CN1057055C - Bicycle derailleur cable actuating system - Google Patents
Bicycle derailleur cable actuating system Download PDFInfo
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- CN1057055C CN1057055C CN95106053A CN95106053A CN1057055C CN 1057055 C CN1057055 C CN 1057055C CN 95106053 A CN95106053 A CN 95106053A CN 95106053 A CN95106053 A CN 95106053A CN 1057055 C CN1057055 C CN 1057055C
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Abstract
A bicycle gear shifting system having rotatable front and rear handgrip shift actuators operatively associated with control cables. In some forms of the invention the control cable is directly actuated by the handgrip rotator, while in other forms the shifter rotator drives a separate 'jack spool' which in turn actuates the control cable. A cam on either the handgrip rotator or the jack spool is configured so as to substantially compensate for increasing force of the derailleur return spring during down-shifting. Compensation is provided in the shift actuators of the invention for various lost motions in the derailleur shifting mechanisms and control cable systems. The shift actuators of the invention also provide overshift movement of the derailleur mechanisms in the down-shifting direction so as to overshift the bicycle chain a sufficient amount beyond the destination derailleur sprocket so that the chain will approach the destination sprocket in the same direction as it would in the up-shifting direction. The shift actuators of the invention also provide equalization for the higher derailleur return spring force during down-shifting than during up-shifting, and allow fine-tuning to avoid chain rasp, which is particularly important for cross-over riding.
Description
The application is dividing an application of No. 93102614.8 patent application.
The present invention is the part continuation application of No. 07/672,431, the U.S. Patent application submitted on March 20th, 1991 for bicycle change gear transmission device steel cable actuating system.
The present invention relates to the gear change system of change gear transmission formula bicycle, specifically, in this system that relates to, the front and rear derailleur is respectively by rotating handle gear shift actuating device accuracy control.
In the technical field of bicycle change gear transmission device gear change system, just feel for a long time but and unsatisfied needs be a kind ofly in gearshift procedure, not require a hand, or at least one thumb leaves the system of handlebar.The gearshift of many derailleurs is to activate by the gear-shift lever that is installed on the down tube, and gear-shift lever is mounted on the pipe in some system, and gear-shift lever is mounted on the handle in other systems.This gear-shift lever that is installed on pipe or the following pipe all requires a hand to leave handle fully in gearshift procedure.Being installed in gear-shift lever on the handle and can being lifted away from handle and pushing off lever with thumb and activate of some derailleurs with thumb, but this also can influence the control to bicycle, and be clumsy, therefore most of cyclists leave handle with hand and remove mobile gear-shift lever.For safety with conveniently need both hands just can not handle derailleur from handle.Although feel for a long time need a kind of like this derailleur gear change system, just known to the applicant, still do not exist both hands not leave the gear change system that handle just can be finished the derailleur that gear shift moves in the prior art.
Needing to use hand, is that the gear change system of the derailleur of the thumb typical prior art of leaving handle is disclosed in following US Patent at least: the 4th, 055, No. 093, and the 4th, 194, No. 408, the 4th, 201, No. 095, the 4th, 384, No. 864 and the 4th, 548, No. 092.
The gear change system technical field midium or long term of bicycle chain puller feel but still unsatisfied needs be a kind of can " more shelves (overshifting) " but uncomplicated, expensive again comparatively speaking system.So-called " shelves more " are exactly chain overshoot sprocket wheel, get back to the motion of the position that aligns with the target sprocket wheel then again.Know for a long time that people in the art the motion of this shelves more needs for gear shift more successfully early in the gear down process.Great majority are dialled chain device gear change systems and are not finished mounting mechanism in this shelves more any, thereby the cyclist needs the position of mobile modestly gear-shift lever directed overshoot sprocket wheel, and then get back to the target sprocket wheel.This requires the cyclist to accomplish two things, and one is the definite degree of shelves more that needs, and another part is to grasp the time of getting over shelves.To obtain the satisfied motion of shelves more by this means and need cooresponding skill.
Applicant's Paterson (Patterson) is a prior art US Patent 4,900, No. 291 and the 4th, 938, No. 733 patentee, also be the co-inventor of No. the 07/672nd, 431, above-mentioned relevant patent application, that the gearshift of above-mentioned three disclosed bicycle chain pullers of patent document has is intrinsic, a shelves feature more automatically.The present invention finishes the identical function of shelves more, and simple in structure, and cost is low.
The applicant knows that two other discloses the existing patent of the gearshift of the bicycle chain puller with intrinsic feature of shelves more, and promptly US Patent the 4th, 267, No. 744 and the 4th, 384, and No. 864.The mechanism of these two patents is all very complicated.The device of these two patents all can be determined shelves path increment more voluntarily, but all can not determine the shelves time more.This all relies on the cyclist, and he at first will move to gear-shift lever P PARK Position P more, and then it is moved to normal gear.
Above-mentioned two prior art patents more another problem of gear mechanism to be them all provide the identical stroke of shelves more for each sprocket wheel of rear shifter, problem is in many gear transmission system, for different free gear sprocket wheels, the best scope of shelves stroke is different more, another problem of the intrinsic feature of shelves more is in above-mentioned two patents, and the stroke of shelves more best for other free gear sprocket wheel is that promptly the dead slow near wheel is all too big than sprocket wheel for No. 1 sprocket wheel.For the best of other sprocket wheel more the shelves path increment cause the chain that takes off easily from No. 1 sprocket wheel, this may major injury bicycle.Therefore, owing to the path increment of shelves more to all sprocket wheels all is identical, so the gear mechanism more of above-mentioned two prior art patents all can not produce enough strokes of shelves more, so that carry out best gear down action by most of free gear sprocket wheels.
Long-term another problem paid close attention to of people is the accurate anterior gear transmission system of wishing that a kind of can not only carrying out " parallel storing (parallel riding) " is set and can carry out " cross over and put (cross-over riding) " in this professional domain.For example, the anterior gear transmission system of a pair of sprocket wheel, parallel storing is promptly served less free gear sprocket wheel than hinge wheel, and serve big free gear sprocket wheel than minor sprocket, cross over putting is that chain can be from being across to big free gear sprocket wheel than hinge wheel, or chain can be from being across to less free gear sprocket wheel than minor sprocket.The spanning position of this chain causes " chain friction (chain rasp) " problem easily, and the solution to this problem in the general prior art is to make the anterior chain box of dialling the chain device have the gap of broad between boxboard.Do although it is so and can reduce chain friction, but also can cause gear shift inaccuracy and the problem of taking off chain again and again.In aforesaid U.S. Patent the 4th, 900, No. 291 and the 4th, 938, solved this problem in No. 733 and the 07/672nd, No. 431 disclosed device of relevant U.S. Patent application, device of the present invention also has simple in structure and cheap advantage.
In in the art another problem that relates to the gear change system of rear shifter be, in dialling chain device and steel cable actuating system thereof, many lost motion points are arranged, these lost motions are accumulated as a sizable lost motion total amount, for example about 0.040 to about 0.070 inch.The applicant finds, in the gear down course of action, in order to carry out accurate classification gear shift, must eliminate the lost motion of all this accumulations substantially before the shelves more of stroke and actual gear shift increment on the gear shift actuating device.The aforesaid U.S. Patent the 4th of applicant's Paterson, 900, the 291 and the 4th, 938, No. 733 and relevant U.S. Patent application the 07/672nd, No. 431 device provides compensation to the lost motion of above-mentioned accumulation, and device of the present invention also provides compensation in a kind of simple and economic mode to above-mentioned accumulation lost motion.
People recognize for a long time in this professional domain, and turning handle can be used for control vehicle mechanism, specifically as motor bike and bicycle.Some such devices are disclosed in No. the 829th, 283, the French Patent (FRP).Recently other commercially available device " banked winding posture (simple spools) " outside handle installs, its shortcoming is: (1) steel cable pulling rate is too big, (2) required torque that acts on the selector of rotation is too big, and (3) need drive gear-shift lever with thumb.Be applied to first kind of said apparatus on the bicycle change gear driving device known to the applicant and be described US Patent the 4th at applicant's Paterson, 900, No. 291 and the 4th, 938, disclosed arm revolving gear gearshift in No. the 07/672nd, 431, No. 733 and the above-mentioned relevant U.S. Patent application.The present invention also provides such device in a kind of simple and economic mode.
EP423779 discloses another kind of turning handle formula bicycle shift device.
In view of the above-mentioned problem with other that exists in the prior art, basic purpose of the present invention is to solve the problem that exists in the gear change system of bicycle chain puller of the prior art.
Another object of the present invention provides a kind of gear change system of bicycle change gear driving device, this system has a gear shift actuating device, it can make things convenient for and is sleeved on the handle rotationally, thereby the cyclist need not when gear shift a hand or thumb leaves handle, thereby make the more convenient and safety of gear shift.
Another object of the present invention provides a kind of gear change system of bicycle chain puller, its handle gear shift actuating device is simple in structure, cheap, but use in conjunction with dialling the chain device, the performance of its improvement has all surpassed the gear change system of dialling the chain device of most prior art in each side.
Another object of the present invention is a kind of bicycle change gear driving device, has one handle gear shift actuating device, and this actuating device has " coiling posture (Jack spool) " device and is used for spurring or the pine oil steel cable according to the rotation of handle rotating element.
Another object of the present invention provides a kind of coiling posture handle gear shift actuating device of novelty, it is characterized in that bobbin winder bracket is driven by steel cable by the handle rotating element.
Another object of the present invention provides a kind of coiling posture handle gear shift actuating device of novelty, it is characterized in that bobbin winder bracket by the handle rotating element by gear drive.
Another object of the present invention provides a kind of handle gear shift actuating device of bicycle chain puller, it is characterized in that being provided with escapement between the fixed body of handle rotating element and handle actuating device.
Another object of the present invention provides a kind of coiling posture handle gear shift actuating device of bicycle chain puller, it is characterized in that between bobbin winder bracket and fixed sturcture escapement being arranged.
Another object of the present invention is a kind of turning handle gear shift actuating device of the posture bicycle chain puller that winds the line, it is characterized in that utilizing bobbin winder bracket to make the control steel cable of dialling the chain device with desirable direction, preferably pass the gear shift actuating device, so that reduce the cliding friction of steel cable to greatest extent with the direction that is basically parallel to handle.
Another object of the present invention provides a kind of bicycle chain puller gear change system, can consider and compensate the many lost motions in dialling chain device and actuating steel cable thereof fully, thereby can accurately finish the classification gear shift.
Another object of the present invention provides the handle gear shift actuating device of a kind of gear for cycle mechanism, it is characterized in that compensating lost motion at least in part by a kind of unsteady spring installation, the floating spring means for engaging is between a bobbin winder bracket and a fixed installation part.
Another object of the present invention provides a kind of gear change system of bicycle chain puller, wherein, the factor of steel cable lost motion such as steel cable shell compressibility and warpage are eliminated to greatest extent, and it is become to predict, thereby help accurately to determine and compensate all accumulation lost motion factors.
Another object of the present invention provides a kind of gear change system of bicycle chain puller, wherein a turning handle gear shift actuating device with dial chain device cooperating, so that make torsion that the cyclist uses basic uniformity gear down easily, although the pull back spring power of low more group of chain device of speed ratio is big more by whole gears.
