 56 or 58. This is borne out by the fact that for uniform, easy, positive index shifting, the cam member of the respective front or rear shift actuator 62 or 66 is preferably constructed to accommodate the peculiar characteristics of any particular front or rear derailleur mechanism, such as chain gap variations through the gears, actuation ratios through the gears, return spring strength and variations through the gears, takeup for lost motion in the cable system, derailleur pivots, guide pulley and the like, and fine-tune front shift actuator locations are provided to accommodate chain cross-over between front and rear derailleur sprockets without chain rasp in the front derailleur cage. Figures 3-11 illustrate the details of construction of the rear handgrip shift actuator 66. The primary operative member in shift actuator 66 is a generally cup-shaped cam member 74 having a generally cylindrical cam portion 75 that is arranged coaxially of the respective handlebar end portions 72, and a generally flat outer end portion 76 which is transverse to the axis of handlebar end portion 72. The generally cylindrical portion 75 of cam member 74 terminates inwardly at an inner end 77 which is also transverse to the axis of handlebar end portion 72. Cam member 74 nests within a generally complementary cam cover member 78 which has a generally cylindrical barrel portion 79 that overlies the cam portion 75, and a generally flat, transverse end portion 80 that overlies the cam portion 76. The generally cylindrical portions 75 and 79 of the respective cam and cover members 74 and 78 are preferably of stepped configuration as illustrated, the inner part of the cylindrical cam portion 75 being radially thickened to provide a relatively wide cam operating surface and increased hand torquing radius, and the inner part of the cover barrel portion 79 being thickened for further hand torquing radius. After cam member 74 has been assembled within cover member 78, a cover bushing 82 is mounted on the

inner end of cover member 78, bushing 82 having a skirt portion 84 which is engaged within cover member 78. Bushing 82 is permanently bonded to cover member 78, preferably by ultrasonic welding, or alternatively by adhesive means. Cam member 74 is preferably molded from a high-strength, chemically lubricated plastic material such as Delrin 500CL that provides a durable and lubricious cam operating face, as well as freedom of rotation of cam member 74 about the handlebar end portion 72. Cover member 78 and its bushing 82 are preferably molded from a plastic material such as ABS which has high resistance to ultraviolet light penetration and will therefore protect cam member 74 from ultraviolet deterioration.

Cam member 74, cover member 78, and bushing 82 are registered such that all three members rotate together. Two registration systems are provided, one registering cam member 74 to cover member 78, and the other registering bushing 82 to cover member 78. Figure 10 best illustrates these two registration systems. The registration of bushing 82 to cover member 78 includes a generally axially directed external key 86 on bushing skirt 84, key 86 being received in a complementary generally axially directed keyway recess 88 in the cover barrel portion 79. The registration system between cover member 78 and cam member 74 consists of one or more generally radially directed slots formed in the outside of cam end portion 76, and a similar number of registering, generally radially directed ribs projecting from the inside of the cam cover end portion 80. In the embodiment illustrated in Figures 3-11, there are three of such slots 90 and ribs 92, and these are irregularly spaced about the center axes of cam member 74 and cover member 78 so that the cam and cover members 74 and 78, respectively, can only be assembled in one position of relative rotation. This is so that a tactile sensor 93 on the outside of cover bushing 82 will also have a single, fixed rotational position relative to

cam member 74, so as to provide an indication to the cyclist of the particular gear which is engaged. The tactile sensor 93 is best seen in Figures 5 and 11, being shown in the six o'clock position in Figure 5. For convenience in molding, the tactile sensor 93 is axially aligned with bushing key 86. As handgrip shift actuator 66 is rotated to shift the derailleur mechanism from gear to gear, sensor 93 rotates an equivalent amount, thus providing the cyclist with a tactile indication of the selected gear ratio. The operating surface of cam member 74 engages and rides over a cam pin 94 which is fixedly attached to the handlebar end portion 72. As seen in Figures 3, 4, 7 and 11, cam pin 94 is generally cylindrical in shape and has a reduced diameter portion 95 at one end. Cam pin 94 is mounted in the handlebar end portion 72 with its reduced diameter portion 95 located in an aperture 97 through the wall of handlebar portion 72 so as not to extend beyond the outer surface of handlebar portion 72. Cam pin 94 extends diametrically across the inside of handlebar portion 72, projecting outwardly through a larger aperture 97 in the wall of handlebar portion 72, with a cam-operating end portion 98 of cam pin 94 extending radially outwardly from the outer surface of handlebar portion 72 to provide a fixed, smooth, rounded bearing member against which the cam operating face or surface 99 of cam member 74 rides.

Cam pin 94 serves two functions. First, its external portion 98 provides the aforesaid bearing surface which is engaged by cam operating face 99. Second, cam pin 94 provides a locater for the end of the cable housing or casing. A bore 100 is provided diametrically through cam pin 94 at a location radially centered within the handlebar portion 72 and axially aligned with handlebar portion 72. The rear derailleur shifting cable 101 passes through this bore 100. A counterbore 102 of bore 100 presents a shoulder that faces inwardly of the handlebar end. Registering center apertures 103 and 104 extend through the cam and cover member ends 76 and 80, respectively, and an annular

bearing plate 105 is moulded into the cam member end 76 so as to present a metal bearing surface in a direction outwardly of the handlebar end. After cable 101 extends through cam pin bore 100, it passes through the cam member end bore 103 and bearing plate 105, and terminates at eithe a crimped collar or cast-on metal bead 106, which may be made of lead. The housing or casing 107 for cable 101 has a ferrule 108 crimped over its end, and ferrule 108 seats within the cam pin counterbore 102, thus providing a fixed location for cable housing 107 relative to cable 101. The return spring of rear derailleur mechanism 58 constantly tensions the cable 101, which in turn constantly biases the cam operating face 99 against the cam pin operating end 98. When cable 101 is pulled outwardly by cam operating surface 99 relative to the handlebar end, the other end of cable 101 will actuate rear derailleur mechanism 58 in a down-shift movement to a larger freewheel sprocket closer to the wheel 40; while release of cable 101 by cam operating face 99 will allow the return spring of rear derailleur mechanism 58 to pull cable 101 toward the derailleur mechanism 58 and cause derailleur mechanism 58 to up-shift the chain away from wheel 40 to a smaller sprocket. The generally helical, stepped operating face 99 of cam member 74 is preferably arranged to move axially outwardly of the handlebar end when twisted clockwise as viewed by a cyclist, thereby pulling cable 101 outwardly and shifting rear derailleur mechanism 58 to a larger sprocket and larger gear ratio. Conversely, when cam member 74 is twisted counterclockwise by the cyclist, derailleur return spring tension on cable 101 will cause cam member 74 to move inwardly of the handlebar end, allowing derailleur mechanism 58 to shift upwardly to a smaller sprocket.

Preferably, a portion of cover bushing 82 overlies a collar fixedly mounted on the handlebar end portion 72, such that bushing 82 and collar 109 cooperate as a baffle to minimize entry of dust into the shift actuator mechanism, which might otherwise cause premature wear in the mechanism.

Collar 109 has a locator button 110 thereon which seats in a handle bar hole 111 to fixedly position collar 109 on handlebar end portion 72.

Figure 8 illustrates the profile of operating face or surface 99 of cam member 74, laid out flat for convenience in understanding. Cam operating face 99 consists of a series of peaks or crests 112 and intermediate detent valleys 114. The operating face 99 has six detents and five intermediate peaks, to serve a 6-sprocket rear derailleur freewheel as seen in Figure 1. As seen in Figure 8, the rear shift actuator 66 is twisted all of the way to its highest gear, smallest sprocket position, with cam pin 94 located in the uppermost, first detent 114. As shift actuator 66 is rotated from the position of Figure 8, a first cam ramp 115 rides upwardly against cam pin 94, and the first peak 112 rides over pin 94 so that the pin then becomes located in the second detent 114. At the first detent position, which is shown, the rear derailleur mechanism 58 substantially aligns chain 52 with sprocket #6, which is the smallest sprocket of freewheel 54. At the second detent 114, rear derailleur mechanism 58 substantially aligns chain 52 with sprocket #5, which is th second smallest sprocket of freewheel 54. As rear shift actuator 66 is progressively rotated to move the cam operating surface 99 upwardly as viewed in Figure 8, successive detents 114 engage over pin 94 to substantially align chain 52 with successively larger freewheel sprockets for successively lower gear ratios until pin 94 is lodged i the lowermost detent 114 as viewed in Figure 8, in which location the rear derailleur mechanism 58 has moved chain 5 substantially into alignment with sprocket #1 of freewheel 54, which is the lowest gear ratio.

