Gear shifting mechanism

Shifting mechanism

Field of invention

The present invention relates to a device for actuating a shifting mechanism with a multiple sprocket variable ratio power transmission. The invention can be embodied in a bicycle shifting mechanism.

Background of the invention

A typical shifting bicycle has a drive chain that links the pedal-driven crank to the driven wheel. The drive train can have a number of sprocket wheels (chain links) with different pitch diameters and a number of sprocket wheels with different pitch diameters. The front sprocket is coupled to the crank and rotated by the pedal. The rear sprocket is coupled to the driven wheel of the bicycle. A chain couples one of the front sprockets to one of the rear sprockets. Different gear ratios can be selected via the moving chain, allowing the chain to couple the selected sprocket to the selected sprocket.

Some bicycles have a front and rear shifting gears that can be actuated by a steel cable. The single rider can manipulate the front shifting gear train and move the chain to the selected front sprocket. The single rider can manipulate the rear shifting gear train to move the chain to the selected sprocket.

There are a variety of mechanisms that are mounted to the handle, and the rider can use the mechanism mounted on the handle to operate the front and rear shifting gears to achieve the desired gear ratio. For example, some bicycles have a pivotable lever on each side of the handle. One tie rod is coupled to a steel cable that operates the front shifting gear transmission, and the other pull rod is coupled to the steel cable that operates the rear shifting gear transmission. single The driver can select the desired gear ratio by pivoting the lever.

The GRIP SHIFT shifting mechanism provides a pair of collars that are attached to the handle. One collar is attached to the right handle of the bicycle, and the other collar is attached to the left handle of the bicycle. One of the collars is coupled to the cable that operates the front shifting gearing. The rear collar is coupled to the cable that operates the rear shifting gear train. A single rider can rotate the collar relative to the bicycle handle to select the desired gear ratio.

No. 4,201,095 to Cirami describes a bicycle transmission having a single lever that operates both front and rear shifting gears to achieve a progressive and programmed series of gear ratios. The Cirami mechanism has two flat face cams. The intermediate gear ratio is obtained in sequential increments from the lowest to highest gear ratio position of the tie rod. Cirami proposes a type of shift that avoids the gear ratio of the cross chain.

Another single-vehicle transmission is disclosed in US Patent No. 4,279,174 to Ross, which allows a single rider to operate the front and rear shifting gears via manipulation of a single controller. The Ross transmission requires a two-speed shifting gear mechanism: a front-shifting gearing mechanism that deflects the spring and a "push-pull" rear-shifting gearing mechanism. The Ross transmission is constructed to provide a progressive shift type. Ross describes a type of shifting in which four variations involve simultaneous shifting or shifting the position of the two shifting gears to provide a series of progressive gear ratios.

An electronic device for controlling the front and rear shifting gears of a bicycle is disclosed in U.S. Patent No. 5,577,969 to Watarai. A single rider can shift the device between different gears by operating a lever.

U.S. Patent No. 1,114,400 to Brix describes a mechanism for adjusting the position of a rod that controls the locomotive's spark plug controller, throttle, muffler controller, and engine clutch. Each lever can be adjusted independently. The Brix mechanism uses a two-cylindrical sleeve that is coupled and placed inside the handlebar of the locomotive. Each sleeve is associated with one of the control rods and has a helical slotted configuration on its cylindrical surface. When the locomotive rotates the handle, one of the sleeves is rotated while the other sleeve is prevented from rotating. The cam follower travels within the helical slot of the rotating sleeve, causing longitudinal movement of the associated lever.

U.S. Patent No. 5,970,816 to Savard describes a bicycle transmission that provides a mechanism for controlling the front and rear shifting gears. The mechanism operates by rotating a handle. A cylindrical tube is attached to the inner end of the handle. The tube has rails on its inner and outer faces. The steel cables from the front and rear shifting gears are individually coupled to the corresponding followers of a pair of cam followers. The cam followers are each slidable on one of the rails. As the barrel rotates, the member moves the variable speed gear train cable to select different gear ratios. The cam follower and the follower guide are disposed outside the handle and are positioned close to each other. This results in a large bulbous assembly on the inside of the handle that can be rotated separately. The split recess mechanism maintains the collar in response to the selected gear ratio. Savard's organization is similar to that of Cirami, Ross, etc., and can be combined to provide the best shifting type to avoid undesired redundant gear combinations. A mechanism similar to the Savard organization is sold by the French EGS company under the trade name Synchronous Transmission (SYNCHRO SHIFT). However, the large size of the synchronous transmission mechanism is not desirable. Its size is incompatible with standard bicycle brake levers.