Another object of the present invention provides a kind of gear change system of bicycle rear shifter, and the pull back spring power of wherein dialling the chain device is compensated, so gear down and the power of changing the basic identical size of high-grade action request.
Another object of the present invention provides a kind of gear change system of bicycle chain puller, wherein, although perhaps the distance between different sprocket wheels has difference, although and when gear down to No. 1 is the sprocket wheel of speed ratio minimum, wish restriction more the shelves amount avoiding taking off chain, turning handle gear shift actuating device with dial chain device cooperating and can provide the best amount of shelves more for gear down.
Another object of the present invention provides a kind of gear change system of bicycle chain puller, and wherein, a turning handle gear shift actuating device has intrinsic shelves ability more and structure is very simple.
Another object of the present invention provides a kind of gear change system of bicycle chain puller, and this system has the intrinsic ability of shelves more, but does not require that manual input limits all or part of shelves more and activates.
Another object of the present invention provides a kind of gear change system of bicycle chain puller, wherein, one turning handle gear shift actuating device moves in order to carry out the classification gear shift as far as possible reliably and accurately, and implements best grade increment more for each sprocket wheel of dialling the chain device.
Another object of the present invention provides a kind of gear change system of bicycle chain puller, wherein, dial the chain device and activate by a turning handle gear shift actuating device, this actuating device can the accurate adjustment gear to avoid chain friction, particularly in leap storing process.
Another object of the present invention provides a kind of gear change system of bicycle chain puller, and this system has the intrinsic function of shelves more, and wherein, shelves are regularly set up automatically by natural gear shift campaign more, and do not require cyclist's input.
Another object of the present invention provides a kind of handle gear shift actuating device, it is characterized in that having a kind of " nautilus " shape cam gear of novelty, dial the increase of pull back spring power of chain device and the minimizing of dialling the pull back spring power of chain device when changing top grade in the time of gear down can being compensated when being used to spur steel cable, thereby the alerting ability that can be applicable to various group of chain device is provided, and can carries out the amount of spin of handle rotating element of any needs so that carry out the linearity pulling amount of corresponding required tricing line steel cable.
Another object of the present invention provides a kind of gear change system of bicycle chain puller, and this system has the handle gear shift actuating device that is rotatably installed in inboard, handle end on the handle.
According to the present invention, one is equipped with front and rear portions and dials the bicycle of chain device and have the front and rear portions handle gear shift actuating device that is sleeved on rotationally on the handle, forward handle gear shift actuating device is dialled chain device cooperating with the front portion at work and is made anterior group chain device gear shift, and handle gear shift actuating device in rear portion makes the rear shifter gear shift with the rear shifter cooperating at work.Rear handle gear shift actuating device preferably is contained in the handle right side, and forward handle gear shift actuating device preferably is contained in the left side of handle so that be adapted to most of cyclists, and this is because rear shifter is dialled the gear shift more frequently of chain device than the front portion.
The present invention has the one handle rotating element, can be substantially is used for rotating and gear shift in alignment with the pivot center of handle, and alleged " bobbin winder bracket " of applicant can be around a rotational that preferably is basically perpendicular to handle.The handle rotating element mechanically is connected in bobbin winder bracket, therefore, rotation at gear down direction upper handle rotating element can cause the corresponding rotation of bobbin winder bracket on the gear down direction, and the handle rotating element can cause also that in the backward rotation of changing on the high-grade direction bobbin winder bracket changes high-grade backward rotation accordingly.Dial chain device control steel cable and be connected in bobbin winder bracket, therefore, the gear down rotation of bobbin winder bracket can be revolted the pull back spring power of dialling the chain device and be spurred steel cable, bobbin winder bracket change high-grade the rotation then and harmonious the pine oil steel cable of the pull back spring of dialling the chain device.
In some form of the present invention, being connected between handle rotating element and bobbin winder bracket is that a kind of short steel rope connects.During handle rotating element gear down is rotated, this short steel rope connects the corresponding gear down pulling that is pulled the gear down rotation that causes bobbin winder bracket and dials chain device control steel cable, the top grade that changes of handle rotating element rotates then pine oil steel cable connection, makes the pull back spring power of dialling the chain device by dialling the effect of chain device control steel cable can cause the high-grade rotation of changing of bobbin winder bracket.
In another kind of form of the present invention, mechanical connection is that gear transmission connects between handle rotating element and bobbin winder bracket, preferably but need not to be bevel gear and connect.In gear-driven form, the gear down of handle rotating element is rotated the direct bobbin winder bracket that drives and is done the rotation of gear down direction so that the control steel cable of chain device is dialled in tension, and the direct bobbin winder bracket that drives of high-grade rotation that changes of handle rotating element changes high-grade direction rotation, so that pine oil is dialled the control steel cable of chain device.
The handle rotating element and be fixed in the part of handle or structure between can implement to engage for the click of various speed ratios when chain being placed on each free wheel sprocket or each forward sprocket (promptly for).In gear-driven form of the present invention, because in gear down with change that transmission all is the failure-free transmission between high-grade both direction upper handle rotating element and the bobbin winder bracket, so above-mentioned joint can be located immediately at bobbin winder bracket and be fixed between the part or structure on the handle, so that realize the gear shift actuating device and dial that the most direct click engages between the chain device.
The best solderless wrapped connection of part of gear shift actuation ends of control steel cable of dialling the chain device is on one " nautilus " shape cam.During cam was made gear down and rotated, the control steel cable was to spur on the radius that reduces gradually of nautilus shape cam, like this and the pulling moment of torsion that progressively increases compensate the pull back spring power that progressively increases of dialling the chain device.In contrast, during this cam changes high-grade the rotation, the control steel cable of dialling the chain device on the radius that cam increases gradually by pine oil to adapt to the pull back spring power that reduces gradually of dialling the chain device.
Have in the form that between handle rotating element and retaining element or structure gear engages of the present invention, the handle rotating element has a series of preferably corresponding to the ratchet notches of rear portion free gear sprocket wheel number or anterior chain link number.These recesses of handle rotating element are crossed on a spring installation, in the groove of this spring installation on being fixed in the fixed sturcture of handle in two spacing controlled slips.Spring installation its two spacing between slidably shift movement eliminate the lost motion of dialling in chain device and the steel cable system thereof during making the gear down of handle rotating element before actual gear shift action occurs, but then during changing top grade pine oil fall these lost motions.The above-mentioned sliding action of spring installation also provides the increment of shelves more of group chain device control steel cable motion during gear down.
In gear-driven form of the present invention, the ratchet ball device that bobbin winder bracket can have corresponding to the ratchet notches stop motion mechanism of rear portion free gear sprocket wheel number or anterior chain link number such as spring bias voltage can be stated from the fixed sturcture that is fixed on the handle.In this case, in the transitional slide motion of the independent spring installation of spacing of stop, make handle rotating element and bobbin winder bracket can eliminate above-mentioned lost motion and be provided at gear down during the increment of shelves more of control steel cable motion.
Slidably the spring installation with displacement can change the taller springs rigidity of changing top grade into from the low spring stiffness of gear down, so that the taller springs power of chain device pull back spring when gear down is dialled in basic compensation.Perhaps, also can compensate the pull back spring power of dialling in the chain device, promptly provide less than the inclination angle of changing high-grade slope on the gear down slope of ratchet notches by following manner.
The above-mentioned slidably spring installation of displacement can eliminate lost motion and the increment of shelves more of steel cable motion is provided, this spring installation preferably also has an additional function, even the handle rotating element rotates a less relatively non-gear shift amount before and after any main stop position, so that make the cyclist go forward the mobile chain in back so that eliminate chain friction at each chain link or free gear chain wheel location, and no matter chain may be in where going up of rear shifter free gear, this point is a particular importance for crossing over storing.
Handle gear shift actuating device of the present invention, according to present cyclist's requirement, the fixed handle inboard that is preferably in handle is contained on the handle.But handle gear shift actuating device of the present invention can be installed in the handle both ends equally or be installed on the position of any needs of handle.
An importance of the present invention is the common actions between in handle gear shift actuating device and many different gear transmission system any one.In the various gear transmission system each all has soluble special operating feature in the bobbin winder bracket nautilus shape cam of the present invention, these characteristics are included in the various lost motions of dialling in chain device and the steel cable system thereof, spacing in free gear sprocket wheel or the variation of chain interannular, dial the pull back spring power of chain device, and make rate of change of chain this pull back spring power when being displaced downwardly to big free gear sprocket wheel or chain link or upwards moving to less free gear sprocket wheel or chain link or the like when dialling the chain device.Special nautilus shape cam among the present invention, its special profile solves and/or has compensated the above-mentioned special characteristics of any concrete gear transmission system, thereby all become early reliable and classification gear shift that accurately aim at from another the gear shift each time of a free gear sprocket wheel or chain hoop.Therefore, the cam of gear shift actuating device of the present invention can with the gear transmission system co-operation with compensation in dialling chain device and steel cable system thereof the accumulation lost motion and provide the best amount of shelves more to each gear during in gear down.
The intrinsic motion of shelves is more all considered in design on the cam of handle gear shift actuating device of the present invention, thereby provides best shelves more to each gear down action.Shelves more so also are not required for more shelves and regularly carry out independent manual input; Rotating naturally of handle gear shift actuating device on the handle automatically is shelves timing more.
Consult following explanation and accompanying drawing and will more clearly understand above and other objects of the present invention and advantage.
Fig. 1 is the partial side view of bicycle, reflects forward and backward group of chain device, and according to the gearshift of front and back of the present invention change gear mechanism;
Fig. 2 is the partial enlarged view of rear shifter shown in Figure 1;
Fig. 3 is the partial enlarged view along 3-3 line among Fig. 1;
Fig. 4 is the part sectional view along 4-4 line among Fig. 3;
Fig. 5 is the part figure along 5-5 line among Fig. 2, and part is cut open, and part is not cut open;
Fig. 6 is the partial view along 6-6 line among Fig. 2, and part is not omitted and drawn;
Fig. 7 is the cutaway view along 7-7 line among Fig. 6;
Fig. 8 is along 8-8 line partial view among Fig. 2, and part is not omitted and drawn;
Partial enlarged view shown in Figure 9 is represented the adjustment feature of dialling the chain device at rear portion shown in Figure 2;
Figure 10 is the part sectional view along 10-10 line among Fig. 2;
Figure 11 is the block diagram of the part of shown in Figure 2 group of chain device, each point of indication lost motion;
Figure 12 is the expression scheme drawing of shelves more;
Figure 13 is anterior office's cutaway view of dialling the chain device;
Figure 14 is the scheme drawing of the parallel storing of expression;
Figure 15 is that the scheme drawing of putting is crossed in expression;
Figure 16 is the scheme drawing of the parallel storing of expression;
Figure 17 is similar to Figure 16, is that the scheme drawing of putting is crossed in expression;
Figure 18 is similar with 17 to Figure 16, and expression is revised leap situation shown in Figure 17 by the mode of click spring one of lock position in it being shifted to another lock-bit position;
Figure 19 is the local diagrammatic sketch of mountain bike handle end, represents first kind of shovel cams of front and rear handle gearshift of the present invention;
Figure 20 is the sectional elevation along 20-20 line among Figure 19, the inner end of the shovel cam handle gear shift actuating device (with respect to the handle end) of expression rear shifter, and the rear portion of extending therefrom control steel cable conduit;
Figure 21 represents some CONSTRUCTED SPECIFICATION of rear handle actuating device along the axial cutaway view (for handle) of 21-21 line among Figure 20;
Figure 22 is the sectional elevation along 22-22 line among Figure 21, and expression is according to the ratchet system in first kind of shovel cams of rear shifter transmission device of the present invention;
Figure 22 A is the view of the click spring in the present invention's first shovel cams shown in Figure 22;
Figure 23 is the sectional elevation along 23-23 line among Figure 21, expression shovel cam structure, wherein, first increment of camming surface in the gear down motion of the handle gear shift actuating device of rear shifter, wherein, click spring becomes lower spring constant from higher spring constant, so that the pull back spring power of chain device is dialled in compensation at gear down course of action postmedian;
Figure 25 is similar with 24 to Figure 22, and wherein, the handle gear shift actuating device of rear shifter of the present invention is carrying out a series of gear down actions;
Figure 26 is similar in appearance to Figure 22, and 24 and 25, be illustrated in when finishing a series of gear downs action the relation between the parts of rear shifter handle gear shift actuating device.