As rear shift actuator 66 is thus shifted from the smallest, highest gear freewheel sprocket position as shown in Figure 8 to successively larger, lower gear freewheel sprockets, it pulls cable 101 against the return spring of rear derailleur mechanism 58 outwardly relative to the

handlebar end portion 72, to the left as viewed in Figures 5, 7 and 8, and to the right as viewed in Figure 6. As rea shift actuator 66 is rotated the other way to shift upwardl from the largest freewheel sprocket in which the lowermost detent 114 of Figure 8 is engaged over cam pin 94 towards successively smaller and higher gear freewheel sprockets, the return spring of rear derailleur mechanism 58 draws cam member 74, together with its cover member 78 and bushing 82 incrementally to the right as viewed in Figures 5, 7 and 8, and to the left as viewed in Figure 6. The position illustrated in Figures 5-8 are the smallest freewheel sprocket, highest gear ratio position, while the phantom line position illustrated in Figures 5 and 6 represents the largest freewheel sprocket, lowest gear ratio position. In all axial positions of cam member 74, bushing 82 will overlie handlebar collar 109 to serve the function of inhibiting entry of dust or dirt into the shift actuator mechanism.

Each of the cam face detent valleys 114 serves two functions. First, it serves to axially locate cam member 7 relative to handlebar end portion 72, and hence correspondingly axially locate cable 101, and thereby position derailleur mechanism 58 for alignment of drive chain 52 with a respective sprocket of freewheel 54. Each of the cam face detent valleys 114 also serves as a detent for positively rotationally locating, and hence indexing, cam member 74 relative to the handlebar end portion 72, thereby effecting positive index shifting. Nevertheless, both the cam ramp slopes 115 and the back slopes 116 of cam operating face 99 are gentle enough slopes so that, together with the rounding of peaks 112, both down-shifting and up-shifting are effected easily and smoothly.

As will be described in detail hereinafter in connection with detailed illustrations of a derailleur mechanism and associated cable actuation system, according to the present invention for the down-shift direction of rotation of cam member 74 toward larger freewheel sprockets.

the heights of the cam face peaks 112 above the preceding detents 114 are calculated to first take out all lost motio in the derailleur mechanism and in the cable system, next actuate the derailleur mechanism a shift increment of movement in which the chain is brought into alignment with the next larger sprocket, and then further actuate the derailleur mechanism in an overshift increment of movement. Then, as cam member 74 completes such down-shift to the nex higher detent 114, there is first a backlash in which the lost motion originally taken up is released, and then the overshift increment is released. By this means, both the derailleur mechanism and the cable move in the up-shift direction at the completion of each down-shifting event. This restores all of the lost motion locations in both the derailleur mechanism and the cable system at the end of a down-shifting event to exactly their same positions as if a up-shift to a smaller sprocket had been effected, and it also places the cable friction direction the same as for an up-shifting event, whereby the same precise derailleur positioning, and hence cable locating, will occur at any freewheel sprocket destination, whether that destination wa arrived at after an up-shift or a down-shift.

As noted above, the specific profile of cam operating face or surface 99 is determined by the operating characteristics of the specific derailleur mechanism with which it is used. The profile of cam operating face or surface 99 illustrated in Figure 8 is adapted for use in cooperation with a Shimano Model No. RD-7401 derailleur.

As best illustrated in Figure 8, a stop projection 117 is provided adjacent the lowest gear detent 114. This is for the purpose of blocking further rotation of shift actuator 66 and thereby avoiding the possibility of cam fac 99 riding off pin 94 and jumping to the highest gear detent 114. As also best seen in Figure 8, a notch or cutout 118 is provided in the inner edge of bushing 82. This is to provide clearance for cam pin 94 as cam member 74 is shifte from the next lowest gear detent 114 to the lowest gear

detent 114 .

The detent function of cam surface detent valleys 114 provides for self-locking of cam member 74 at each gear position without reducing the ease of operation of handgrip shift actuator 66. For example, in some known index shifting systems which include a detent mechanism comprised of a ball and slip plate, the locking feature is added to the system by increasing the tension between the ball and slip plate, which makes the shifting mechanism relatively difficult to operate. In the present invention, the self-locking feature does not require any increased tension on any of the component parts of the system, thereby providing self-locking without reducing the ease of operation of shift actuator 66. Figures 12 and 13 illustrate one form of front handgri shift actuator 62 which employs a two-position cam member, generally designated 120. The front shift actuator 62 with cam member 120 cooperates with and controls the front derailleur mechanism 56 for shifting between the two chain wheels of a 2-chain wheel front sprocket cluster 50. The front handgrip shift actuator 62 is similar to the rear handgrip shift actuator 66 heretofore described, except for the profile of operating face or surface 122 of cam 120. Figure 13 is a view in which the cylindrical cam member 120 has been opened out to a flat plan for ease of understanding, but in Figure 13 cam operating surface 122 i shown facing generally opposite the direction in which cam operating face 99 is shown in Figure 8.

Cam operating face or surface 122 has a first detent valley 124 for the smaller, higher gear ratio chain wheel o cluster 50, and a second detent valley 126 for the larger, lower gear chain wheel of cluster 50. Cam operating face 122 has a single rounded peak 128 between the two detents 124 and 126, with a cam ramp 130 extending between small chain wheel detent 124 and peak 128, and backslope 131 bein disposed between peak 128 and large chain wheel detent 126. Cam stop surfaces 132 and 134 are provided adjacent the

respective detents 124 and 126 to prevent inadvertent over-actuation of front shift actuator 62.

Cam 120 of Figure 13 may, if desired, be modified to accommodate a derailleur system having a 3-chain wheel cluster, such as the Shimano Hyperglide derailleur system. This can be done by embodying three successive detents with two intervening peaks, instead of the two detents 124 and 126 and single intervening peak 128.

The profile of cam operating face 122 will vary according to the particular derailleur mechanism with which it is utilized. As with rear shift actuator 66, front shif actuator 62 cooperates in its mode of operation with the particular front derailleur mechanism 58 for which it is constructed, through the front control cable 60, and it is this overall combination which constitutes the front derailleur aspect of the present invention. Front handgrip shift actuator 62 provides positive index shifting of front derailleur mechanism 56 in substantially the same manner as rear handgrip shift actuator 66 provides positive index shifting of rear derailleur mechanism 58.

Figures 14 and 15 illustrate an alternative front handgrip shift actuator 62* having a cam member 136 with an operating face 138 that has two primary detents 140 and 142 separated by a primary cam peak 144 and cam ramp 146. Primary detent 140 is for the smaller, higher gear ratio chain wheel of cluster 50, and primary detent 142 is for th larger chain wheel of cluster 50 for "parallel riding"; i.e., the primary detents 140 and 142 are the parallel riding positions of cam 136. Parallel riding positions are when the smaller chain wheel is driving the larger sprocket of the rear multiple freewheel 54, or the larger chain whee of cluster 50 is driving the smaller sprockets of multiple freewheel 54.