U.S. Patent No. 5,447,475 to Socard discloses two separate and equivalent Different bicycle shifting mechanisms. The second mechanism provides the best shifting type to avoid cross-chains. The mechanism is actuated by a steel cable that is coupled to a handle mounted to the shifting mechanism and is provided with two tie rods; one pull rod for shifting upwards and the other for shifting downwards. The mechanism includes a cam that rotates 90 degrees at each shift.

No. 4,530,678 to Wechsler discloses a bicycle shifting mechanism that uses a cylindrical cam with a cam follower to control the rear shifting gear mechanism. The cam system is integrated into the rear shifting gear transmission mechanism, and has a cam slot cut to the outer surface thereof. The second rotary cam is used to control the front shifting gear transmission. The second cam system is integrated into the front shifting gear transmission mechanism. A steel cable mechanically couples the front and rear shifting gears so that when one moves, the other moves. Wechsler's previous shifting gear cam mechanism was formed to alternate between the large and small chain rings for each successive shift.

No. 4,900,291 to Patterson discloses a bicycle shifting mechanism having a rotary handle actuator cam that is coupled to a shifting gear transmission through a steel cable. Separate independent cams are provided to control the front and rear shifting gears. The cam faces of the cam edges are adjacent to a fixed post. The cam surface has peaks and valleys, and the cam surface uses cable tension to index the transmission. When the cam rotates, the cam slides in the longitudinal direction. The end of the cable is attached to the cam.

U.S. Patent No. 5,681,234 to Ethington discloses "Early Bicycle Automatic Transmission Transmission" which uses a speed sensor and force sensor and a programmable logic controller and two servo motors to automatically shift bicycles according to operating conditions. Transmission. Ethington reveals the type of transmission in which all gears are used in ascending order. Multiple speed changes involve simultaneous shifting of both the front and rear shifting gears.

No. 5,803,848 to Nier discloses a transmission system that employs the same type of shifting type used by Socard et al. Such a system uses a flat radial cam that is cam coupled and rotatably mounted to the handle. The Nier's system combines a cam (which operates the front shifting gear mechanism with a mechanical linkage), and the other cam has a node that actuates the electric motor to pull or release the rear shifting gearing mechanism by a predetermined amount. The best shift type is obtained by using a combination of three cams.

U.S. Patent No. 5,865,062 to Lahat discloses several mechanisms for controlling both the front and rear shifting gears to achieve the optimum shift type. These mechanisms show that a single cylinder has two cam faces, as well as a number of twin cylinders with a single cam face configuration. In all cases, the cam and follower are located outside the handle. In some cases, the cam and follower assembly are erected in separate housings rather than being pivotally mounted to the handle. In summary, these mechanisms are directed to synchronizing the control of both the front and rear shifting gears to achieve a sequential combination of pre- and post-predetermined gears.

Although bicycles have a long history of development and various shifting mechanisms have been proposed for bicycles, there is still a need for a practical shifting mechanism suitable for use in bicycles and other pedal powered vehicles. There is a particular need for a shifting mechanism that allows the user to select the desired gear ratio without separately controlling the two shifting mechanisms.

Summary of invention

The present invention provides ratio selection mechanisms and related methods. The ratio selection mechanism can be used for bicycles and other pedal power mechanisms. The ratio selection mechanism can also be used for other purposes where the gear ratio is selected via the control two mechanisms.

One aspect of the invention provides a shifting mechanism. The mechanism includes a rotary handle member having first and second rail faces on an inner surface of the interior of the bore thereof. The first and second follower members are configured to engage the first and second rail faces, respectively, and the first and second cable anchors are coupled to the first and second followers, respectively. The rotation of the handle member can simultaneously adjust the position of the first and second cable anchors.

The first and second followers are located on opposite sides of the bore.

The first and second rail faces include slots on the surface of the handle member. The one or more slots include a plurality of notches on one of its sides, and the recess can be located in the recessed position. The recess is conveniently disposed in the slot that controls the operation of the front shifting gear mechanism. In addition, the recess may be disposed in the slot to control the operation of the rear shifting gear transmission mechanism; or the recess may be distributed between the slots to control the operation of the front and rear shifting gear transmission mechanisms. In still another alternative, a separate recess mechanism can be provided to maintain the handle member in a position corresponding to the selected gear ratio.

The handle member is rotatably mounted to the hollow handle. The first and second followers are respectively coupled to the first and second cable anchors by means of members passing through the handle bores. Using such a specific embodiment, the first and second followers can extend through the longitudinally disposed slots of the handle. Each of the followers includes a head that extends through the corresponding slot and the head is wider than the neck of the corresponding slot. The follower neck may be elongated relative to the follower head. Each slot has an enlarged portion The corresponding follower head can penetrate the slot enlargement portion. The amplifying portion is located outside the normal moving range of the follower.