Figure 27 is similar to Figure 23, be illustrated in when finishing the action of a series of step-down shelves, the driving steel cable of shovel cam and rear shifter be pulled to maximum steel cable relation, the position of described shovel cam is equivalent to the location of part shown in Figure 26;
Figure 28 is similar with Figure 24-26 to Figure 22, represents a series of beginnings of changing high-grade action, wherein, click spring has been changed to higher spring stiffness position so that the weakening of the pull back spring power of compensate for rearward gear drive;
Figure 29 is similar to Figure 28, and the process of high-grade each action is changed in expression;
Figure 30 is along 30-30 line partial enlarged view among Figure 21; Be illustrated in steel cable and connection in the handle gear shift actuating device of rear shifter;
Figure 31 is the partial enlarged view along 31-31 line among Figure 19;
Figure 32 is the sectional elevation along 32-32 line among Figure 30, and is similar to Figure 20, but represents the forward handle gear shift actuating device in handle left side;
Figure 33 is the axial cutaway view along 33-33 line among Figure 32, and is similar to Figure 21, but represents forward handle gear shift actuating device;
Figure 34 is the cutaway view along 34-34 line among Figure 33, the anterior steel cable release position of dialling each part of chain device actuator of expression, and rotational arrow represents to draw the beginning of steel cable actuating;
Figure 35 is similar to Figure 34, anterior first increment of motion of drawing steel cable to activate of dialling chain device actuator of expression, and click spring has moved to P PARK Position P more among the figure;
Figure 36 is similar to Figure 34, and the anterior chain device of dialling of expression continues the actuating of pulling steel cable in the gear down process;
Figure 37 is similar to Figure 34, and what a series of gear downs of the anterior group chain device of expression were moved finishes;
Figure 38 is similar to Figure 34, represents a series of beginnings of changing high-grade action of anterior change gear mechanism;
The scheme drawing of Figure 39 is represented the gear down of the anterior group chain device of three chain links and is changed high-grade order;
Figure 40 is similar to Figure 21, is second kind of shovel cams according to rear shifter of the present invention;
Figure 41 is corresponding to Figure 22, along the cutaway view of 41-41 line among Figure 40, and mechanism of expression Figure 40 institute is in the state of top-gear position;
Figure 42 is corresponding to Figure 23, and along the section-drawing of 42-42 line among Figure 40, expression is in the mechanism shown in Figure 40 and 41 of top-gear position;
Ratchet shown in the partial enlarged view presentation graphs 40-42 shown in Figure 43 in second kind of shovel cams of rear shifter actuating device is arranged;
The ratchet of first kind of shovel cam of rear handle actuating device shown in the layout schematic diagrammatic sketch 19-31 shown in Figure 44 is arranged, the slewing area of representative type steel cable pulling scope and corresponding handle actuating device;
Figure 45 is similar to Figure 44, the anterior situation of dialling the gear shift actuating device of chain device shown in the presentation graphs 32-39;
Figure 46 is the partial view that is similar to Figure 19, the handle end of expression mountain bike, first kind of bobbin winder bracket form of the front and rear handle gearshift of the present invention that draws among the figure;
Figure 47 is the amplification stereogram in zone shown in the label 47 among Figure 46, the left end of expression handgrip and on anterior handle gear shift actuating device is installed;
Figure 48 is the partial enlarged view along 48-48 line among Figure 46;
Figure 49 is the cutaway view along 49-49 line among Figure 48, and partly drawing, short steel rope is in transmission connection between handle rotating element and bobbin winder bracket;
Figure 50 is the partial plan layout along 50-50 line among Figure 48, and wherein some part is not omitted and drawn, and the short steel rope that further is illustrated between handle rotating element and the bobbin winder bracket is in transmission connection, and expression is from the steel cable output of dialling the control of chain device of bobbin winder bracket;
The block diagram of simplification shown in Figure 51 is represented the relation between handle rotating element and the bobbin winder bracket, and arrow represents to change the maneuverability pattern of low control steel cable tension among the figure;
Figure 52 is another rough schematic view, and this figure is the plane of arrangement figure of handle rotating element and bobbin winder bracket, and the control steel cable initiative part phase-splitting of the short steel rope passive part of bobbin winder bracket and bobbin winder bracket is opened among the figure, the maneuverability pattern of directional arrow indication gear down tension;
Figure 53 is the axial cutaway view along 53-53 line among Figure 46, some CONSTRUCTED SPECIFICATION of expression left side (the anterior chain device of dialling) handle gear shift actuating device;
Figure 54 is the cutaway view along 54-54 line among Figure 53;
Figure 55 is another cutaway view along 55-55 line among Figure 53;
Figure 56 is another cutaway view along 56-56 line among Figure 53;
Figure 57 is the fragmentary axial cross-section along 57-57 line among Figure 50, and the anterior chain device control steel cable export structure of dialling of expression comprises that one adjusts reel;
Figure 58 is another amplification view along 58-58 line among Figure 48, the relative bobbin winder bracket of this cutaway view is axial, and handle is horizontal relatively, the CONSTRUCTED SPECIFICATION of expression bobbin winder bracket, and the position of the position of transmission short steel rope and the control steel cable of dialling the chain device on it;
Figure 59 is the part sectional view along 59-59 line among Figure 58, bobbin winder bracket is originally as view, special expression bobbin winder bracket and group chain device and the relation between the passive short steel rope of the rotating part of a side, and bobbin winder bracket and the relation between group chain device control steel cable of opposite side;
Figure 60 is the partial enlarged view along 60-60 line among Figure 48, engagement relationship between the selector fixed body of special expression gear shift rotating element and the anterior group chain device of three chain links, rotating element is in the top-gear position, therefore, chain is placed on the minimum chain link, the stage of the continuous gear down that the beginning that directional arrow indication gear shift rotating element gear down is rotated, Figure 60-63 explanation are rotated from top-gear position to Figure 63 deep low gear position handle gear shift actuating device of Figure 60;
Figure 61 is similar to Figure 60, gear shift rotating element and click spring have moved the first cw increment from Figure 60 position, this is enough to eliminate the lost motion of dialling in chain device and the steel cable system thereof, and the increment of shelves more of steel cable motion is provided, but also deficiency so that chain from chainlet ring gear down to intermediate link;
Figure 62 represents second cw gear down increment that the gear shift rotating element rotates, and wherein, moving of anterior group chain device has been enough to make chain be placed on intermediate link;
Figure 63 represents last cw gear down increment that the gear shift rotating element rotates, and its ratchet structure is placed on chain on the big chain link, and this has just finished the order of each action of gear down;
Figure 64 represents that first conter clockwise that gear shift rotating element and ratchet structure thereof rotate moves to position at the beginning of the beginning shown in Figure 60 with changing, and lost motion is by pine oil, but chain is still stayed on the big chain link;
Figure 65 represents second conter clockwise increment that gear shift rotating element and ratchet structure thereof rotate, and its middle sprocket moves to intermediate link; The 3rd of gear shift rotating element also is last conter clockwise increment, and ratchet structure moves back to the position of top-gear shown in Figure 60 with each part, and wherein, chain is placed on the minimum chain link; The meticulous adjustment rotation and the ratchet structure thereof of gear shift rotating element, wherein click spring moves to shown in Figure 60 and 65 between the position, does not make chain move to another chain link from a chain link, and this makes chain can do meticulous adjustment location to be avoided chain to rub;
Figure 66 is the partial enlarged view along 66-66 line among Figure 46, represents to dial near the rear end of handle right-hand end the handle gear shift actuating device of chain device, and this figure is similar to Figure 48, but direction is opposite;
Figure 67 is the local amplification view along 67-67 line among Figure 66, gear shift rotating element and its ratchet structure and the spring of expression rear shifter, being in it changes high-grade fully, cw end position with respect to the fixed body of gear shift actuating device, for rotating element and its ratchet structure are the elimination lost motion and get over grade rotating counterclockwise of increment and get ready, this action is shown in directional arrow, be a succession of gear down action then, wherein, chain is from minimum, the free gear sprocket wheel of high speed ratio moves to maximum, the free gear sprocket wheel of dead slow ratio;
Figure 68 is the part sectional view along 68-68 line among Figure 67, and the bobbin winder bracket of the gear shift actuating device of expression rear shifter is on its top-gear position;
Figure 69 is similar to Figure 68, but shown in directional arrow in Figure 68 and 69, for the position of Figure 68, bobbin winder bracket is in part gear down position among Figure 69;
The partial view that Figure 70 is similar to Figure 48, the anterior bobbin winder bracket handle gear shift actuating device of dialling the chain device of expression, dotted line is illustrated between the gear shift rotating element at the aforementioned short steel rope place of being in transmission connection and the bobbin winder bracket and is in transmission connection with bevel gear among the figure;
Figure 71 is the simplification block diagram similar to Figure 51, and the gear that is illustrated between the passive bevel gear of gear shift spinner driving bevel gear and bobbin winder bracket connects, the motion of directional arrow indication gear down direction among the figure;
Shown in Figure 72 in the partial view, some part is not omitted and is drawn, part is cut open, the figure shows gear drive of the present invention, the bobbin winder bracket form, wherein, joint action is directly to finish between the fixed sturcture of bobbin winder bracket and actuating device, the motion of directional arrow indication handle rotating element gear down direction among the figure;
Figure 73 is the partial view along 73-73 line among Figure 72, and dotted line is illustrated in bobbin winder bracket and anterior work connection of dialling between the chain device control steel cable, the rotation of the gear down direction of directional arrow indication handle rotating element and bobbin winder bracket among the figure among the figure;
Figure 74 is the part sectional view along 74-74 line among Figure 72, the details of the direct ratchet structure between expression bobbin winder bracket and fixed sturcture, and the rotation of the driven ring gear of bobbin winder bracket and ratchet ring part separately, interconnect elimination and the pine oil that spring installation makes lost motion in the rotation, the meticulous adjustment of getting over shelves and abating the noise becomes possibility, the bobbin winder bracket annular section is in its top-gear in the drawings, i.e. the clockwise direction end position;
Figure 75 is the partial view of the part of Figure 74, and ring gear moves with respect to the ratchet ring conter clockwise in first gear down increment of eliminating lost motion and shelves motion more among the figure;
Figure 76 is similar to Figure 75, and ratchet ring conter clockwise gear down is to the intermediate link position among the figure.