There is a propensity for chain 52 to rasp against the side plates of the front derailleur cage when the rider is "riding cross-over," i.e., when the smaller chain wheel of cluster 50 is driving the smaller sprockets of multiple

freewheel 54, or when the larger chain wheel of cluster 50 is driving the larger sprockets of multiple freewheel 54. The conventional means for avoiding such rasping is by providing an undesirably wide front derailleur cage, which tends to result in inaccurate and undesirably difficult shifting between the two chain wheels of cluster 50 and leads to frequent derailling. Cam member 136 completely solves this problem and enables a relatively narrow and therefore accurate front derailleur cage to be employed by providing a secondary detent adjacent each of the primary detents 140 and 142. Thus, a secondary detent 148 is provided adjacent the smaller chain wheel primary detent 140, with a peak 150 between detents 140 and 148; and similarly, a secondary detent 152 is provided adjacent the larger chain wheel detent 142, with an intermediate peak between detents 142 and 152.

When riding cross-over with chain 52 engaged over the smaller chain wheel of cluster 50, the chain angles from th smaller chain wheel rearwardly and outwardly toward smaller sprockets of the rear freewheel 54. When the smaller chain wheel secondary detent 148 is engaged over cam pin 94, cam 136 is raised to pull the front derailleur cage laterally toward the larger chain wheel, thereby relieving engagement of the front derailleur cage against chain 52 and avoiding rasping. Conversely, when chain 52 is engaged over the larger chain wheel of cluster 50, in the cross-over position, chain 52 angles rearwardly and inwardly toward larger sprockets of freewheel 54, again tending to rasp against the front derailleur cage. In this situation, by shifting cam member 136 so that the larger chain wheel secondary detent 152 is engaged over cam pin 94, the front derailleur cage is enabled to be pulled by its return sprin back toward the smaller chain wheel of cluster 50, thereby again relieving rasping of chain 52 against the chain cage. The parallel and crossτ-over riding positions will be discussed further herinafter in connection with Figures 40-43, which illustrate these riding positions.

Secondary detents 148 and 152 constitute "fine-tune" cam positions which enable fine-tuning of the front derailleur cage regardless of the relative sprocket positions of chain 52 on the front chain wheel cluster and the rear freewheel, eliminating chain rasping and enable a relatively narrow front derailleur cage to be employed for accurate positive index shifting without likelihood of derailling.

It is to be noted that the fine-tune detents 148 and 152 in cam operating face 138 are outside of the cam face range for the primary front derailleur shifting, which rang extends from the smaller chain wheel primary detent 140 up cam ramp 146 and past the peak 144 to the primary large chain wheel detent 142. Thus, as viewed in Figure 15, the fine-tune detent 148 for the smaller chain wheel is located above the primary detent for the smaller chain wheel, while the fine-tune detent 152 for the larger chain wheel is located below the primary detent 142 for that chain wheel. With the fine-tune secondary detents 148 and 152 thus located, cam member 136 will not "trip over" either of the fine-tune detents when a primary shift is effected either upwardly or downwardly between the two primary detents 140 and 142, thus avoiding rider confusion which tended to occu with prior art front derailleur fine-tune attempts where th mechanisms did tend to trip over the fine-tune and provide false indications to the rider as to the actual front derailleur shifting location.

Figures 16-19 illustrate an alternative rear handgrip shift actuator, generally designated 160, wherein the cam portion 74* and cover portion 78' of the shift actuator are combined as a unitary molded structure. A cover bushing 82 is secured within the end of cover portion 78' , preferably by ultrasonic welding, or alternatively by adhesive means. Handlebar collar 109 remains in the system as an aid in baffling against entry of dust or dirt into the region of cam portion 74' . Although the embodiment having the combined cam and cover portions 74' and 78' is simpler and

more economical to manufacture than the form shown in detai in Figures 3-11, the embodiment of Figures 3-11 is presentl preferred, since cover members 78 and bushings 82 are universally adapted for use with any of the cams for the various derailleur mechanisms. Thus, the universally usabl cover members and bushings require less custom molding. Moreover, the embodiment of Figures 3-11 is also preferable since the functional characteristics desired for the plasti used in the cover member 78 are different from the functional characteristics desired for the plastic of which cam member 74 is made. Specifically, in the embodiment of Figures 3-11, a high-strength chemically lubricated plastic such as Delrin 500CL is preferred for cam member 74. Such plastic, however, is not best suited for use in either cove member 78 or bushing 82 for several reasons. It does not provide an aesthetically pleasing appearance, it does not have good ultraviolet resistance, and it tends to be slippery when grasped. Thus, a different type of plastic is used for cover member 78 in the embodiment of Figures 3-11, such as ABS, which is easily molded and provides both an aesthetically pleasing appearance and good ultraviolet resistance.

Nevertheless, the embodiment of Figures 16-19 wherein the cam and cover members are combined into a unitary structure 160 is contemplated within the scope of the present invention. When referring now to Figures 16-19, like reference numerals are used with primes for parts which correspond to those in the embodiment of Figures 3-11. Cam portion 74* is, by way of example and not of limitation, a 5-position cam wherein the cam operating face 99' has five detent valleys 114' separated by four rounded peaks 112' . As best seen in Figures 16 and 19, cam operating face 99' rides over a pin 94*. The 5-position cam operating face 99' cooperates through control cable 101' with a derailleur mechanism (not shown) embodying a 5-sprocket multiple freewheel. The middle detent 114' is shown engaged over cam pin 94' corresponding to engagement of the drive chain with

the middle freewheel sprocket for the middle speed of the 5-speed system.

The rear handgrip shift actuator 66' shown in Figures 16-19 is rotatably mounted on the handlebar end portions 72 such that rotation of the combined cam and cover unit 160 causes axial displacement of control cable 101* operatively coupled to the derailleur mechanism. Control cable 101' extends through a diametrical bore 100' in cam pin 94', and thence through a bore 103' in the end portion of the combined cam and cover 160, terminating externally of such end portion in a crimped collar or cast-on metal bead 106" which bears against bearing plate 105' cast into the end portion of the combined cam and cover 160. Housing or casing 107* for control cable 101' has a ferrule 108' crimped on its end which is located within a counterbore 102* of the cam pin bore 100*.

Referring again to Figure 19, the axial steps or spacings between successive detents 114 corresponding to successive freewheel sprocket destinations are approximatel the same for the cam face profile 99' of cam portion 74'.

This is enabled by the fact that cam portion 74* is matched to an overall rear derailleur system wherein cable 101' has minimal stretch, and the cable housing length is minimized in extent and is of a type having minimal compressability and warp under cable tension. Such a cable system is shown in Figures 20-26, and described in detail in connection wit those Figures. Thus, as viewed in Figure 19, from the position of the uppermost detent 114' being engaged over ca pin 94", at which location the derailleur mechanism return spring has its minimum loading, to the position at which th lowermost detent 114' is engaged over cam pin 94', where th derailleur mechanism return spring has its maximum loading, detents 114' do not have to be axially separated by progressively greater increments to accommodate cable stretch and/or cable housing compression and warp, whereby substantially equal axial increments between successive detents 114' are suitable for providing chain alignment wit

successive freewheel sprockets.

To the contrary, cam face detents 114 of- cam 74 as viewed in Figure 8 have increasing axial increments or separations from the position shown where the uppermost detent 114 is engaged over cam pin 94 successively down to where the lowermost valley 14 is engaged over cam pin 94, s as to accommodate a cable system which has considerable sponginess in it, caused by stretch in cable 101 and/or compression and warp in cable housing 107 a.s the force of the derailleur mechanism return spring increases for this succession of detents 114 being engaged over cam pin 94.

Figures 20-30 illustrate another derailleur-equipped bicycle, generally designated 10a, showing details of the derailleur apparatus, a presently preferred derailleur actuating cable system, and defining locations in the derailleur and cable systems of lost motion or "slop" which are accurately accounted for in the present invention.