The handle member includes one or more substantially cylindrical cam members. The inner side wall of the cam member may face away from the first and second rail faces. The cam member can be secured to the interior of the bore of the substantially outer tubular handle member. The first and second rail faces include slots in the surface of the one or more cam members. The slots can extend through the wall of one or more cam members.

The cable anchor has a cam member projection via a longitudinal slot that is additionally provided through the handle. The shifting mechanism includes a bracket for each of the cable anchors. The width of the bracket is greater than the corresponding additional slot width.

The shifting mechanism can be used in combination with a transmission mechanism comprising: a plurality of front sprockets; a chain; a plurality of rear sprockets; and a steel cable actuating front shifting gear transmission mechanism, wherein the front sprockets can be selected to engage the chain; a cable drive actuated gear shifting mechanism that engages one of a chain and a plurality of rear sprockets; a first cable that couples the first cable anchor with the front shifting gear; and a second cable It joins the second cable anchor and the rear shifting gear transmission.

The handle member is rotatably mounted to the handle, and the first and second followers are coupled to the first and second cable anchors by a handle member, respectively, which member is slidable in the longitudinally extending recess of the handle.

Another aspect of the present invention provides a shifting mechanism comprising: a hollow handle; a member mounted to be longitudinally movable inside the handle; a cable anchor member protruding from the member through the slot of the handle wall; An actuating mechanism coupled to move the member between a plurality of selected positions.

Another aspect of the present invention provides a bicycle comprising: a frame; a handle; a plurality of front sprocket mounted to the frame; a chain; a plurality of rear sprocket; and a steel cable actuated prior shifting gear transmission mechanism, The chain can engage the selected first sprocket; after the wire is actuated, the shifting gear transmission can engage the chain with one of the plurality of rear sprockets; a first steel cable that is coupled at the first end a shifting gear transmission mechanism; a second steel cable coupled to the rear shifting gear transmission at the first end; and a shifting mechanism. The shifting mechanism includes a handle member rotatably mounted to the handle. The handle member has first and second rail faces on a substantially cylindrical inner face of the bore thereof. a first follower engages the first rail surface and is coupled to the first cable at the second end; and a second follower engages the second rail surface and is coupled to the second steel at the second end cable. The handle member rotates relative to the handle to adjust both the front and rear shifting gears.

Another aspect of the invention provides a method of controlling the position of a first member and a second member along a longitudinal axis. The method involves positioning the first member and the second member within a bore of a handle at a first angular position and a second angular position centered on the longitudinal axis. The first member and the second member respectively engage the first rail surface and the second rail surface of the inner surface of the handle. The method also involves rotating the handle centered on the longitudinal axis while maintaining the first angular position and the second angular position substantially fixed. In this way, the positions of the first member and the second member along the longitudinal axis are determined by the shapes of the first rail surface and the second rail surface, respectively.

The method also includes adjusting the first cable and the second cable position, the first cable and the second cable being coupled to the first member and the second member, respectively.

Other features of the various aspects of the invention and the description of the specific embodiments are set forth below.

Simple illustration

BRIEF DESCRIPTION OF THE DRAWINGS In the drawings, non-limiting embodiments of the present invention are illustrated, and FIG. 1 is an isometric view of a shifting mechanism mounted on a bicycle handle according to an embodiment of the present invention; FIG. 2 is a first view of FIG. A close-up view of the shifting mechanism; Fig. 3 is a partially cutaway view of the shifting mechanism of Fig. 1; Fig. 4 is an exploded view of the shifting mechanism of Fig. 1; and Figs. 5 and 6 are plan views of the shifting mechanism of Fig. 1; Fig. 5A is a longitudinal sectional view of the shifting mechanism of Fig. 1 in the plane of Fig. 5A-5A; Figs. 6A, 6B, 6C and 6D are the shifting mechanisms of Fig. 1 respectively at plane 6A-6A, 6B of Fig. 6. 1-6B, 6C-6C and 6D-6D cross-sectional views; Fig. 7 is an isometric view of the cam cylinder of the shifting mechanism of Fig. 1; Fig. 8 is an isometric view of a portion of the handle of Fig. 1; And Fig. 8B are enlarged views of portions 8A and 8B, respectively, and Fig. 9 is an enlarged isometric view of a portion of the handle of Fig. 1, the cam followers are removed; and Figs. 9A and 9B are respectively ninth The figure is an enlarged view of the area of 9A and 9B; Fig. 10 is a line diagram of a specific embodiment of the shifting mechanism, the cable extension is a function of the rotation angle of the handle; 11 is a schematic view showing the operation of a shifting mechanism according to an embodiment of the present invention; FIG. 12A is a view of a guide surface of a transmission according to an embodiment of the present invention; and FIG. 12B is a view of FIG. 12A FIG. 13 is a bottom view of the transmission according to another embodiment of the present invention; and FIGS. 13A-13D are cross-sectional views through the shifting mechanism of FIG. 13; and FIG. 14 is based on Another embodiment of the present invention, a bottom view of the transmission; and Figs. 14A-14D are cross-sectional views through the shifting mechanism of Fig. 14.