Fig. 1-18 draws one and has equipped the bicycle 10 of group chain device, express the rear portion and the chain device is dialled in preceding change, this paper recommends dials the details of the steel cable system that the chain device activates, and defines do not have the position of putting motion in dialling chain device and steel cable system, and this will do accurate explanation in the present invention.
The axle journal of pedal crank 44 is connected in bottom bracket 22, and is included in the pair of pedals arm 46 of vehicle frame 12 both sides, and in right-hand tread plate crank 44 the anterior change gear transmission chain link group 48 on vehicle frame 12 right sides.Chain link group 48 shown in Fig. 1 and Figure 14-18 has two chain links, and its work will be got in touch the present invention hereinafter and be described in detail.A kind of actuating of three chain link groups is described hereinafter with reference to Figure 32-38.In Fig. 1, messenger chain 50 is engaged on the big chain link in two chain links, and extends back and the compound free gear 52 of dialling the chain device meshes, so that masterpiece is used on the trailing wheel 39.Compound free gear 52 is one six chain wheel set.
The anterior label of dialling the chain device is 54, and the label of rear shifter is 56.Anterior control steel cable 58 is dialled chain device 54 with the front portion and is connected in a forward handle gear shift actuating device 60, and as shown in figure 19, its connection mode is identical with the mode that Figure 19-31 the rear portion control steel cable of representing in detail is connected in rear handle gear shift actuating device 66.Rear shifter
Central part at rear shifter 56 has a parallelogram lindage, it has one can swing but be laterally connected in the back supporting mass of suspension bracket 40, the a pair of parallel linkage that extends forward from supporting mass, and the moving body that is connected in the front end of two parallel linkages, under the effect of steel cable pulling force, but the moving body side direction inwardly moves towards vehicle frame 12, and under the effect of the pull back spring of dialling the chain device in being installed on parallelogram lindage, side direction outwards moves apart vehicle frame 12.
The label of back supporting mass is 72, is installed in swingably on the bolt 74, and bolt 74 is by being threadedly connected to suspension bracket 40.As shown in Figure 8, coil spring 76 around pivot bolt 74 within supporting mass 72, around bolt 74 bias voltage supporting mass 72 deasil or forward.One end bearing of spring 76 is in supporting mass 72, and the other end then is supported on a plate 78, shown in Fig. 8 and 9.Supporting shoulder 82 on the suspension bracket 40 at the supporting mass angular adjustment screw 80 on the plate 78, so that adjust the moment of torsion of spring 76 effectively.
The preceding moving body 84 of parallelogram lindage 70 keeps parallel with supporting mass 72, and particularly moves with respect to compound free gear 52 is laterally outer, interior with respect to vehicle frame 12.Outer link rod 86 is connected in supporting mass 72 and moving body 84 by pivot 88 and 90, and 92 of interior link rods are connected in supporting mass 72 and moving body 84 by pivot 94 and 96.
As shown in figure 10, the pull back spring 98 of dialling the chain device is the coil springs that are sleeved on the pivot 96, its two arm is supported on moving body 84 and link rod 92 respectively, thereby parallelogram lindage 70 is pressed to one flat partially, compacter state, thus with moving body 84 with respect to vehicle frame 12 and free gear 52 side direction to external pressure.As Fig. 2, shown in 8 and 10, steel cable folder 100 is contained on the outer link rod 86, so that clamp the end of steel cable 64.The pulling force that increases on the steel cable 64 pulls into parallelogram lindage 70 more open, and therefore rectangular shape, makes moving body 84 move inward with respect to vehicle frame 12 and free gear 52.
Pulley casing 102 is bearing in the inner of moving body 84 swingably, and extends downwards therefrom.A top leading sheave 104 is bearing in the top of pulley casing 102 near moving body 84 free to rotately, and a bottom tension pulley block 106 is installed in the bottom of pulley 102 free to rotately.Pulley casing 102 is made of outer, interior boxboard 108 and 110, and outer boxboard 108 is installed on the casing pivot bolt 112 that stretches out from moving body 84.By deasil or pull back, extension spring 114 acts on moving body 84 and the outer boxboard 108 pulley casing 102 by a casing pivot extension spring 114 in moving body 84.
The steel cable system 62 of rear shifter structurally reduces and strictness is limited in lost motion common in the bicycle shift steel cable, any inevitable lost motion is become to predict as much as possible, so that accurately eliminate or compensate by the cam member in the handle gear shift actuating device 66.Above-mentioned lost motion usually occurs, and this is because the flexible steel cable that makes that gear down steel cable pulling force causes is pulled out from the steel cable shell, and steel cable becomes slack in its shell, the compression of steel cable shell, and the stretching of steel cable and steel cable are adjusted the cause of the lost motion in the reel.The structure of steel cable system 62 has also reduced the friction between steel cable and its shell so that further reduce the deflection of steel cable shell, and by reducing to make gear down more easy with the friction vector of the steel cable gear down reversing of motion greatly, particularly all the more so under the situation that needs to have on the steel cable of gear down than big pulling force.
Consider above-mentioned factor, rear portion steel cable shell is divided into two sections shorter parts, one section front steel rope shell 122 and one section rear steel rope shell 124, front steel rope shell 122 extends to steel cable conduit 258 as shown in figure 20, and link to each other with handle gear shift actuating device 66 at work, rear steel rope shell 124 extends to rear shifter 56 from the rear positions on the end fork 34.Most of length of rear portion control steel cable 64 thereby do not have shell, and have only and bottom bracket 22 under a guides between small friction, this will contrast Fig. 3 and 4 hereinafter and describe.Because two sections steel cable shells 122 and 124 length are short, thus steel cable compression lost motion reduced widely, and make the prediction easily that becomes of this lost motion.
By adopting at the steel cable shell that does not axially have compression substantially the steel cable compression is greatly reduced, this point will contrast Fig. 6 and 7 hereinafter and describe.This steel cable containment structure that does not have compression has substantially also significantly reduced the deflection of steel cable shell under steel cable gear down tension, and makes this deflection and thereby the lost motion that produces the very easy prediction that becomes.
Consult Fig. 1 now, front steel rope shell 122 is adjusted reel 126 places at spring-loaded front steel rope shell and is stopped, 64 of steel cables pass from reel 126, and reel 126 is bonded in the front rack 128 adjustably by screw thread, and 128 of front racks are fixed near the right side of managing 18 upper ends down.Rear steel rope shell 124 is adjusted cylinder 130 places at back cover and is stopped, and 64 of steel cables pass from reel 130, and reel 130 is bonded in the tail-bracket 132 adjustably by screw thread, and 132 of tail-brackets are fixed on the supporting mass 72 of dialling the chain device.Can know among Fig. 5 and see that be with helical compression spring 136 on the tube reducing threaded portion 134 of adjustment reel 130, stage clip 136 stops the harmful rotation of reels 130 with respect to its carriage 132.Have unavoidable problem between reel and carriage screw thread, stage clip 136 makes reel shift to the left side slightly with respect to carriage 132 when not gear shift of steel cable is subjected to less pulling force.Yet in the gear down process, when steel cable 64 is subjected to big pulling force, reel 130 will be shifted to carriage 132 by above-mentioned thread pitch, so just produce lost motion in the steel cable system.It is similar invalid also can to produce between preceding adjustment reel 126 and its carriage 128.Lasso 138 tightly is enclosed within the end of rear casing 124, and is bonded in the axial recess of adjusting reel 130.
Consult now Fig. 3 and 4, one steel cable guide carriages 140 be fixed on bottom bracket 22 below, and supporting the arc steel cable guide frame 142 and 144 of a cross-notching, under two guide frames, forward and backward steel cable 58 and 64 is free to slide.The steel cable system that the chain device is dialled in the front portion that comprises steel cable 58 is anterior identical with the steel cable system 62 of rear shifter.Therefore, front steel rope 58 upwards extends to the main pipe 18 down in forward position, pass similar to reel 126 one and adjust reel, this adjustment reel is by being threaded on the carriage that is contained in the left side similar to carriage 128, front steel rope 58 also has the steel cable shell similar to the shell 122 of rear steel rope system 62, shown in Figure 32 and 34-38, extend to a steel cable conduit 258 from adjusting reel, and be connected in front hand grip gear shift actuating device 60.Rear steel rope 64 open grounds are from adjusting reel 126 backward along main pipe down 18 sides, its guide frame 144 times, extend to back cover along end fork backward and adjust reel 130.
Drawing in Fig. 6 and 7 one does not axially have the steel cable shell 150 that compresses substantially and is used for steel cable 58 and 64, but shown in the figure be rear steel rope 64.The core of shell 150 is a series of metal filaments 152 of being made by tough and tensile metal such as steel that annular is closely arranged, and its trend is axial substantially.Metal filament 152 is laid with very slow promptly very long helix line, and for example about three inches long just have a circle.The ring battle array of metal filament 152 is fixed between plastic wrapper 154 and the plastics inner catheter 156 with circular configuration.Inner catheter 156 is to be made as Delrin (Delrin) by tough and tensile antifriction plastics, and this inner catheter, and the short steel rope in shell 122 and 124 150 have significantly reduced the friction of steel cable in shell.Inner catheter 156 closely but freely cooperate to reduce the lost motion in the sweep of shell 122 and 124 with steel cable 64.
The applicant determines, substantially the steel cable shell 150 that does not have a compression-type has not only been eliminated the steel cable compression as the lost motion origin cause of formation substantially fully, and eliminated " monkey motion " (monkey motion) tendency of common steel cable substantially, thereby two kinds of serious origin causes of formation of lost motion have been eliminated substantially.The origin cause of formation of lost motion in rear shifter
Though the above-mentioned steel cable system that preferably adopts as the present invention part has only minimum, the nothing that can finely predict is put motion, but each gear transmission system all has the origin cause of formation of many generation lost motions, these lost motions are summed into sizable lost motion at steel cable connecting portion 100, this lost motion that adds up is also different in every kind of different gear transmission system, and variation range is from about 0.040 inch to about 0.070 inch.For the failure-free classification gear shift that has handle gear shift actuating device 66 of the present invention.Dial the chain device for every kind one gear shift actuating device cam independently preferably is set, so that reliably in chain device eliminate and solve the lost motion that adds up each different dialling.The mode of operation of first kind of shovel cam of this gear shifting actuator of rear shifter will contrast accompanying drawing 19-31 hereinafter and describe in detail.