As with the bicycle 10 shown in Figure 1, bicycle 10a has a frame 12a including a head tube 14a, top tube 16a, main down tube 18a, seat tube 20a, bottom bracket 22a, fron fork 24a, handlebar stem 28a, handlebar 32a with end portions 72a, and down fork 34a and bottom fork 36a. The rear ends of down fork 34a and bottom fork 36a are connecte to a pair of spaced dropouts 170 within which the rear axle bolt 172 is fixedly mounted for supporting rear wheel 40a. The wheel hub rotates on ball bearings about axle bolt 172, and a lateral extension of the wheel hub supports the derailleur freewheel on its outside, with ratchet means therebetween which engages when chain power is applied to the freewheel, and disengages to allow free rolling of the rear wheel relative to the derailleur freewheel. A derailleur hanger 174 is integrally formed with dropout 170, extending downwardly therefrom.

A pedal crank, generally designated 46a, is journalled in bottom bracket 22a, and includes a pair of pedal arms 48 on opposite sides of frame 12a, and chain wheel cluster 50a on the right-hand side of frame 12a inboard of right-hand

pedal crank 46a. The chain wheel cluster shown has two chain wheels, the operation of which in connection with the present invention will be discussed in detail hereinafter. Drive chain 52a is shown engaged over the larger of the two chain wheels, and extends rearwardly therefrom into engagement with derailleur multiple freewheel 54a for applying power to rear wheel 40a. The multiple freewheel 54a shown has a 6-sprocket cluster.

The front derailleur mechanism is generally designated 56a, and the rear derailleur mechanism is generally designated 58a. Front control cable 176 connects front derailleur mechanism 56a to a front handgrip shift actuator 62 shown in Figures 2, and 12 or 13, connecting in the same manner that cable 101 connects to the rear shift actuator 6 as shown in detail in Figures 3-11. The housing, support and adjustment features for front control cable 176 are similar to those of the rear control cable, but somewhat simplified, and will be described in detail in connection with the description of the rear derailleur cable system. The rear derailleur cable system is generally designated 178, and includes rear control cable 180 which extends from rear derailleur mechanism 58a to rear handgrip shift actuator 66 that is mounted on handlebar end portion 72a. The connection of rear control cable 180 to rear shif actuator 66 is the same as shown in Figures 3-11 and described in detail in connection with those Figures.

The Rear Derailleur Mechanism

The apparatus of rear derailleur mechanism 58a is best illustrated in Figures 21 and 27-30. The novel cooperative mode of operation of rear handgrip shift actuator 66, rear cable system 178, and rear derailleur mechanism 58a is illustrated in Figures 31-36, and will be described in detail in connection therewith.

At the heart of rear derailleur mechanism 58a is a parallelogram generally designated 182 which has a rear

support body pivotally but laterally fixedly connected to hanger 174, a pair of parallel links extending forwardly from the support body, and a shifter body attached to the forward ends of the links that is shiftable laterally inwardly toward the bicycle frame 12a under the influence o cable tension, and shiftable laterally outwardly away from frame 12a under the influence of a derailleur return spring contained in the parallelogram.

The rear support or mounting body is designated 184, and is pivotally mounted on a mounting bolt 186 which is threadedly connected to hanger 174 as best seen in Figure 2 A helical pivot spring 188 around pivot bolt 186 is housed in support body 184 and biases support body 184 clockwise o forwardly about bolt 186. One end of spring 188 bears against body 184, while the other bears against a plate 190 as best seen in Figures 27 and 28. A support body angle adjust screw 191 on plate 190 bears against a shoulder 192 on hanger 174 for adjusting the effective torque of spring 188. The forward shifter body 194 of parallelogram 182 is held parallel to support body 184 by the parallelogram linkage, and shifts transversely inwardly and outwardly relative to the frame 12a, and in particular, relative to the multiple freewheel 54a. An outer parallelogram link 196 connects support body 184 and shifter body 194 by means of respective pivot pins 198 and 200; and an inner parallelogram link 202 connects support body 1984 and shifter body 194 through respective pivot pins 204 and 206. Derailleur return spring 208 is best seen in Figure 29, and is a helical spring with its coil located around pivot pin 206, and having respective arms which bear against shifter body 194 and link 202 so as to bias parallelogram 182 toward a flattened, more closed condition, thereby biasing shifter body 194 laterally outwardly relative to frame 12a and freewheel 54a. A cable clamp 210 seen in

Figures 21, 27 and 29 is mounted on outer parallelogram link 196 for clamping the end of cable 180. Increased tension on

cable 180 pulls parallelogram 182 toward a more open, rectangular configuration, thereby moving shifter body 194 inwardly relative to frame 12a and freewheel 54a.

A pulley cage 212 is pivotally supported on the inner end of shifter body 194, extending downwardly therefrom. A upper guide or jockey pulley 214 is freely rotatably supported in the upper part of pulley cage 212 adjacent shifter body 194, and a lower tension pulley 216 is freely rotatably mounted in the lower portion of pulley cage 212. Cage 212 consists of outer and inner cage plates 218 and

220, respectively, outer cage plate 218 being mounted on a cage pivot bolt 222 which projects from shifter body 194. Pulley cage 212 is biased clockwise or rearwardly by means of a cage pivot tension spring 224 inside shifter body 194 which works against body 194 and outer cage plate 218.

Chain 52a extends rearwardly from one of the two chain wheels of chain wheel cluster 50a over one of the six sprockets of multiple freewheel 54a, then downwardly and forwardly over the front of guide pulley 214, then downwardly and rearwardly over the rear of tension pulley 216, and then forwardly back to the chain wheel. Guide pulley 214 shifts laterally according to lateral movements of shifter body 194 under the influence of rear control cable 180 as directed by rear handgrip shift actuator 66 so as to shift chain 52a downwardly or upwardly from sprocket to sprocket of freewheel 54a. As chain 52a shifts from a larger to a smaller sprocket on freewheel 54a, more chain becomes available in the overall chain loop, and tension pulley 216 moves rearwardly under the influence of cage pivot tension spring 224 to take up this slack. Conversely as chain 52a shifts from a smaller to a larger sprocket of freewheel 54a, tension pulley 216 gives way forwardly against the force of tension spring 224 to provide the necessary additional chain length for the added circumference of the larger freewheel sprocket.

Rear Derailleur Cable System

The rear derailleur cable system is constructed to minimize and strictly limit lost motions or "slop" commonly found in bicycle shift cables, and make whatever lost motions that are inevitable as predictable as possible so they can be accurately taken up and compensated by cam member 74 in handgrip shift actuator 66. Such lost motions commonly occur from cable housing flexure under down-shifting cable tension toward rounding out of the cabl housing, looseness of the cable in its housing, cable housing compression, cable stretch, and lost motion in cabl adjustment barrels. Cable system 178 is also constructed t minimize friction between the cable and its housing so as t further reduce cable housing flexure, and to make down-shifting easier by substantially reducing the friction vector between housing and cable which opposes cable down-shifting movement, particuarly under the relatively high pulling force on the cable that is required for down-shifting.

With these factors in mind, the rear cable housing is provided in two relatively short sections, a forward cable housing section 226 which extends into the handlebar end portion 72 and operatively connects with shift actuator 66 as shown in Figures 5-7, and a rearward cable housing section 228 which extends from a rearward location on bottom fork 36a to the rear derailleur mechanism 58a. Most of the length of rear control cable 180 is thus free of housing, and has only minimal friction against a guide under bottom bracket 22a discussed hereinafter in connection with Figures 22 and 23. The shortness of cable housing sections 226 and 228 greatly reduces cable compression lost motion and makes it very predictable.