Detailed description of the preferred embodiment

The following description describes a specific embodiment of the present invention that can be used to select a gear ratio for a pedal power unit. In particular, the following description describes a bicycle having a cable actuated prior speed shifting gear mechanism that can place a drive chain on one of a plurality of front sprockets; and a geared transmission after a wire cable actuation A mechanism that places the drive chain on a selected one of a plurality of rear sprockets. However, the invention is in no way limited to such specific embodiments.

As indicated herein, a number followed by the letter "F" indicates the component associated with the front shifting gear mechanism. This number is followed by the letter "R" indicating the associated component of the rear shifting gear mechanism. The same number indicates the components associated with both the front and rear shifting gears.

Figs. 1 to 3 show that the shifting mechanism 10 is attached to the bicycle handle 12. The shifting mechanism 10 controls the front and rear shifting gear transmission mechanisms (not shown) by the steel cables 14F and 14R, respectively. The shifting mechanism 10 is operable by the rotary handle 16. The handle 16 is rotated in the first angular direction and the shifting mechanism 10 moves the cables 14F and 14R in a coordinated manner, thus selecting an increasing gear ratio. When the handle 16 is rotated in a second angular direction opposite to the first angular direction, the shifting mechanism 10 moves the cables 14F and 14F in a coordinated manner, thus selecting a decreasing gear ratio.

The handle 16 can be covered with an elastic material. The shape of the outside of the handle 16 is suitable for gripping. For example, the outside of the handle 16 may be cylindrical or generally cylindrical. The handle 16 preferably has a diameter of no more than about 38 mm so that it can be easily grasped by a child's user and an adult user with a generally sized palm. The handle 16 includes a cam cylinder 20 that is coupled to rotate relative to the handle 12 with the handle 16. The cam cylinder 20 can be integral with the handle 16 or can include separate components.

The cam cylinder 20 has a bore 21 that receives one end of the handle 12. The inner end 20' of the cam cylinder 20 is directed away from a surface to prevent the cam cylinder 20 from sliding inwardly along the handle 12. A pair of rail faces 22 are defined in the bores 21. In the illustrated embodiment, the rail faces 22F and 22R each include all of the slots.

In the illustrated embodiment (see FIG. 4), a low friction plastic material such as a hermetic pad 23 made of Delrin is disposed at the inner end of the cam 20. The airtight gasket 23 rotates along with the cam 20, facing away from the flat surface of the casing 23A, and the casing 23A is again facing away from the ram column 45, and the ram column 45 is clamped to the handle 12. The airtight gasket 23 prevents the cam 20 and the casing 23A from being worn by friction with each other, and provides a contact area with the cam 20 and the casing 23A.

The position of each of the steel cables 14 is controlled by one of a pair of members 24 (refer to Figure 5A), each of which includes a follower 26. Followers 26 each engage a guide rail The counterpart of face 22. The member 24 is positioned at a fixed circumferential surface relative to the handle 12, but is free to advance in the longitudinal direction. When the handle 16 is rotated relative to the handle 12, the follower 26, as indicated by arrows 27F and 27R, moves the member 24 in the longitudinal direction. In the particular embodiment shown, the follower 26 includes a pin that projects into the interior of the slot of the corresponding rail surface 22. The follower member 26 is cylindrical, and the diameter of the follower member 26 is slightly smaller than the width of the slit into which it projects. As best seen in Figure 6C, the outermost end of the follower 26 in the radial direction can be curved to conform to the curvature of the bottom of the rail surface 22. This allows the contact area between the follower 26 and the surface of the guide surface 22 to be increased.

Each steel cable 14 is coupled to a corresponding member 24. In the particular embodiment shown, each member 24 has a cable anchor 28 that receives one of the steel cables 14.