Figure 11 is illustrated in the position of some lost motion in the common gear transmission system.At first, shown in A among Figure 11, a swing lost motion is arranged on the supporting mass 72 of its pivot bolt 74.Depend on whether chain is inwardly moving to big free gear sprocket wheel or just outwards moving to less free gear sprocket wheel, and supporting mass can upper and lower rocking.Secondly, on each of four link rod pivot pins 88,90,94 and 96, lost motion is arranged all.When supporting mass 72 rocked downwards at the A place, 84 of moving bodys upwards rocked, and when supporting mass upwards rocks, rock under the moving body side direction, and this motion is represented by B in Figure 11.All when moving body 84 rocks, the link rod 86 and 92 of parallelogram lindage also can rock, shown in C among Figure 11.In addition, also have lost motion between pivot bolt 112 and moving body 84, this is transformed into the lost motion between pulley casing 102 and the moving body 84 again, shown in D among Figure 11.In addition, leading sheave 104 also has the side direction lost motion on its pivot.Grade (overshift) more
Below with reference to Figure 21-29 in detail cam mechanism in the gear shift actuating device 66 is described in detail, cam mechanism not only is used for compensating above-mentioned lost motion, and the increment of shelves more when being used to provide towards big free gear sprocket wheel gear down.This increment of shelves more has some functions.It is that leading sheave 104 makes chain shift to the lateral angle of next big free gear sprocket wheel, and this makes than the tooth of hinge wheel and bites chain.What inwardly surmount next bigger sprocket wheel to make leading sheave 104, thereby make chain in fact deflect past tooth than hinge wheel, and like this, the tooth of sprocket wheel is the easier carrier bar of biting just, and gear shift is more prone to, reliably.The shelves increment also makes chain carry out its last motion in the direction of the sprocket wheel bigger from the next one towards the process of object chain wheel gear down more, thereby at the kickdown course of action, chain is to finish its convergence towards the target sprocket wheel with hypothesis on that direction of changing top grade.In changing high-grade action, when the less target sprocket wheel of chain convergence, the steel cable pulling force is lax, therefore, the lost motion that adds up is released, and little and stable with force vector towards the steel cable reverse movement of final destination, this is because the low power by the steel cable shell in steel cable side is less.For towards than hinge wheel gear down situation, identical factor also is suitable for, thereby adopts this moment more shelves to change high-grade direction at last near the target sprocket wheel.Therefore, towards the gear down of same free gear sprocket wheel with change high-grade action chain is equally accurately aimed at sprocket wheel.Therefore, in changing high-grade process, concerning each free gear sprocket wheel, calculate initial very easily aim at also and provide correct chain location when the gear down each sprocket wheel.
Figure 12 has illustrated the implication of " shelves more ".Each figure among Figure 12 A, B and the C states, from No. 6 free gear sprocket wheels, the sprocket wheel of mother's minimum is towards No. 5 free gear sprocket wheels, promptly in the gear down course of action of time minimum sprocket wheel, rear shifter free gear 52 and with the relation of leading sheave 104.The label that surmounts the freewheel casing of wheel hub is 160.Free sprocket wheel is numbered from No. 1 to No. 6 with traditional order.In Figure 12 A, leading sheave 104 and chain 50 are aimed at No. 6 free gear sprocket wheels at work.Just preparing from No. 6 sprocket wheels to No. 5 sprocket wheel gear downs, Figure 12 B then represents a shelves increment more, and leading sheave 104 is moved on the gear down direction or claims shelves more to surmount the position of aiming at No. 5 sprocket wheels significantly, chain 50 is moved to get over P PARK Position P.Leading sheave 104 pine oils are got back to and the i.e. position that aligns of No. 5 sprocket wheels of target sprocket wheel, above-mentionedly move to be under the effect of the pull back spring 98 of derailleur shown in Figure 10, to carry out, and carry chain 50 make itself and target sprocket wheel promptly No. 5 sprocket wheels aim at, shown in Figure 12 c.Leading sheave 104 and chain 50 final alignment position are with identical from the aligned position of No. 4 sprocket wheels when No. 5 chains are high-grade by turns among Figure 12 c, be that the target sprocket wheel is from same direction approach-ing, and the lost motion that adds up is by pine oil, and the steel cable shell is also identical to the friction vector of steel cable.
The anterior chain device of dialling
Figure 13 and 16-18 presentation graphs 1 middle front part are dialled the CONSTRUCTED SPECIFICATION of chain device.The label of the clearest parallelogram lindage that illustrates of Figure 13 is 170.The connecting element of parallelogram lindage 170 is supporting masses 172, and supporting mass 172 clamps on the present pipe 20 by clip 174.Change gear transmission case 176 is made up of outer, interior boxboard 178 and 180, and they are connecting among upper connector shown in Figure 13 182 and Figure 16,17 and 18 attaching parts 184 under the appreciiable respectively.Outer link rod 186 two ends, the top of parallelogram lindage are pivotably connected in supporting mass 172 and transmission gearbox 176 by pivot 188 and 196 respectively.Inner link rod 192 two ends, the bottom of parallelogram lindage also are pivotably connected in supporting mass 172 and transmission gearbox 176.The label of transmission gearbox adapter shaft is 194, and the supporting member adapter shaft then covers on after the part of supporting mass in the drawings.
Shown in Figure 13 and 16, a helical spring 196 be sleeved on the pivot 194 of link rod 192 and abut against link rod 192 and transmission gearbox 176 so that bias voltage parallelogram lindage 170 makes transmission gearbox inwardly be partial to frame member 20, thereby inwardly be partial to less chain link.Helical spring 196 is covered by spring case 198.
One actuator arm 200 upwards inwardly stretches to frame member 20 as the prolongation of the outer link rod 186 in top.The anterior steel cable 58 of dialling the chain device is connected actuator arm near its free end by the folder of the steel cable on actuator arm 200 202.
The anterior chain device 54 of dialling is controlled by forward handle gear shift actuating device 60 by steel cable 58.Because mechanism is simple, steel cable is shorter, compares with the rear portion gear transmission system, and it is minimum that the aforementioned lost motion factor in the anterior pick-off gear driving system reduces to.However, forwardly dial in the handle gear shift actuating device 60 of chain device still and can be overcome with the same way as that rear portion gear transmission system and relevant handle shift actuation device 66 are described in detail.
Figure 14 represents the position when cyclist's " parallel storing " chain 50.Chain link group 48 shown in Figure 14-18 has two chain links, a big chain link 210 and a chainlet ring 212.Rear portion free gear 52 is one six chain wheel set, comprises sprocket wheel No. 1 to No. 6.In Figure 14, transmission gearbox 176 is vertically aimed at big chain link 210, also aims at substantially with No. 5 sprocket wheels of free gear.In normal parallel storing, when chain engages is on big chain link 210, rear shifter will only be driven and make the free gear sprocket wheel of chain 50 three minimums, promptly No. 6, move between No. 5 and No. 4 sprocket wheels, for in these three free gear sprocket wheels any, chain 50 is all still aimed at transmission gearbox 176 fully, thereby avoids rubbing outer boxboard 178 or interior boxboard 180.Equally, during normal parallel storing, rear shifter will only be driven the free gear sprocket wheel promptly No. 1 that makes chain be positioned at three maximums, on one in No. 2 and No. 3 sprocket wheels, also can avoid the friction of chain.
Figure 15 represents the situation of " cross over and put ", and in this situation, chain 50 is engaged in big chain link 210, and rear shifter then has been driven and has made three maximum free gear sprocket wheels of chain engages, promptly No. 1, one of No. 2 and No. 3 sprocket wheels.Like this,, transmission gearbox 176 do not conform to desirable width, the chain interior boxboard 180 that will rub unless having.Wide like this transmission gearbox normally is used for adapting to crossing over and puts, but may cause taking off chain easily.Still consult Figure 15,, on No. 5 or No. 6 free gear sprocket wheels, will produce opposite leap so and put situation if chain is positioned on the chainlet ring 212 and is positioned at No. 4 of three minimums, at this moment, the chain outer boxboard 178 that will rub.
Figure 16 is illustrated in the sort of parallel storing situation among Figure 14, and chain 50 is engaged on the big chain link 210, and chain passes transmission gearbox 176 from central authorities substantially.Figure 17 represents among Figure 15 that chain forwardly is engaged on the big chain link 210 in the sort of leap storing situation, and is engaged on No. 1, the free gear sprocket wheel of three maximums at the rear portion, on No. 2 or No. 3.As seen from the figure, chain boxboard 180 in transmission gearbox 176 anterior frictions.Figure 18 represents after the cam mechanism that uses forward handle gear shift actuating device 60 carries out meticulous adjustment (back will be described in detail), the situation that chain 50 is suitably aimed in transmission gearbox 176 again.Mountain bike
Several forms of handle gear shifting actuator of the present invention in the at present popular especially mountain bike are described now.Figure 19 represents the front end 220 of mountain bike, has one slightly to the wide handle 222 that retreads.Common left and right sides handle 224 and 226 is contained in handle 222 two ends respectively.The anterior handle gear shift actuating device 60 of dialling the chain device be sleeved on handle 222 from the inboard near left side fixed handle 224, the handle gear shift actuating device 66 of rear shifter is sleeved on handle 222 fixed handle 226 that keeps right from the inboard.Gear shift actuating device 60 of the present invention and 66 is suitable for being contained on the arbitrary line position of handle, preferably is contained on the handle shown in Fig. 1 and 19, opens with its end part interval, but is suitable for too being contained near the handle two ends.
Front portion change gear transmission steel cable system 228 comprises anterior chain device control steel cable 230 and the shell 232 thereof dialled.The anterior change gear transmission steel cable system 228 of mountain bike 220 is preferably identical with bicycle 10 system for use in carrying shown in Figure 1, anterior steel cable shell 232 ends at the sort of adjustment roll device shown in Figure 5, anterior change gear transmission control steel cable 230 extends along main pipe 233 down, shown in Fig. 3 and 4, under bottom bracket, cross over, and have and resemble the steel cable shell that the sort of shown in Fig. 6 and 7 do not have compression substantially.
Rear portion change gear transmission steel cable system 234 comprises the sort of rear portion change gear transmission control steel cable 236 as illustrated in fig. 1 and 2, front steel rope shell 238 and rear steel rope shell (not drawing).Rear portion change gear transmission steel cable system 234 is preferably with shown in Fig. 1-7 and identical in conjunction with the described the sort of back gear driving wire rope of these accompanying drawings system 62.
Figure 19-31 expression is according to the structure of first kind of shovel cams of the handle gear shift actuating device 66 of rear shifter of the present invention and the details of work.In first kind of shovel cams of the present invention, compensation to step-down shelves and the different power that uprise change gear transmission pull back spring 98 (see figure 10)s between shelves is provided by gear shifting actuator click spring two-stage variable elastic stiffness, therefore, step-down shelves and a handle gear shifting actuator application force that uprises the basic identical size of shelves needs.In the rear portion variable gear handle gear shift actuating device 66b shown in Figure 40-43, to the compensation of the power of rear portion change gear transmission pull back spring 98 be by gear down with change high-grade different ratchet notches gradients and provide, hereinafter consult Figure 40-43 this point will be described in detail in detail.Rear portion shovel cam is dialled first kind of form of the handle gear shift actuating device 66 of chain device
Figure 19-31 describes rear shifter handle gear shift actuating device 66, wherein, click spring is in gear down and change and be provided with the two-stage variable elastic stiffness between top grade, wherein less elastic stiffness is for the step-down shelves action of resisting the pull back spring of dialling the chain device is provided with, and big elastic stiffness is to dial the high-grade action of changing of chain device pull back spring for dependence to be provided with.These two kinds of different spring stiffnesss are to realize with the rotational displacement of click spring is collaborative, the rotational displacement of click spring has also compensated the steel cable system of rear shifter and the lost motion in the rear shifter, the increment of motion of shelves more of rear shifter control steel cable also is provided, and these two kinds of different spring stiffnesss make gear down basic identical with the rotary action power of changing high-grade required handle gear shift actuating device 66.The fixing inside of rear handle gear shift actuating device 66
The gear shift actuating device 66 of rear shifter comprises a basic round 240 for circle, is used for making it to be fixed on the left part of handle 222, within right handles 26.The round 240 of actuating device comprises an internal mandrel part 242, and mandrel segment 242 has a central circular hole 243, and phoenix is just overlapped and fits on the handle 222.Adorn a stop screw 246 (preferably hexagonal stop screw) in the radially screw 244 on the mandrel segment 242 of round 240, so that mandrel segment 242 is locked on the handle 222.