Cable compression is further greatly reduced by employing a substantially axially compressionless cable housing or casing described hereinafter in connection with Figures 25 and 26. The construction of such substantially

compressionless cable housing also greatly reduces cable housing flexure under cable down-shifting tension, and makes such flexure and consequent lost motion very predictable. Referring to Figure 20, forward cable housing section 226 ends at a spring-loaded front cable housing adjustment barrel 230 through which cable 180 extends and which is adjustably threadedly engaged in a front bracket 232 that is affixed to the right-hand brazon near the upper end of down tube 18a. The rearward cable housing section 228 ends at a rear housing adjustment barrel 234 through which cable 180 passes and which is threadedly adjustably engaged in a rear bracket 236 that is secured to derailleur support body 184. As best seen in Figure 24, a reduced threaded portion 238 of adjustment barrel 234 carries a helical compression spring 240 which resists inadvertent rotation of barrel 234 relative to its bracket 236. There is inevitable clearance between the barrel and bracket threads, spring 240 shifting barrel 234 slightly to the left relative to bracket 236 when cable 180 is under relatively small tension when a shift is not being made. However, during a down-shift when cable 180 is under relatively large tension, barrel 234 will move toward bracket 236 through such thread clearance, which represents lost motion in the cable system. Similar lost motion will occur between front adjustment barrel 230 and its bracket 232. A ferrule 242 is crimped over the end of rearward housing section 228 and is engaged within an axial recess in adjustment barrel 234.

Referring now to Figures 22 and 23, a cable guide bracket 244 is secured underneath bottom bracket 22a, and supports a pair of grooved, arcuate cable guides 236 and 248 under which the respective front and rear cables 176 and 180 freely slide. The front derailleur cable system, including cable 176, is the same as the forward portion of rear derailleur cable system 178. Thus, front cable 176 extends upwardly and forwardly along the main down tube 18a, passing through an adjustment barrel like barrel 230 which is threaded into a bracket like bracket 232 mounted on the

left-hand brazon, front cable 176 then having a cable housing section like section 226 of rear cable system 178 which extends from the adjustment barrel into the handlebar end portion and connects to the front handgrip shift actuator 62 in the manner best shown in Figures 5-7. The rear cable extends exposed from adjustment barrel 230 rearwardly alongside main down tube 18a, under its guide 248, and thence rearwardly along bottom fork member 36a to the rear housing adjustment barrel 234. Figures 25 and 26 illustrate the substantially axially compressionless cable housing, designated 250, which is employed for both of the cables 176 and 180, but shown with rear cable 180 therein. The core of housing 250 is an annular series of closely packed, primarily axially oriente wires 252 made of a tough metal such as steel. Wires 252 are arranged in a very slow or long helix, as for example a revolution in only about every three inches of length. The annular array of wires 252 is held in its circular configuration between an outer plastic jacket 254 and an inner plastic guide tube or liner 256. Inner guide tube 25 is made of a tough anti-friction plastic material such as a Delrin which, together with .the short lengths of cable 250 in cable sections 226 and 228, greatly minimizes cable friction in the housing. Inner guide tube 256 is closely yet freely fitted about cable 180 to minimize lost motion i the curved portions of housing sections 226 and 228. Applicant has determined that the substantially compressionless-type cable 250 not only substantially completely eliminates cable compression as a lost motion factor, but it also substantially minimizes the tendency for conventional cable to round out or give in a "monkey motion," thereby substantially eliminating two heretofore serious sources of lost motion.

Sources of Lost Motion in Rear Derailleur Mechanism

While the aforesaid cable system preferably employed as a part of the present invention has only minimal and very predictable lost motion, every derailleur system has numerous sources of lost motion which cumulatively add up to a substantial amount of lost motion at the cable connection 210, and this cumulative lost motion varies for almost every different derailleur system, over a range of from about .040 inch to about .070 inch. For positive index shifting with applicant's handgrip shift actuator 66, a separate cam member 74 is preferably provided for each type of derailleur mechanism so as to positively take up and account for the cumulative lost motion in each derailleur mechanism. The mode of operation of cam member 74 in this regard is described in detail hereinafter in connection with Figures 35 and 36.

Figure 30 illustrates some of these points of lost motion or slop in conventional derailleur systems. First, there is a wobble type of lost motion of support body 184 on its pivot bolt 186 indicated at A in Figure 30. Support body 184 torques downwardly or upwardly, depending upon whether the chain is being shifted inwardly to a larger freewheel sprocket or outwardly to a smaller freewheel sprocket. Next, there is lost motion at each of the four link pivot pins 198, 200, 204 and 206. When support body 184 torques or twists down as at A, then shifter body 194 twists upwardly, and when support body 184 torques or twists up, then shifter body 94 twists downwardly, these motions being indicated at B in Figure 30. Whenever shifter body 194 twists, the parallelogram links 196 and 202 also twist as indicated at C in Figure 30. Further, there is lost motion between cage pivot bolt 222 and shifter body 194, which translates into lost motion between pulley cage 212 and shifter body 194 as indicated at D in Figure 30.

Additionally, there is lateral lost motion of guide pulley 214 on its pivot axis.

Overshift

Shift actuator cam member 74 is not only configured at its operating face 99 to account and compensate for the cumulative lost motions referred to above, but also for an overshift increment in the down-shift direction to a larger freewheel sprocket. This overshift increment serves several functions. It is the lateral angle at which guide pulley 214 addresses the chain to the next larger freewheel sprocket which causes the larger sprocket teeth to snag the chain. By moving guide pulley 214 inwardly somewhat beyond the next larger sprocket so that the chain in effect angles across the teeth of the larger sprocket, the sprocket teeth more readily snag the chain plates to provide an earlier, more positive shift. The overshift increment also causes the chain to have its final movement during a down-shift event toward the destination sprocket from the direction of the next larger sprocket, whereby during a down-shifting event the chain makes its final approach to the destination sprocket in the same direction as it would for an up-shifting event. During an up-shifting event, as the chain approaches the smaller destination sprocket, cable tension is relaxed such that the cumulative lost motion has been relaxed or backlashed, and the force vector opposing cable movement to the final destination is small and stable because of low cable force laterally against the cable housing. The same factors hold true for a down-shift to a larger sprocket when overshift is employed so that the final destination is reached in the up-shift direction.. Accordingly, both the down-shift and up-shift events to the same freewheel sprocket will result in the same accurate alignment of the chain with the sprocket. Initial alignment which is conveniently calculated for each freewheel sprocket during up-shifting thereby also provides the correct chain positioning for down-shifting to each sprocket.

A factor which varies and which is accounted and compensated for in the cam operating face 99 of applicant's

shift actuator cam member 74 is "chain gap." Chain gap is the length of chain between a particular freewheel sprocket and the derailleur guide pulley 214. For the purpose of the present description, chain gap is hereby defined as the length of chain between its tangent contacts with guide pulley 214 and a freewheel sprocket with which the chain is engaged or is to be engaged during a shifting event. Referring to Figures 31 and 32, Figure 31 shows chain 52a engaged with the smallest sprocket 258 of freewheel 54a. This is the #6 sprocket, representing the highest gear ratio It will be seen that the chain gap, designated 259, is relatively long. Figure 32 shows chain 52a engaged with the largest sprocket 260 of freewheel 54a, and it will be seen that the chain gap 261 is relatively short. The chain gaps for the six freewheel sprockets vary successively from relatively long for the smaller freewheel sprockets to relatively short for the larger freewheel sprockets.

During down-shifting, the same lateral increment of movement of guide pulley 214 will cause the chain to approach a relatively small freewheel sprocket at a much shallower lateral angle than a relatively large freewheel sprocket, making it more difficult for the relatively small . sprocket teeth to snag the chain than for the relatively large sprocket. Thus, for positive, early shifting, it is desirable to provide greater overshift for relatively small freewheel sprockets than is necessary for relatively large freewheel sprockets. For the relatively smaller sprocket, this will provide a steeper lateral angle of approach of the chain to the sprocket-so that the sprocket teeth will more readily snag onto the chain and cause an earlier and more positive shift.