The cable 14 is attached to the cable anchor 28 by a steel cable anchor attached to the steel cable to a suitable device. In the specific embodiment of Figures 8 and 9, each of the steel cables 14 extends through the aperture 29 of the corresponding cable anchor 28. The cable 14 has an amplifying portion 30 (refer to Fig. 4), and the amplifying portion cannot be fitted through the opening 29. Other devices may also be used to attach the cable 14 to the cable anchor 28. For example, the steel cable 14 having the enlarged end portion may be slotted by the steel cable anchor; or a mechanical clamp may be disposed on the steel cable anchor to clamp the steel cable.

Each of the steel cables 14 is run inside a sheath 32. The position of the cable 14 relative to its sheath 32 can be adjusted by an adjustment nut 34 that is an adjustable engagement cable conduit 35. The cable duct 35 is attached to the handle 12 by, for example, clamping. In the particular embodiment shown, the cable conduit 35 is not secured to the handle 12. The cable conduit 35 is maintained in position by the cable 14, and the cable 14 is held in place by the cam follower 22. The cable conduit 35 is allowed to float slightly, allowing the shifting mechanism 10 to be eccentric, so that the shifting mechanism can absorb several shocks without causing damage. Tension of steel cable 14 The cable duct 35 is maintained to be slidably fitted toward the mast 45. A cover 36 (see Figure 2) is provided to protect the cable anchor 28 and to prevent dust and other contaminants from contacting the shifting mechanism.

The members 24 are arranged to move without interfering with each other. This item can be achieved by separating the members 24 in the circumferential direction. As illustrated, the members 24 can be opposite each other or can be spaced more closely around the circumference of the handle 12. The special members 24 can be spaced from each other by 90 degrees or several other angles from each other.

As shown in Fig. 8, the member 24 is located inside the handle 12. The follower 26 projects outward through the slot 33 of the handle 12. As shown in Figures 8A and 9A, each of the followers 26 includes a head 37 that is wider than the corresponding slot 33 and includes a neck 38 through which the neck 38 passes. As shown in the specific embodiment, the neck 38 can be elongated relative to the head 37. The slot 33 has an amplifying portion 33' through which the head portion 37 can pass. The illustrated assembly state ensures that the follower 26 fully engages the channel face 22. The amplifying portion 33' is preferably tied at a short distance from the positive length of movement provided by the rail surface 22 such that the head portion 37 of the follower 36 does not encounter the enlarged portion 33' during normal operation.

The cable anchor 28 also projects through the slot 39 of the handle 12. In the particular embodiment shown, the bracket 40 is mounted to each of the cable anchors 28. The bracket 40 is assembled to receive the enlarged end of the cable 14. The bracket 40 is wider than the slot 39 which prevents the cable anchor 28 from slipping inwardly through the slot 39 in the radial direction. The bracket 40 holds the cable anchor 28 in position so that the cable 14 is supported so that the cable 14 does not excessively rub the adjustment screw 34 and the inner surface of the cable conduit 35 when the shifting mechanism 10 is in operation. Since each steel cable 14 passes through the hole of the bracket 40 and penetrates the hole of the cable anchor 28, when the steel cable 14 is under tension, the steel cable 14 can The bracket 40 is secured to the cable anchor 28 together. Therefore, the follower 24 is limited to move only in the longitudinal direction. Bracket 40 is not required for operation of shifting mechanism 10.

The rail surface 22, as desired, moves the follower 26 longitudinally, and then moves the cable 14 to control the front and rear shifting gears (or other shifting mechanisms) that can be switched through the series as the handle 16 rotates through its range of motion Gear ratio. For the specified rotation of the handle 16, the longitudinal travel of the member 24 is determined by the helical slope of the rail surface 22 of interest (i.e., each rotational unit and longitudinal displacement). If the particular angular extent of the rail surface 22 extends generally in the circumferential direction (i.e., in the relatively low helical slope region), then when the follower 26 is in the particular angular region, the rotation of the handle 16 will cause the corresponding member 24 to Little or no vertical movement. Conversely, if the follower member 26 is attached to the angular region where the rail surface 22 has a large helical slope, the rotation of the handle 16 will cause a greater longitudinal movement of the corresponding member 24. The front and rear rail faces 22 are generally shaped differently from one another. Conversely, the handle 16 is rotated through a range of angles, causing the member 24F to move through different distances from the member 24R and/or in different directions.

In the particular embodiment shown, the rail surface 22 is shaped such that when the handle 16 is tied to any of a plurality of discrete angular positions, the cable 14 is positioned to provide a particular gear ratio corresponding to the angular position.