Radially outer bow-shaped recess 248 is suitable for holding a basic complementary bow type spring spare 250 on axle 242, and bow type spring spare 250 is made as Delrin by elastic resin, but also can be made by other resin or elastic metallic.Can provide the axle 242 of dual spring rate and the feature of spring installation 250 to describe in detail hereinafter.
Fixing round 240 also comprises a cover part 252, cover part 252 is single-pieces and extends radially outwardly from it with the mandrel segment 242 of round 240, and comprise a flat substantially radial component 254, radial component 245 ends at its radially outer edge with a cylindrical flange 256, the axially basic end of pointing to handle 222 of flange 256.
Bow-shaped recess 248 on the mandrel segment of fixing round 240 comprise a pair of on arc between the sliding surface 264 opened of cap, they end at the end shoulder 266 and 268 substantially radially of groove 248 respectively.The feature of shoulder 266 can be called " gear down " shoulder, this be since ratchet spring spare 250 in the process of gear down action against it, and the feature of shoulder 268 can be called " changing top grade " shoulder, this be since ratchet spring in the process of changing high-grade action against it.A pair of rib 270 extends radially outwardly from the two ends of the sliding surface 264 of groove 248.Respectively facing to shoulder 266 and 268.Come in rib 270 and 272 spaces, but as a pair of rib, and they are bordering on the former more partially in the low shoulder 266 changing high-grade shoulder 268 and change.
Bow type spring spare 250 in this form of the present invention is described now.Spring installation 250 is the leaf springs with a toxoplasm part 274, and its end 275 and 276 is depended on and carried out that gear down is still changed top grade and against shoulder 266 and 268.In the gear down course of action, end 275 will be against shoulder 266, and shown in Figure 24-26, and in changing high-grade course of action, end 276 will be against shoulder 268, as Figure 22, shown in 28 and 29.
Arc ratchet spring spare 250 has two pairs of ribs that radially inwardly point to, and wherein a pair of label is 277 and 278, and they are to lay respectively near the end 275 of the toxoplasm part 274 of spring and 276 outer end rib.Another label to rib is 280 and 282, is by the end rib bar, and this is because they are from spring end 275 and 276 is spaced apart inwardly.These two inner ribs 280 and 282 spaced apart same distance are as the interval between rib 270 and 272.Yet, as a pair of rib, inner rib 280 and 282 equally spaced apart from the end 275 and 276 of bow type spring body portion 274.
The gear shift calibration projection 284 of one rounding is extended from the toxoplasm part 274 of spring 250 substantially radially outwardly.The outer handle rotating element of rear handle gear shift actuating device 66
The rotating element 290 of rear handle gear shift actuating device 66 clearly is shown among Figure 19 and Figure 21-29.The rotating element 290 of handle comprise one be rotatably supported in handle 222 near the fixing elongated cylinder 292 at left handle 226 places, fixedly right handles 226 makes cylinder axial location on the direction that is breaking away from handle on the handle 222.Foamed rubber or foam neoprene handle 294 are locked regularly on cylinder rotatable 292, so that the swelled handle radial dimension makes handle rotating element 290 usefulness hand operations get up more comfortable.
One steel cable actuating flanged structure 296 extends radially outwardly from the axial inner ends (with respect to the end of handle 222) of cylinder 292.Progressively axially look from the end of handle 222, steel cable activates flange 296 to have with the lower part:
It at first is a plate-like part 298 that extends radially outwardly from the inner of cylinder 292.In a trial-production part of the present invention, it is thick that plate-like part 298 is made about 1mm.Second is that a steel cable that axially protrudes from plate-like part 298 activates section 300, and in the trial-production part of the invention described above, it extends axially about 3mm from plate-like part 298.Be clearly shown that in the radial cross-section of Figure 23 and 27 steel cable activates section 300, in addition, also can see it in Figure 21.The sense of rotation steel cable cam path 302 that activates on the section 300 at steel cable substantially radially outward opens wide so that admit the control steel cable 236 of rear shifter.Steel cable activates section rotatably with thin cylindrical steel cable glissile segment 304 beginnings, glissile segment 304 changes transition with anticlockwise direction in Figure 23 and 27 be " a shovel cam " 306, shovel cam 306 has the entering part 308 of a transition, from the cylindrical glissile segment 304 of book to radially progressive cam ramps part 310 and the first bossing 312 of cam.The surface of shovel cam 306 is included in the groove 302.Cam path 302 is to activate between the plate-like part 298 of flanged structure 296 and the 3rd member that steel cable activates flanged structure 296 at steel cable to form, and the 3rd member is one and activates section 300 axial raised semicircle ratchet portions 314 from steel cable.
The ratchet portions 314 that steel cable activates flanged structure 296 has the external cylindrical surface of aiming at plate-like part 298 diametrically.One axial thin oblique jerk shoe 320 activates the front portion that defines steel cable cam path 302 on the section 300 at steel cable, enters ratchet portions 314 smooth-goingly.
Ratchet portions 314 has a series of radially inner, ratchet notches 322 spaced apart on circumference, the calibration projection 284 of the rounding of spring installation 250 successively snap in the recess 322 so that gear shift driving chain 50 is introduced on each sprocket wheel of the compound free gear 52 of rear portion change gear transmissions.In the rear portion variable gear handle gear shifting actuator 66 shown in Figure 19-31,7 ratchet notches 322 are arranged, corresponding to 7 sprocket wheels of compound free gear 52.These ratchet notches 322 spaced apart on the circumference so that on each final shift pattern of rear handle gear shift actuating device 66, make driving chain and each sprocket wheel realize accurately aiming at.Corresponding to the transverse pitch between each sprocket wheel of compound free gear 52, the spacing between the ratchet notches 322 can change on demand so that driving chain 50 is accurately aimed at each sprocket wheel of compound free gear 52.
As Figure 23, shown in the solid line in 27,30 and 31, and as Figure 22,24-26, shown in 28 and 29 the dotted line, static steel cable end cap carriage 324 is bearing on the internal support part 242 of fixing toxoplasm 240.A hole 326 on the carriage 324 is passed in the end of rear portion control steel cable 61, and steel cable end pearl 328 (normally lead is made) is seated in the steel cable end cap carriage 324.Steel cable end cap carriage 324 and be placed on wherein steel cable end pearl 328 handle end of the control steel cable 236 of rear shifter is fixed on the fixing position with respect to toxoplasm 240 and handle 222.
As previously mentioned, shovel cam 306 comprises following three parts: the entering part 308 of transition, cam ramps part 310 and cam lobe part 312.Cam lobe part 312 has a cup point 329.On the top-gear position shown in Figure 23-26, cup point 329 is bonded on fixing the steel cable end cap carriage 324 and steel cable end pearl 328, and shown in Figure 22-24, this is handle rotating element 290 end position in the counterclockwise direction.On the deep low gear position shown in Figure 26-28, cup point 329 turns over about 136 ° from steel cable end cap carriage 324 and steel cable end pearl 328 cws, as shown in figure 27.The mode of operation of the handle gear shift actuating device 66 of rear shifter shown in Figure 29-31
Changing continuously of the handle gear shift actuating device 66 of rear shifter hanged down action shown in Figure 24-27, and wherein Figure 26 and 27 is depicted as the deep low gear position; Change high-grade action then shown in Figure 28 and 29, the top-gear position is shown in Figure 22 and 23.The action of rear shifter gear down
The gear down action of rear shifter starts from the top-gear position shown in Figure 22 and 23, passes through Figure 24-27 one by one, to the deep low gear position shown in Figure 26 and 27.Gear down is the minimum sprocket wheel (speed ratio is the highest) of the free gear 52 of rear shifter, through the maximum sprocket wheel (speed ratio minimum) of a series of free gear sprocket wheels to free gear 52.The mechanism of rear portion gear shift actuating device 66 is provided with and preferably makes actuating device 66 from top to down in the gear down course of action shift to the cyclist, and makes actuating device 66 from top to down leave the cyclist in changing high-grade process.Therefore, as shown in figure 19, in the process of gear down, the top of gear shifting actuator 66 pulls to or claims to turn to the cyclist.Also be like this among Figure 21.For gear down action, in Figure 20 and 22-27, rear handle gear shift actuating device 66 clockwise rotates, and in the deep low gear position shown in Figure 26 and 27, the gear down directional arrow is shown among Figure 24-26.
Consult Figure 22 and 23 now, as shown in the figure, first kind of form of the present invention is in the top-gear position, prepares to begin to carry out a series of gear down actions, and this moment, each parts was in upper/lower positions.(1) control steel cable 236 in rear portion is in its slack position, and the cam ramps part 312 of shovel cam is in anticlockwise direction position (seeing Figure 23).(2) the calibration projection 284 on the bow type spring spare 250 is in the top-gear recess (recess of up time direction end position in Figure 22 and 24) in a series of ratchet notches 322.(3) end 276 of bow type spring spare 250 is (at Figure 22,24-26,28 and 29 anticlockwise direction ends) bow-shaped recess 248 on the fixing toxoplasm 240, as shown in figure 22, (4) on the Gu Ding toxoplasm 240 two ribs 270 that radially outward point to 272 rotatably in alignment with the inner rib 280 and 282 of identical arc isolated bow type spring spare 250 so that relatively the gear down action high-grade the action provides higher spring stiffness for fwd changes.(5) steel cable end bracket 324 and end pearl 323 are positioned at the cup point 329 of the steel cable actuating section 300 of handle rotating element 290.
The first step of gear down order clearly is shown in Figure 22 and 24, bow type spring spare 250 from its shown in Figure 22 change high-grade position (this device it against the shoulder 268 of fixing toxoplasm 240) move to gear down shown in Figure 24 position (at the other end of this position spring spare 250 shoulder 266) against the toxoplasm of fixing 240.In this first incremental process of gear down motion, spring calibration projection 284 is still stayed in its top-gear ratchet notches 322, therefore, along with handle rotating element 290 clockwise directions (Figure 22-24) rotate, spring installation 250 from fixing shoulder 268 against the position move to and fixedly shoulder 266 against the position, the inner rib 280 and 282 of spring installation 250 moves apart rib 270 and 272 respectively, therefore, the spring stiffness of spring installation 250 is decreased to the spring stiffness that whole length had between outer end rib 277 and 278 of spring installation 250.Finish three things in first increment of handle rotating element 290 motions.The first, spring installation 250 is converted to the compensation that low spring stiffness provides the pull back spring power to derailleur in the gear down course of action to increase.The second, as previously mentioned, it provides the preliminary increment of rotation so that rear portion control steel cable 236 is done initial tension to handle rotating element 290, thus the lost motion in the steel cable system of elimination rear shifter and rear shifter.The 3rd, as previously mentioned, it provides the increment of shelves more of steel cable motion, so that the failure-free stepped gearing.