Figure 33 illustrates what is meant by "overshift." Each of Figures 33A, B and C diagrammatically illustrates rear derailleur freewheel 54 and its relationship to guide pulley 214 and chain 52a during a down-shifting event from freewheel sprocket #6, the smallest sprocket, to freewheel sprocket #5, the next smallest sprocket. _. The freewheel hub

which overrides the wheel hub is diagrammatically illustrated as 262. The freewheel sprockets are numbered i their conventional order, from 1-6. In Figure 33A, guide pulley 214 and chain 52a are operatively aligned with the # freewheel sprocket. A down-shift is to be made from sprocket #6 to sprocket #5, and Figure 33B illustrates the overshift increment. Guide pulley 214 is moved or overshifted in the down-shifting direction substantially beyond alignment with the destination sprocket #5, moving chain 52a to this overshift position. Guide pulley 214 is then relaxed back to alignment with the destination sprocke #5, being moved under the influence of derailleur return spring 208 shown in Figure 29, carrying chain 52a with it into accurate alignment with the destination sprocket #5 as shown in Figure 33C. The final, aligned location of guide pulley 214 and chain 52a of Figure 33C will be the same as the position of alignment for an up-shift from sprocket #4 to sprocket #5, the destination having been approached from the same direction with the cumulative lost motion released or backlashed, and the friction vector of the cable housing sections against the cable being the same.

Compensating for Variations in Derailleur Return Spring Force

Figure 34 shows a 6-position cam member 264, laid out flat, for applicant's rear handgrip shift actuator 66 which has a cam operating face 266 configured for cooperation wit a derailleur system embodying the cable system 178 describe above. The successive cam detent valleys from the smallest sprocket, highest gear position to the largest sprocket, lowest gear position are designated 268, 270, 272, 274, 276 and 278. The axial spacings 280 between these successive detents are substantially the same, because with the cable system 178 there is no need for any material compensation i cam face 266 for conventional cable system lost motions.

However, down-shifting from the smallest sprocket position 268 to the largest sprocket position 278 successively increases the loading on derailleur return spring 208 during the shifts from freewheel sprocket to sprocket. To compensate for this progressively increasing return spring loading, cam ramps 281 of the successive cam lobes from the smallest sprocket detent 268 to the largest sprocket detent 278 are progressively flattened for progressively increasing mechanical advantage, thereby enabling the successive down-shifting increments to be effected with substantially the same amount of torque on handgrip shift actuator 66. Thus, the configuration of cam operating face 266 is such that the arcs of rotation between the successive shift locations will progressively increase, these succesive arcs being designated 282, 284, 286, 288 and 290.

Down-Shift Event

Figure 35 diagrammatically illustrates a down-shift event controlled by a cam 292 embodied in a rear handgrip shift actuator 66 according to the invention. Cam 292 has an operating face 293 configured to produce a series of shifting increments which will reliably and repeatably produce positive index down-shifting events. As viewed, during the actual shifting event, cam pin 94 would be stationary in the horizontal rotational direction and movable by cam 292 in the vertical axial direction, while cam 292 would be movable to the left in the horizontal rotational direction. However, it is the relative rotational positioning between cam 292 and cam pin 94 which effects the shifting event, and for convenience of illustration cam 292 is shown stationary, and cam pin 94 is shown moving to the right in successive positions relative to cam 292.

During the shifting event, cam pin 94 is moved from a higher gear ratio detent 294 to the destination lower gear

ratio detent 296, cam pin 94 riding from valley 294 up cam ramp 298, over peak 300, and down backslope 302 into valley 296. Cam operating face 293 is specifically configured for optimum positive index shifting of a Shimano Hyperglide rea derailleur mechanism, and the portion of cam operating face 293 illustrated in Figure 35 is dimensioned for a down-shif event from freewheel sprocket #4 at detent 294 to freewheel sprocket #3 at detent 296. The successive axial positions of cam pin 94 relative to cam 292 are referenced to the center of cam pin 94, and are designated 1-6. In the actua mechanism of handgrip shift actuator 66, these six position represent the successive axial positions of cam 292. The combination of the Shimano Hyperglide rear derailleur mechanism 58a and applicant's rear derailleur cable system 178 have a cumulative lost motion of approximately .040 inch, and cam 292 first takes up this lost motion in its movement from position 1 to position 2. This rear derailleur mechanism 58a has a shift span from th center of freewheel sprocket 4 to the center of freewheel sprocket 3 of .112 inch. Accordingly, the next increment of movement of cam 292, from position 2 to position 3, causes this .112 inch lateral shifting movement in the derailleur mechanism 58a. Applicant's testing has determined that a .058 overshift movement of derailleur mechanism 58a will produce optimum early and positive index shifting from sprocket #4 to sprocket #3 in this particular derailleur mechanism, and accordingly cam operating face 293 is configured to provide an overshift increment of .058 inch from position 3 to position 4 in Figure 35. At position 4, cam peak 300 is axially aligned with cam pin 94.

As this shifting event progresses down backslope 302, the .040 inch takeup is first released as backlash between positions 4 and 5, and then the overshift increment of .058 inch is released between positions 5 and 6, position 6 being the destination position at which the chain is aligned with freewheel sprocket #3. A critical factor in the shift event depicted in Figure 35 is the backlash release on cam

backslope 302 of substantially the entire takeup increment of .040 inch. This assures that the derailleur mechanism 58a and cable system 178 are substantially completely relaxed to the same condition they would be in at the end of an up-shifting event, thereby assuring the same alignment between chain and sprocket for both a down-shifting event and an up-shifting event to the same destination freewheel sprocket.

The takeup increment of the cumulative lost motion (.040 inch in the example) plus the shift increment (.112 inch in the example) is considered by applicant to be a minimum limit for the axial shifting movement of the cam member during each down-shifting event. This minimum axial down-shifting movement of the cam is best stated in terms of cam lobe height, which, in Figure 35, is the height between detent 294 and peak 300, or the height between positions 1 and 4 _* Therefore, the minimum cam lobe height according to the invention is hereby defined as a sufficient cam lobe height to substantially account for both the lost motion in the derailleur and cable systems (takeup) and the spacing between the centers of the origin freewheel sprocket and the destination freewheel sprocket (shift).

It is presently preferred that the cam lobe height be sufficient that it will cause the derailleur mechanism to move the chain a sufficient amount beyond the destination freewheel sprocket in a down-shifting event so that the chain will approach the destination sprocket in the same direction as it would in an up-shifting event, such cam lobe height being sufficient to first release the backlash on the lobe backslope 302, and then allow some reverse chain movement toward the destination sprocket. Such chain reversal is an observable phenomenon. In a conventional cable system, cable housing compression and warping are only substantially completely released or backleashed when the cable tension friction vector that opposes down-shift cable movement is reversed to the lesser cable friction vector of up-shift cable movement.

It is preferred that the cam lobe heights exceed these minimum and preferred lower limits to account for wear that will increase the cumulative lost motion in the derailleur system. Applicant considers the maximum limit for applicant's cam lobe height for each down-shift event except the final one to sprocket #1 to be such that the cam lobe not cause the derailleur system 178 to move the chain sufficiently far laterally inwardly to cause a double shift, i.e., to skip on over the destination sprocket to the next sprocket. For sprocket #1, applicant considers the upper limit for the respective cam lobe height to be such that it not cause the derailleur mechanism to move the chain laterally inwardly sufficiently to derail the chain off of sprocket #1. While applicant considers these to be the upper limits for the cam lobe heights, it is presently preferred that the cam lobe heights not cause the derailleur mechanism to shift the chain laterally during any down-shifting event sufficiently to cause chain rasp against the next freewheel sprocket inboard of the destination sprocket. Nevertheless, for optimum positive index shifting, applicant prefers that each cam lobe be sufficiently high to bring the chain as close to the next freewheel sprocket as possible without the chain rasping against the next sprocket. These maximum and preferred upper limits are observable phenomena.