The shifting mechanism 10 preferably includes a recessed mechanism that allows the handle 16 to rotate the handle 16 in either angular direction with a number of resistances when the one of the angular positions is separated. In a preferred embodiment, at least one of the steel cables 14 is maintained under tension, and the corresponding portion of the rail surface 20 has a recess 41 in the direction of the rail surface. The position of the recess 41 allows the handle 16 to be in one of a plurality of angular positions The follower 26 engages one of the recesses. The recess 41 is shaped such that if the handle 16 is rotated in either angular position, the follower 26 must be moved to pull the corresponding cable. The cable 14 is maintained under tension by a spring or other deflection element (not shown). The deflection elements can be components corresponding to the components of the front and rear shifting gears, or other shifting mechanisms operated by the cable 14. Current use of front and rear shifting gear transmission components typically includes a spring, and the spring as a deflection element may have a separate actuating mechanism within the mechanism of the shifting device 10. A separate actuation mechanism is not required in a particular embodiment of the invention.

The shifting device 10 can be made extremely compact and short. As shown in Fig. 2, the shifting mechanism 10 can be sufficiently compact and short so that it does not interfere with the use of the typical bicycle brake lever 44. As shown in Fig. 3, the shifting device 10 is integrated by supporting the post 45 of the brake lever 44. The post 45 can form part of a standard brake clamp.

Bicycles can theoretically use a variety of different gear ratios. For example, a bicycle with three front sprocket wheels and eight rear sprocket wheels should theoretically have 3x8=24 different gear ratios. With conventional transmissions, all possible gear ratios are typically utilized. In reality, however, not all combinations of front and rear sprockets are expected to be used. A variety of possible gear combinations provide redundant gear ratios and/or result in severe cross-chain conditions. I hope to avoid the "cross chain". Cross-chains occur, for example, when the chain is joined to the largest front sprocket and the largest rear sprocket (or the smallest front sprocket and the smallest rear sprocket). In addition, several different front and rear sprocket combinations typically provide a very similar gear ratio. Used for a set of designated front and rear sprockets, typically with a pair of front and rear sprockets that provide the optimum shift type. For example, Table 1 shows a bicycle with 3 front sprockets with 28, 38 and 48 teeth and 8 rear sprockets with 11, 12, 15, 17, 20, 23, 26 and 30 tooth gears respectively. ratio.

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As shown in the "Include" column of Table I, a series of representations can be obtained by deleting the sprocket pairs with undesired cross-chain front-to-back sprocket pairs and providing gear ratios similar to those provided by other front and rear sprocket pairs. Expected variable type before-back sprocket pair. The resulting optimal shift type has a smaller number of gear ratios. For example, the Table I shift type includes 12 of the 24 possible front-rear sprocket pairs. The rail faces are shaped to provide an optimum shift type, such as the shift type shown in Table I, in which the handle 16 is continuously rotated in an angular direction, and the cable 14 is progressively operated to sequentially select the pair of sprockets included in the optimum shift type.

Figure 10 is a line graph showing a specified rotation angle (θ) for the handle 16 and a longitudinal displacement (x) of the cables 14F and 14R. Figure 10 shows the best shift type for the 3x7 assembly state, using 11 of the 21 possible gear combinations. As can be seen from Figure 10, the individual angular positions of the handles 16 need not be equally spaced from one another. As can also be seen from Fig. 10, the rail surface 22 extends over the handle 16 over 360 degrees so as to move through the full extent provided by the rail surface 22, the handle 16 needs to be rotated more than a full revolution.

The torque required to rotate the handle 16 increases with the tension of the cable 14, and the specified angle of rotation (θ) of the handle 16 (i.e., the helical slope of the rail surface 22), as the cable 14 is pulled through the displacement (x) increase. The friction between the various component elements also affects the required torque. Usually, when the two cables 14 are pulled, the user needs to work shifting between the split angular positions (for example, both the current and the rear shifting gears move the chain to the maximum sprocket shifting, For example, Tables 1 and 10 show the shift between the eighth gear ratio and the ninth gear ratio in the shift series, wherein the 38-15 sprocket pair shifts to the 48-17 sprocket pair). The torque that the user must apply to make such a difficult shift can be reduced by the forming rail surface 22, and the rail surface 22 is shaped such that when such a difficult shift is made, the rotation angle (θ) through which the handle 16 rotates is relatively less mechanical work. The rotation angle of the handle 16 is greater when the shifting is completed. The shape of such a rail surface 22 is shown in Figure 10 as a line having a lower relative slope. Conversely, the rail face 22 can be shaped to handle the handle 16 when less effort is required. Can be rotated through smaller angles. The change in the angle of rotation between the individual angular positions is determined by the amount of work required, allowing the rail surface 22 to have a plurality of slopes from a relatively slow to less gentle slope.