Shown in Figure 22-27, clockwise carrying out along with the rotation of handle rotating element 290 gear downs, the calibration projection 284 of bow type spring spare 250 one after the other is bonded in the ratchet notches 322, from top-gear recess shown in Figure 24, by inferior high-grade recess shown in Figure 25, last then to deep low gear recess shown in Figure 26.
Figure 23 and 27 is shown clearly in the gear down rotation process of handle rotating element 290, and the pulling steel cable activates situation about finishing.At first consult Figure 23, Figure 23 illustrates handle rotating element 290 top-gear positions, the cam of shovel cam 306 plays part 312 and is in its anti-clockwise end position, approach most steel cable conduit 258, on the quite big degree of rear portion control steel cable 236 around small diameter cylinders shape steel cable glissile segment 304 bendings of steel cable cam path 302.Therefore, in Figure 23, steel cable 236 is discarded to the position that it extends most.Thereby steel cable 236 is passed through the gear down action of rear shifter and moves Figure 26 and deep low gear position shown in Figure 27 to through position shown in Figure 22 and 23 along with handle rotating element 290 is rotated, the shovel cam lobe divides 312 to clockwise rotate shown in Figure 23 and 27 with the steel cable part of expansion loop around shovel cam 306, thereby make steel cable 236 more and more move apart the thin cylindrical cam glissile segment 304 of cam path 302, shift to the entering part 308 of shovel cam 306 respectively, ramp portion 310 and bossing 312, thereby draw in steel cable 236 so that make rear shifter 56 laterally move past compound free gear 52 gradually.
Shovel cam 306 of the present invention has very big alerting ability, is applicable to commercially available in recent years various gratifying rear shifter, thereby also is suitable for said mechanism is retrofited.Can make the difference than minor diameter and shovel cam lobe part 312 of thin steel cable glissile segment 304 be adapted to the required steel cable amount of exercise of any specific rear shifter (no matter passing by, existing and future) than between the major diameter.The existing common group of chain device need about 0.760 inch steel cable amount of exercise in case when being spurred from the free gear sprocket wheel gear down of minimum to maximum free gear sprocket wheel.Test shows that the diameter difference from about 1 inch steel cable glissile segment 304 to about 1.6 inches cam portion of the present invention 312 will be rotated at handle rotating element 290 and be made 0.760 inch of steel cable pulling about 136 ° process.This is to meet normal gear shift slewing area, also meets normal torque range.In sample of the present invention.The diameter of steel cable glissile segment 304 is 1 inch, and the diameter of cam lobe part 312 is 1.6 cun, and the amount of spin of its handle rotating element 290 can calculate by following formula, and: π * (1.6-1) is that π * (D-d), this is corresponding to 136 ° of above-mentioned values.Therefore, the sort of simple coiling posture actuating device of mentioning in the relative prior art part, the amount of spin of handle rotating element 290 in steel cable moves each increment is sizable, therefore than the sort of simple coiling posture actuating device sizable mechanical advantage is arranged, the recess 322 of rotation more is separated by comes, engage and reduce the wearing and tearing of recess wall so that realize more accurate ratchet-type.
Because steel cable 236 is in its lax top-gear position, the appreciiable part of the steel cable in the outer cover 252 activates on the thin cylindrical steel cable glissile segment 304 of section 300, as shown in figure 23 around steel cable.According to the mode of operation of this form of the present invention, expand into a bigger diameter around the steel cable ring of cam path 302 from the top-gear position at the course of action of gear down, and on fixing toxoplasm 240, still keep static at the steel cable end of auspicious Zhu328Chu.This situation is opposite with the situation of common banked winding posture gear shift actuating device, and in the later case, the steel cable end is to activated device to rotate, and therefore, can not bring mechanical advantage.So, though this form of the present invention is durable, maneuverable handle rotating element 290, the degree of rotation that between top-gear and deep low gear, can have any needs, for example, the number of degrees that one concrete needs rotate are 136 °, but common simply being limited to around the posture gearshift can only be rotated about 80 °, make pulling more difficult, and disadvantageously ratchet notches is leaned on quite tightly, thereby generally need redesign to dial the chain device, so that make the normal value of steel cable amount of exercise greater than the steel cable pulling, promptly about 0.760 inch.
By adjust cam lobe part 312 than major diameter and steel cable glissile segment 304 than the ratio between the minor diameter, thereby adjusted obtained mechanical gain amount rightly, thereby be applicable to any existing rear portion change gear transmission device.In contrast, existing banked winding posture handle gear shift actuating device but requires to redesign fully rear shifter to adapt to the limited turning power of actuating device.To accomplish in the design of derailleur that this point just can't obtain optimum efficiency.
The spiral curve shape of shovel cam 306 has " nautilus " shape, when its entering part 308 by transition, when cam ramps part 310 and cam lobe part 312 are advanced, its shape changes to some extent, therefore is adapted to the variation that pulling requires to steel cable between the different sprocket wheels in succession of free gear 52.This steel cable pulling and variation mainly are owing to dial the result that the pull back spring power of chain device increases concerning gear down action in succession, this variation is compensated by the profile of shovel cam 306, so that in a series of gear down course of action of steel cable pulling, provide the steel cable pulling that reduces gradually degree according to the degree of rotation of handle rotating element 290.
First kind of form of the rear shifter that draws in detail among Figure 20-31 mainly rely on the two-stage spring stiffness of ratchet bow type spring spare 250 compensate gear down than change high-grade require more energetically, this is because to dial chain device pull back spring power in the gear down process bigger.However, the size of pulling force also can further be adjusted or meticulous adjusting when gear down, and this is to realize by the angle of inclination that each sprocket wheel for the compound free gear 52 in rear portion changes ratchet notches 322 both sides.This just in a small amount adjustment for first kind of form of rear shifter shown in Figure 20-31, in the mechanism shown in Figure 20-31, the ratchet spring spare of dual spring rate 250 provides in gear down and has changed that to dial chain device spring force between the top grade poor.In the rear portion change gear transmission handle gear shift actuating device 66b shown in Figure 40-43.Gear down and the main compensatory device of changing rear shifter pull back spring power difference between top grade are angle of inclination, the relative both sides of ratchet notches poor of actuating device.
Present suggestion is, when the shovel cam when ramp portion 310 enters bossing 312, the shovel cam edges up highly, to be enough to concerning each sprocket wheel of compound free gear 52 guarantee that rear shifter can make chain enough amount of shelves more of directed overshoot free gear sprocket wheel in the gear down action, thereby make the chain will be with as the equidirectional convergence target sprocket wheel that changes high-grade action, the height that the shovel cam edges up will be enough to the at first lost motion gap of pine oil in rear shifter and steel cable system, makes chain can do counter motion towards the target sprocket wheel of free gear 52 then.The counter motion of this chain be a kind of can observed phenomenon.In common steel cable system, when with gear down steel cable reverse movement to bigger steel cable tensioning friction vector when being reversed the less steel cable friction vector that changes high-grade steel cable motion, steel cable case pres-sure and warpage are just finished by pine oil basically.
The applicant thinks, divide the greatest limit of 312 height to be for the shovel cam lobe of each gear down action, from last sprocket wheel to 1 sprocket wheel, shovel cam lobe part 312 should be able to guarantee that rear shifter 56 does not make chain 50 inside cross motion and cause the twin-stage gear shift exceedingly, promptly slip over the target sprocket wheel and with next sprocket engagement.For maximum, No. 1 sprocket wheel of deep low gear, the applicant thinks, and the height greatest limit of shovel cam lobe part 312 is, and it should be able to guarantee that rear shifter does not make chain 50 inside side travel and make the chain 50 break away from No. 1 sprocket wheel exceedingly.
Though the applicant thinks that these are each sprocket wheels for free gear 52, the upper limit to shovel cam lobe part 312 height, but present suggestion is that this height of shovel cam lobe part 312 should be able to guarantee that rear shifter does not make the side travel of chain 50 be enough to make inboard next the free gear sprocket wheel of chain friction target sprocket wheel in the course of action of any gear down.However, classification gear shift for the best, applicant suggestion, each of shovel cam lobe part 312 should have enough height corresponding to the part of separately free gear sprocket wheel, so that make chain 50 as far as possible near next free endless chain and don't next free gear sprocket wheel that rubs.The upper limit with recommending of these maximums is can observed phenomenon.Rear shifter changes top grade by first kind of shovel cams of the present invention shown in Figure 21-31
Rotate top grade towards less free gear chain and need not get over shelves on the target sprocket wheel, and the lost motion in dialling chain device and steel cable system is a self-relaxation for chain is felt relieved.Change top grade shown in Figure 27-29, the top-gear position is shown in Figure 27 and 28, changes high-grade motion and then is shown among Figure 29, changes high-grade actuation motion and is represented by the rotation arrow in Figure 28 and 29.
In the deep low gear position of changing high-grade beginning, the calibration projection 284 of ratchet spring spare 250 is arranged in the ratchet notches 322 of anticlockwise direction end, sees Figure 26 and 28, and the steel cable 236 on the shovel cam 306 then is in the state that it is withdrawn most, sees Figure 27.
The high-grade motion of changing of handle rotating element 290 is opposite with the gear down motion, deviates from the cyclist as shown in figure 19 from top to bottom, perhaps the anticlockwise direction shown in Figure 22-29.First increment that the above-mentioned anti-clockwise of handle rotating element 290 rotates makes bow type spring spare 250 move with respect to fixing round 240 anticlockwise directions, this makes it shift to taller springs rigidity position shown in Figure 28 from low spring stiffness position shown in Figure 26, wherein, the inner rib 280 of spring installation 250 and 282 is meshed with the rib 270 and 272 of the round of fixing 240, therefore, make the operating effort of handle gear shift actuating device basic with to change top grade identical, exchange is high-grade, operating effort is consistent with the spring force of dialling the chain device, for gear down, operating effort is then opposite with the spring force of dialling the chain device.Handle rotating element 290 initial that makes spring installation 250 shift to its taller springs rigidity position changed the high-grade lost motion that rotates also relaxed rear shifter and steel cable system, and it can be that the gear down action of carrying out previously causes that above-mentioned nothing is put motion.Figure 29 represents that handle rotating element 290 is just carrying out anti-clockwise and changing high-grade action, spring installation 250 is just carrying out anti-clockwise and is changing high-grade action, and the calibration projection 284 of spring installation 250 sequentially is shifted between corresponding to the ratchet notches 322 of each free wheel sprocket.Forward handle gear shift actuating device 60
Forward handle gear shift actuating device 60 preferably is positioned at the place, inboard near fixing left handle handle 324, is shown in greater detail among Figure 32-39 relevant with operation with structure.Anterior change gear transmission gear shift actuating device 60 comprises a primary circle body 240a similar to the round 240 of rear portion change gear transmission gear shift actuating device.Round 240a comprises an internal mandrel supporting part 242a, and it has a circular central bore, and it can be enclosed within on the handle 222.One location screw 246a is housed among the radially screw 244a on the axle 242a, axle 242a is locked on the handle 222 in rotation direction with axially.