The following chart provides down-shifting data for a Shimano Hyperglide rear derailleur mechanism 58a utilizing applicant's rear handgrip shift actuator 66 and rear cable system 178. This chart is given by way of example only, and not of limitation. This chart illustrates the operation of the invention as heretofore described in connection with Figure 35. The first column, "Sprocket," gives the origin and destination freewheel sprockets, listing down-shift events from the smallest sprocket, #7, down to the largest sprocket, #1. The second column, "Takeup," represents movement from position 1 to position 2 in Figure 35 accounting for lost motion in the derailleur and cable

systems. The third column, "Shift," is the lateral spacing between origin and destination sprocket centers, represented by the shift increment from position 2 to position 3 in Figure 35. The fourth column, "Overshift," lists the overshift increments provided by cam 292 from position 3 to position 4 in Figure 35. The fifth column lists "Overtravel," which is the sum of "Takeup" and "Overshift," or the amount of axial cam travel greater than the "Shift" spacing between the origin and destination sprocket centers. The sixth column lists the amount of overtravel which will just cause double shift in the shifts down to freewheel sprockets 6, 5, 4, 3 and 2, and will just cause derailling in the final shift down to sprocket 1. The amount of takeup required for each down-shifting event is the same, indicating the same amount of cumulative lost motion in the systems. The shift increments vary for the different down-shift events according to variations in the freewheel sprocket spacings. The amount of overshift generally is reduced from the smaller sprockets down to the larger sprockets, principally because of successive reductions in the chain gap. In the shift from sprocket 2 to sprocket 1, the overshift is made small to avoid any possibility of derailling, and with the shortest chain gap at that location, positive index shifting is achieved with only a relatively small amount of overshift. Comparing the overtravel to the double shift figures, it is noted that the cam is configured to bring the chain closest to double shift in the region of the smaller sprockets. This is to produce early and positive index shifting despite the longer chain gaps in the region of the smaller sprockets.

Up-shift

Up-shifting to a smaller sprocket does not require overshifting for accurate centering of the chain on the destination sprocket, and release of lost motions in the derailleur and cable systems is automatic. Nevertheless, with applicant's handgrip shift actuator system in which fo a down-shift there is first takeup of the lost motion, next movement of a shift increment, and finally an overshift increment, when the shift actuator movement is reversed fro that down-shift destination position so as to shift back up to a smaller sprocket, to get over the cam peak there will be, going up the backslope 302, takeup of the lost motion which had been left after the down-shift, plus takeup of th amount of overshift, before the cam ramp slides under the cam pin as the next lower cam detent moves toward the cam pin. This up-shift event is illustrated in Figure 36, whic is the same as Figure 35 except for the reversed rotational direction of movement of cam 292. Referring for convenienc to cam pin 94 as moving relative to cam operating face 293, pin 94 starts in the higher detent 296, then rides up backslope 302 and over peak 300, and thence down cam ramp 298 and into the destination higher gear ratio detent 294. Successive positions of pin 94 relative to cam operating face 293 are indicated by the numbers 1-6. At the #1 origin position, pin 94 is detented in the higher, lower gear rati detent 296. The first increment of movement of cam 292 to the right relative to pin 94 takes up the cumulative lost motion which was left relaxed or backlashed after the previous down-shift or up-shift event. In the example, the takeup is approximately .040 inch. Next, the backslope 302 takes up the amount of overshift that would have been programmed for a down-shift from detent 294 to detent 296, in the example .058 inch. This is motion from point 2 to point 3, point 3 representing the location of pin 94 at peak 300. Then cam pin 94 rides down cam ramp 298, and the takeup-on backslope 32 is first released as backlash between

positions 3 and 4, this being approximately .040 inch in the example. Then the overshift is released between points 4 and 5, this being .058 inch. Finally, the up-shift to the smaller freewheel sprocket is effected between points 5 and 6, in the example .112 inch.

Undercut Cam

Applicant's cam member 74 shown in Figures 4-10 has sufficient circular extent for its operating face 99 to occupy an arc substantially less than 360°, as for example about 325°, with room left for a stop projection 117 at the low gear end of the operating face, for up to about seven gear ratio cam positions, with the cam ramps being gentle enough for easy down-shifting. However, with more than about seven gear ratio positions, the cam ramps may have to be undesirably steep to accommodate the necessary axial displacement for effecting the shifts, and the resulting loss of mechanical advantage may make the twisting effort for down-shifting undesirably large. Figure 37 illustrates a modified, undercut form of cylindrical cam, generally designated 304, which has an extended operating face 306 having eight shift locations while at the same time having gentle cam ramps for easy shifting with an 8-sprocket freewheel. The highest gear ratio detent for the smallest sprocket is designated 308, and in the elevational view of Figure 37 it is seen at the front of the cylindrical cam member 304. Traversing operating face 306 toward the lower gear ratio, larger sprocket locations, the second and third detents 310 and 312, respectively, are both also seen from the front of cam member 304 as viewed in Figure 37. However, the fourth detent 314 is at the rear of cam member 304 as viewed in Figure 37, but is seen through undercut region 316 of cam member 304, which is an elongated, generally helical slot defined between cam operating face 306 and a helical edge, this slot having suficient axial dimension to accommodate the diametrical thickness of the

cam pin. The next two succeeding detents 318 and 319 are still behind cam member 304, but out of view through the undercut region 316, and are therefore shown in dotted lines The final two detents 320 and 322 for the lowest two gears are again on the front of cam member 304 as viewed in Figure 37.

Fine-Tune Detents for Front Derailleur with 3-Chain Wheel

Cluster

In Figures 14 and 15, a cam 136 was shown which had two primary detents for a 2-chain wheel front derailleur cluster, with a secondary, fine-tune detent outside of each of the primary detents to counteract cross-over riding. Figure 38 is a view similar to Figure 15 showing a cam 324 operative for shifting the chain between the chain wheels of a front derailleur system embodying three chain wheels of small, medium and large diameters, having fine-tune secondary detents associated with the small and large diameter chain wheels. With three chain wheels in a front derailleur cluster, the small and large chain wheels may be spaced even further apart than they are in a 2-chain wheel cluster, so the cross-over problem referred to in connection with Figure 15 may be more severe for a 3-chain wheel cluster.

Cam face 326 of cam 324 has three primary detents 328, 330 and 332 for the respective small, medium and large chain wheels. To avoid cross-over chain rasp when the chain is engaged over the small chain wheel, pin 94 may be engaged in a secondary, fine-tune detent 334 which will cause the front derailleur cage to move toward medium chain wheel detent 330 and thereby avoid or minimize chain rasp on the derailleur cage when riding with the chain crossed over. Similarly, a fine-tune secondary detent 336 is provided outside of the large chain wheel detent 332, and engagement of cam pin 94 in detent 336 will move the derailleur cage toward the location of medium chain wheel detent 330 so as to avoid or

minimize chain rasp against the derailleur cage when riding with the chain crossed over.

Front Derailleur

Figures 39 and 42-44 illustrate details of construction of front derailleur mechanism 56a shown generally in Figure 1. The parallelogram is generally designated 338 and is best seen in Figure 39. The fixed- member of parallelogram 338 is a support body 340 which is clamped to seat tube 20a by means of a clamp 342. The derailleur cage is generally designated 344, and consists of outer and inner cage plates 346 and 348, respectively, which are connected by an upper bridge member 350 seen in Figure 39, and a lower bridge member 351 seen in Figures ^* 42, 43.and 44. An outer, upper parallelogram link 352 is pivotally connected at its ends to support body 340 and cage 344 by means of respective pivot pins 354 and 356. An inner, lower parallelogram link 358 is also pivotally connected at its ends to support body 340 and cage 344. The cage connection pin is designated 360, but the support body connection pin is masked behind a portion of the support body as viewed.

A helical spring 362 best seen in Figures 39 and 42 is engaged about outer pivot pin 360 for link 358, and bears against link 358 and cage 344 so as to bias parallelogram

338 and hence cage 344 inwardly toward frame member 20a and thus inwardly toward the smaller chain wheel. Spring 362 is covered by a spring housing 364.