In several embodiments of the present invention, the rail surface 22 is shaped such that each follower angle of the handle 16 when the follower member 26 traverses the rail surface 22 between the adjacent intermediate portions of the angular position, the follower member 26 The moving distance in the longitudinal direction does not exceed 0.06 mm. In several embodiments, the average of each rotation angle during shifting, the movement of the follower does not exceed 0.03 mm.

Figure 11 shows a particular embodiment of the invention in which the front shifting gear mechanism 60F is controlled by a steel cable 14F and the rear shifting gear drive 60R is controlled by a steel cable 14R. The chain 61 can engage the selected one of the front sprockets FS-1, FS-2, and FS-3 by placing the front shifting gear transmission mechanism 60F at a position corresponding to one of its positions FD-1, FD-2, and FD-3. By. Similarly, the rear shifting gear transmission mechanism 60R has a plurality of positions RD-1 to RD-7 which respectively set the chains on the corresponding ones of the rear sprockets RS-1 to RS-7.

The torque applied by the user to rotate the handle 16 can be further controlled by modifying the shape of the rail surface 22 in the portion of the rail surface 22 whose control change portion relates to the change in position of the front and rear shifting gears. As shown in Figures 12A and 12B, the composition of the rail surface 22 moves only one shifting gear transmission at a time when such a shift is made. The angular position 65 corresponds to a single shift in which the rail surface 22F shifts the shifting gear transmission mechanism 60F (refer to Fig. 11) and the rail surface 22R shifts the shifting gear transmission mechanism 60R (refer to Fig. 11). As is most clearly shown in Fig. 12B, in the first portion 66 of the angular portion 65, the rail surface 22R is at an angle, so that the rear shifting gear transmission 60R is shifted, and The guide rail surface 22F does not have a slope, so the front shift gear transmission mechanism 60F does not shift. In the second portion 67 of the angular portion 65, the rail surface 22F is at an angle, so that the front shifting gear transmission mechanism 60F is shifted, and the rail surface 22R does not have a slope, so that the rear shifting gear transmission mechanism 60R does not shift.

Several special variables involve changing the position of both the front and rear shifting gears. For example, as shown in FIGS. 10 and 11, the shift between the fourth gear ratio and the fifth gear ratio and between the eighth gear ratio and the ninth gear ratio involves changing the front shift gear transmission mechanism 60F and the rear shift gear transmission mechanism 60R. The location of the person. In several embodiments of the invention, some multi-speed gear shifting involves shifting one shifting gearing and then moving the other of the shifting gears. For example, when the fourth gear ratio is switched to the fifth gear ratio, the guide rail faces 22R and 22F can be formed so that the rear shift gear transmission mechanism 60R moves first, so that the chain 61 is moved by the fourth rear sprocket (RS-4) to The large third rear sprocket (RS-3); and then the front shifting gear transmission 60F moves, causing the chain 61 to be moved from the first front sprocket (FS-1) to the larger second front sprocket (FS- 2). When the fifth gear ratio is shifted downward toward the fourth gear ratio, the movement order of the front transmission gear transmission mechanism 60F and the rear transmission gear transmission mechanism 60R is reversed. Other multiple shifting gear shifts can be implemented in a similar manner, thus allowing one shifting gear to move before another mechanism.

It will be appreciated that the foregoing specific embodiments provide a bicycle transmission that can be made into a compact and powerful unit. One feature that facilitates making the shifting mechanism 10 compact and short is that the cable anchor 28 is positioned on the inner side with respect to the mast 45, while the cam cylinder 20 and the follower 26 are located outside with respect to the mast 45. The cam follower 24 is moved in the longitudinal direction inside the normal pupil of the cymbal column 45.

Although the invention has been described with reference to specific embodiments, the invention is not limited to the specific embodiments described herein. It will be apparent to those skilled in the art that many changes and modifications may be made in the embodiments of the present invention without departing from the spirit and scope of the invention. E.g:

The shifting mechanism according to the present invention can be adapted to control a "push-pull" shifting gear transmission;

The present invention can be applied to selecting a gear ratio other than a bicycle transmission. The present invention is applicable to a pedal powered vehicle such as a pedal power tricycle, a scooter, a pedal powered water scooter, and the like. The invention can be applied to other devices to select a gear ratio, and other devices include a handle and a suitable variable ratio power transmission;

The shifting mechanism other than the shifting gear transmission mechanism can be controlled by the transmission gear mechanism. For example, the shifting gear mechanism according to the present invention can be used to select a gear ratio for a transmission mechanism including a front or rear shifting gear transmission mechanism and a variable ratio gear train inside the transmission hub;