An actuator arm 366 extends upwardly and inwardly toward frame member 20a as an extension of the upper, outer link 352. Front derailleur cable 176 is attached to actuator arm 366 proximate its free end by means of a cable clamp 368 on actuator arm 366.

Front derailleur mechanism 56a is controlled by front handgrip shift actuator 62 through cable 176. The lost motion factors previously discussed with respect to the rear derailleur system are minimized in the front derailleur

system by the simplicity of the mechanism and shortness of the cable. The lost motion factors may nevertheless be accounted for in the cam lobe heights in the same manner as discussed in detail with respect to the rear derailleur system and associated handgrip shift actuator.

Figure 40 diagrammatically illustrates locations of chain 52a when a bicycle rider is riding "parallel." Chain wheel cluster 50a has two chain wheels, a large chain wheel 370 and a small chain wheel 372. Rear freewheel 54a is a 6-sprocket cluster, including sprockets numbered 1-6. In Figure 40, chain cage 344 is longitudinally aligned with large chain wheel 370, and also substantially aligned with freewheel sprocket #5. In normal parallel riding, when the chain is engaged over large chain wheel 370, the rear derailleur mechanism will only be actuated to shift chain

52a between the three smallest freewheel sprockets, numbers 6, 5 and 4, and with any of these three freewheel sprockets, chain 52a will remain sufficiently aligned with cage 344 to avoid rasping against either of the outer or inner cage plates 346 and 348. Similarly, with cage 344 aligned with smaller chain wheel 372, with normal parallel riding, the rear derailleur will only be actuated to locate the chain on one of the three largest freewheel sprockets, numbers 1, 2 and 3, and chain rasp will be avoided. Figure 41 illustrates the cross-over riding situation in which chain 52a is engaged on the larger chain wheel.370, but where the rear derailleur has been actuated to place the chain over one of the three largest freewheel sprockets, numbers 1, 2 or 3. This will cause chain rasp against inner cage plate 348, unless an undesirably wide chain cage 344 is provided. Such a large chain cage is conventional to accommodate cross-over riding, but can readily lead to derailling. Still referring to Figure 41, if the chain were located over the smaller chain wheel 372, and located on one of the three smallest freewheel sprockets 4, 5 or 6, a reverse cross-over situation would occur in which the chain would rasp against outer cage plate 346.

Figure 42 shows the parallel riding situation of Figure 40, wherein chain 52a is engaged over the larger chain wheel 370, and the chain is generally centered through cage 344. Figure 43 shows the cross-over situation of Figure 41, with the chain engaged over the larger chain wheel 370 at the front, and engaged over one of the three largest freewheel sprockets 1, 2 or 3 at the rear. The chain is seen to be rasping against inner cage plate 348 at the front of chain cage 344. Figure 44 shows chain 52a again properly aligned in chain cage 344 after a fine-tune adjustment has been made with the cam 136 shown in Figures 14 and 15, the cam being moved from a position like detent 142 in cam 136 which will produce the result of Figure 43 to fine-tune detent 152 which will bring the chain into alignment with cage 344 as seen in Figure 44.

Inboard Handgrip Shift Actuators

Figures 45-50 illustrate alternative handgrip shift actuators according to the invention which are located inboard of the handlebar ends, preferably immediately inboard of conventional handgrips. This form of the invention is particularly suitable for "mountain bikes," since riders of mountain bikes like the fixed handgrips at the ends of the handlebar for best control.

Figure 45 illustrates the front end portion of a mountain bike, generally designated 370, which has a widespread handlebar 372 that angles slightly rearwardly. Conventional left and right grips 374 and 376, respectively, are located on the ends of handlebar 372. Front handgrip shift actuator 378 is engaged over handlebar 372 immediately inboard of left grip 374, and rear handgrip shift actuator 380 is engaged over handlebar 372 immediately inboard of right grip 376. The front derailleur cable system is generally designated 382, and includes front control cable 384 and cable housing or casing 386. Front cable system 382 for

mountain bike 370 is preferably the same system as that employed on the bicycle 10a shown in Figure 20, with cable housing 386 terminating at an adjustment barrel arrangement like that shown in Figure 24, cable 384 extending down alongside main down tube 388 and riding under the bottom bracket as shown in Figures 22 and 23, and with substantially compressionless cable housing like that shown in Figures 25 and 26.

The rear derailleur cable system is generally designated 390, and includes rear control cable 392, forward cable housing or casing 394., and a rearward cable housing (not shown) like that seen in Figures 20 and 21. Rear cable system 390 is preferably the same as rear cable system 178 shown in Figures 20-26 and described in detail in connection with those figures.

Figures 46-50 illustrate details of construction of front handgrip shift actuator 378. Actuator 378 has a tubular support body 396 comprised of an elongated inner portion 398 with a cylindrical outer surface 400, and a radially enlarged outer collar portion 402. Inner portion 398 extends from collar portion 402 in the direction of the handlebar end. Collar portion 402 has a cylindrical outer surface 404 which is coaxial with the cylindrical outer surface 400 of the support body inner portion 398. A cylindrical bore 406 extends through the length of support body 396 and has its axis laterally offset from or eccentric relative to the cylindrical outer surfaces 400 and 404, providing a relatively thick side of support body 396 for containing the cam actuating mechanism and receiving the cable housing end, while at the same time maintaining a minimum diametrical dimension for shift actuator 378.

An axially directed cam follower slot 408 is provided on the outside of inner body portion 398, extending the length of inner portion 398. Support body 396 is engaged over handlebar 372, and locked in fixed position relative to handlebar 372 by means of a set screw 410 seen in Figure 46.

A cylindrical cam member 412 is affixed within a generally cylindrical housing 414, being locked to housing 414 by an annular array of pins 416 seen in Figures 47 and 50. Cam member 412 has an annular inboard end 418 which rotatably seats against body collar portion 402, and a generally helical cam operating face 420 formed on its outboard end. Cam operating face 420, being configured to cooperate with the front derailleur mechanism, may have a profile similar to any of those shown in Figures 13, 15 and 38.

Rear handgrip shift actuator 380 is constructed in the same manner as front actuator 378, except for the cam face configur tion, which is adapted for cooperation with the rear derailleur system. The cam member in rear shift actuator 380 embodies the features heretofore described in detail, and may have a profile similar to any of those illustrated in Figures 8, 19, 34 or 35.

Cylindrical housing 414 has a radially inwardly directed flange 422 at its outboard end which registers with the outboard end of body inner portion 398 to provide a barrier against entry of dust and dirt into the mechanism of shift actuator 378. At the inboard end of actuator 378, housing 414 overlaps body collar portion 402 to similarly provide a barrier against entry of dust and dirt into the actuator mechanism.

A cam follower plate 424 rides generally axially in follower slot 408, and has a radially outwardly directed follower pin 426 rigidly secured thereto. Cam follower pin 426 rides against cam operating face 420 as seen in Figures 47, 48 and 49, following the profile of cam face 420. A metal bead 428, which may be made of lead, is cast onto the end of front control cable 384, and seats in a complementary recess 430 in cam follower plate 424. A ferrule 432 crimped on the end of cable housing 366 seats in a recess 434 in collar portion 402 of body 396 to complete the cable connections to shift actuator 378.

Handgrip shift actuators 358 and 360 cooperate with respective front and rear derailleur systems in the same manner as heretofore described in detail for respective shift actuators 62 and 66, with all of the same advantages. Although applicant's handgrip actuators preferably embody cam operating faces which are generally helical in configuration with the detents and peaks along the helix, it is to be understood that alternative configurations may be provided without the detents and peaks being located on the helix. For example, the cam operating face with the detents and peaks may be generally circular, with a lead screw advancing and retracting the cam member, or with a separate cam having a simple helical cam slope performing the advancing and retracting functions. While the present invention has been shown and described herein in what are conceived to be the most practical and preferred embodiments, it is recognized that departures may be made therefrom within the scope of the invention, which is therefore not to be limited to the details disclosed herein, but is to be afforded the full scope of the appended claims.