Using an additional rail surface 22 and associated coupling to a third steel cable, the shifting mechanism in accordance with the present invention can be used to select a gear ratio in a transmission having three shifting mechanisms. For example, a transmission mechanism has front and rear shifting gears and an additional variable ratio gear train inside the transmission hub;

̇ Although the shifting mechanism 10 shown in the drawings is associated with a right handle, the shifting mechanism according to the present invention may be coupled to a left handle or a handle that is not mounted to the handle;

The number of separate angular positions of the individual gear selection mechanisms may vary (ie, in the particular embodiment shown, the number of front and rear sprockets may vary);

The choice of the specific gear ratio is not particularly limited in the present invention. The gear ratio used is required to provide the optimum shift type. Determining the optimum shift type for any shifting gear train is fairly straightforward, arranging the gear ratios in ascending order and selecting the order in which the cross-chains are minimized. This is not difficult for a skilled person, and is a clear starting point for any integrated transmission system.

Instead of being disposed inside the handle bore, the member 20 can be initially slid at the longitudinal slot of the outer surface of the handle as shown in FIG. As a further alternative, the handle 12 includes a flat surface 70A on which the member 24 slides, as shown in FIG.

Instead of using a steel cable 14 to control the operation of the shifting gear transmission, the transmission according to the present invention includes a hydraulic or pneumatic mechanism that controls the shifting device, such as a shifting gear, in response to movement of the follower 26. The operation of the transmission mechanism.

Thus, the scope of the invention is defined by the scope of the following claims.

<p>10Transmission mechanism</p><p>12 bicycle handle</p><p>14F, 14R steel cable</p><p>16handle</p><p>20Cam Cylinder</p><p>20'Inside</p><p>21</p><p>22, 22F, 22R rail surface</p><p>23 airtight cushion</p><p>23AShell</p><p>24, 24F, 24R components</p><p>26 Followers</p><p>27F, 27R arrows</p><p>28Steel cable anchors</p><p>29</p><p>30Amplification</p><p>32sheath</p><p>33 slotting</p><p>33'Amplification</p><p>34 Adjusting nuts</p><p>35Steel cable conduit</p><p>36 Cover</p><p>37 head</p><p>38 neck</p><p>39 slotting</p><p>40 bracket</p><p>41 Notch</p><p>44</p><p>45</p><p>60FFront gear transmission</p><p>60R rear shifting gear transmission</p><p>61Chapter</p><p>65 angular position</p><p>66Part 1</p><p>67Part II</p><p>70 slitting slot</p><p>70A flattened surface</p>

1 is an isometric view of a shifting mechanism mounted on a bicycle handle according to an embodiment of the present invention; FIG. 2 is a close-up view of the shifting mechanism of FIG. 1; and FIG. 3 is a shifting mechanism of FIG. Partial cutaway view; Fig. 4 is an exploded view of the shifting mechanism of Fig. 1; Figs. 5 and 6 are plan views of the shifting mechanism of Fig. 1; and Fig. 5A is the shifting mechanism of Fig. 1 for Fig. 5A - Longitudinal section of the 5A plane; 6A, 6B, 6C and 6D are cross-sectional views of the shifting mechanism of Fig. 1 in planes 6A-6A, 6B-6B, 6C-6C and 6D-6D of Fig. 6, respectively; Fig. 7 is Fig. 1 An isometric view of the cam cylinder of the shifting mechanism; Fig. 8 is an isometric view of a portion of the handle of Fig. 1; Figs. 8A and 8B are enlarged views of the portion of Fig. 8 in the regions 8A and 8B, respectively; 1 is an enlarged isometric view of a part of the handle, the cam follower is removed; the 9A and 9B are respectively an enlarged view of the 9th and 9B regions; and FIG. 10 is a specific embodiment of the shifting mechanism, The cable extends as a function of the rotation angle of the handle; FIG. 11 is a schematic view showing the operation of the shifting mechanism in accordance with an embodiment of the present invention; and FIG. 12A is a guide rail of a transmission in accordance with an embodiment of the present invention. FIG. 12B is an enlarged view of a portion of the rail surface of FIG. 12A; FIG. 13 is a bottom view of the transmission according to another embodiment of the present invention; and FIG. 13A-13D is through FIG. a cross-sectional view of the shifting mechanism; and FIG. 14 is a transmission in accordance with another embodiment of the present invention FIG bottom; 14A-14D and the second picture shows a sectional view through the first transmission mechanism 14 of FIG.