The bow-shaped recess 248a of the radial outward on axle 242a is suitable for accommodating a basic complementary arc leaf spring spring installation 250a spring installation 250a and is preferably made by tough and tensile elastomeric resin such as Delrin, but also available resin or spring metal that other is fit to are made.In the actuating device of handle gear shift forwardly 60, bow-shaped recess 248a and bow type spring 250a cooperating, thereby: (1) is on the gear down direction of the big chain link of less chain hoop, failure-free shelves more are provided between chain link in succession, and (2) can move forward and backward chain slightly with respect to its institute's concrete serobila of ingear, so that avoid chain friction.This just requires bow type spring spare 250a to remain on reliably on one of two rotational positioning; These two rotational positioning are to select according to the non-gear shift rotation increments on the both direction of handle rotating element, and this point hereinafter will describe in detail.
Fixing round 240a have one with axle supporting part 242a single-piece and the cover part 252a that extends radially outwardly from it, and comprise the radial component 254a of a basic horizontal, radial component 254a ends at a cylindrical flange part 256a at its radially outer edge, and flange portion 256a points to the left end of handle 222 in the axial direction substantially.One steel cable conduit 258a is tangential extension substantially from the outside of flange portion 256a, and its centre gangway is tangential alignment of a hole with passing the basic of flange 256a wall, so that make the anterior control steel cable 230 of dialling the chain device enter the cavity that forms in outer cover 252a.The mode that steel cable conduit 258a stops in its outer end is identical with the steel cable conduit 258 of rear shifter shown in Figure 20.
Bow-shaped recess 248a has sizable different with the corresponding bow-shaped recess 248 of rear portion actuating device 66.Groove 248a also has gear down and changes high-grade end shoulder 266a and 268a.The difference of the shape of groove 248a be to have a pair of arc wide, the rib 330 and 332 of Tu Chuing radially outward, rib 330 and 332 defines a pair of groove ends recess 334 and 336 on part.Groove ends recess 334 and 336 is limited to groove outer end shoulder 266a and 268a and fully between the shoulder on rib 330 and 332 338 and 340.
Bow type spring spare 250a is used for the form fit work with groove 248a, provides a shelves effect and an optional fine regulating action more in the chain device 54 so that forwardly dial.Spring installation 250a has a toxoplasm part 274a who ends at end 275a and 276a.A pair of end rib 277a and the 278a that approaches toxoplasm end 275a and 276a extends radially inwardly from toxoplasm part 274a, and front end is through rounding.Bow type spring spare 250a also has a calibration projection 284a who substantially radially outward points to, and protruding 284a is positioned at the central authorities of toxoplasm part substantially.
The handle rotating element 1290 of the handle rotating element 290a that changes actuating device of anterior group chain device and the gear shift actuating device of rear shifter is basic identical, difference is and the anterior number of dialling the corresponding ratchet notches of chain number of rings of chain device, with and the shape of shovel cam be that the requirement of dialling the chain device with the front portion adapts.Therefore, handle rotating element 290a comprises a long cylinder 292a, the handle 294a of one foamed rubber or poly-chloroprene rubber, and steel cable activates flanged structure 296a, and the respective flanges structure 296 of first kind of form of the rear shifter handle gear shift actuating device 66 that flanged structure 296a and detailed earlier herein are crossed is similar.Therefore, the steel cable of forward handle gear shift actuating device 60 activate flanged structure 296a comprise a radial finger to plate-like part 298a, and one steel cable activate a section 300a, steel cable activates section 300a and the steel cable of rear shifter actuating device 66 that to activate section 300 similar basically, is the requirement that adapts to the chain link of front portion group chain device specially but difference is its shape with shovel cam 306 corresponding shovel cams.Therefore, anterior actuating device shovel cam is basic similar to rear portion actuating device shovel cam 306, has previously described identical fundamental mode and advantage.
Steel cable activates flanged structure 296a and also comprises a basic semi-round ratchet portions 314a of being, shown in Figure 34-38, have the ratchet notches 322a that three basic equi-spaced apart come, the calibration of spring installation 259a projection 284a can be selectively be bonded among the ratchet notches 322a according to cyclist's action.
Steel cable end bracket 324a and steel cable end pearl 328a are shown in Figure 33 and 34, and they are fixed with respect to handle 222 with steel cable carriage 324 in first kind of form of the rear shifter actuating device 66 shown in Figure 19-31 and steel cable end pearl 328 identical modes.The mode of operation of forward handle gear shift actuating device 60
Forward handle gear shift actuating device 60 has the similar two-stage mode of operation of handle gear shift actuating device 66 of the rear shifter of crossing to detailed earlier herein, but its mode of operation mainly is to serve shelves purpose more, be then make the cyclist can freedom side travel chain selectively, thereby no matter how the chain rear portion can avoid the friction of chain in the horizontal position of compound free gear 52.For achieving the above object, the ratchet spring spare 250a of anterior gear shift actuating device 60 has two special positions on rotation direction, one is the top-gear detent positions shown in Figure 34 and 38, wherein spring 250a is in the clockwise direction end position with respect to the round 240a of anterior gear shift actuating device shown in Figure 34-38, and another position of spring installation 250a is the anticlockwise direction end position with respect to fixing round 240a, shown in Figure 35-37, this is the position of spring installation 250a in the gear down course of action.
The strong rotation interlocking in the fixing end notches 334 and 336 at fixing round 240a of the calibration projection 294a of spring installation 250a and the rotation interlocking between the ratchet notches 322a on the handle rotating element 290a in the end of spring installation 250a rib 277a and 278a.Therefore, when forwardly dialling chain device gear down action beginning, shown in Figure 34 and 35, handle rotating element 290a will move to gear down position shown in Figure 35 from top-gear inverse position clockwise shown in Figure 34 with spring installation 250a.The steel cable 230 that this preferential increment of motion of spring installation 250a will make handle rotating element 290a the front portion can be dialled the chain device is pulled to the P PARK Position P more that the target chain link of chain device is dialled in front portion that driving chain just shifting to respect to it, for example, dial the minimum chain link of chain device from the front portion to the anterior intermediate link of dialling chain device three chain link groups.In these cases each parts relative position as shown in figure 36, wherein, the calibration of spring installation 250a projection 284a is positioned at the intermediate recesses 322a of handle rotating element 290a, and spring installation 250a is positioned at the anti-clockwise end position.
Because this moment, chain 50 was engaged on the anterior P PARK Position P of dialling on the chain device intermediate link more, the further gear down of handle rotating element 290a is rotated (anticlockwise direction among Figure 34-37) will make the recess 322a of the clockwise direction end of handle rotating element 290a move to the position that is meshed with calibration projection 284a, as shown in figure 37.This is corresponding to maximum, the chain link that speed ratio is minimum, because as Figure 35, spring installation 250a shown in 36 and 37 is in anti-clockwise recess engage position, chain laterally outwards still is in gets over P PARK Position P.
Therefore, though the increment of shelves more of chain 50 motions in the gear down process is owing to spring installation 250a automatically provides from the anticlockwise direction motion that Figure 34-37 looks, but, the horizontal position of chain can accurate adjustment, avoiding producing chain friction on chain any position in three chain ring positions, The method of fine adjustment is handle rotating element 290a to be left one of cyclist from top to bottom be enough to clockwise direction (from Figure 34 and 38) mobile spring spare 250a but be not enough to from chain link being changed high-grade amount to next less chain link.Therefore, according to the horizontal position of chain 50 rear portions on compound free gear 52, the cyclist has the accurate adjustment position of two kinds of selections in order to eliminate chain friction to chain, promptly changes high-grade position shown in the gear down position of the spring installation 250a shown in Figure 35-37 or Figure 34 and 38.
From the big less chain link of chain hoop change top grade as shown in figure 38, among the figure, the rotation arrow of handle rotating element 290a is clockwise, indication handle rotating element leaves the cyclist from top to bottom.Change in the high-grade process this, forward handle gear shift actuating device 60 and gear down process reverse operating, first increment of its motion with spring installation 250a clockwise direction or to the right (from Figure 38) moves so that the lax chain that may stay when changing low grade is got over P PARK Position P, and further motion moves into rotating element 290a ratchet notches 322a the position that engages with calibration projection 284a in succession then.Equally, the same with the action of a series of gear downs, above-mentionedly a series ofly change high-grade the action and make the cyclist according to the horizontal position of chain 50 rear portions on compound free gear 52, can select two engage positions to avoid chain friction to handle rotating element 290a.
Figure 39 schematically draw three chain links anterior gear transmission system gear down and change high-grade order.In Figure 39, a series of curve arrowes on top are represented three gear down actions, and a series of curve arrowes of bottom represent three to change high-grade action.In Figure 39, look from right to left, the right side be minimum chain link in anterior three chain links dialling the chain device; Middle is the medium size chain link; The left side be big chain link.These three chain links are denoted as S, M and L in Figure 39.Vertical dotted line is drawn together into each chain link S, and M and L indicate each chain link S that the cyclist can realize, two chain positions of M and L.
Top in Figure 39, numeral 1 and 2 is illustrated in two selectable chain positions of chainlet ring two opposite sides, two selectable chain positions of chain link two opposite sides during numeral 3 and 4 is illustrated in, numeral 5 and 6 is illustrated in two selectable positions of big chain link two opposite sides.Bottom in Figure 39, position 1 and 2 correspondences are designated as A and B, and position 3 and 4 also correspondence is designated as A and B, and position 5 and 6 also correspondence is designated as A and B.A represents the high-grade position of changing of spring installation 250a shown in Figure 34 and 38, and B is the gear down position of spring installation 250a shown in the presentation graphs 35-37 then.
In the gear down order, be that the adjustment chain 50 of avoiding chain friction to do can originate in position 1 or position 2 according to people by bike, spring installation 250a can originate in position A or B.If chain is in the position 1, and spring installation 250a is at position A, then first increment in the gear down action will be from the position 1 to the position 2, spring installation is moved to position B from its position A.Arrow indication in the middle of the top is 24 the motions to the position from the position, show from chainlet ring S to the laterally shelves motion more of chain of chain link M, the increment of motion of shelves more of chain make its surmount in chain link M to the position 4, so just make spring installation 250a move to its position B.The further gear down of big chain link L is by the arrow indication of left upper portion, relates to the position increment of shelves more of 6 equally, makes spring installation 250a be in its position B.
On arbitrary position in above-mentioned large, medium and small three chain ring positions, the handle rotating element 290a of anterior gear shift actuating device can be subjected to rotate and adjust so that make spring installation 250a be positioned at its engage position A or B to avoid chain friction, and this depends on the sprocket wheel of the compound free gear 52 in the present rear portion of chain this moment substantially.Therefore, for chainlet ring S, chain 50 optionally is in position 1 or 2, and for middle chain link M, chain 50 optionally is in position 3 or 4, and for big chain link L, chain 50 optionally is in position 5 or 6.
Chain link M rubs for fear of chain to the top grade that changes of chainlet ring S from big chain link L warp, can carry out same selection.In a series of beginnings of changing high-grade action, chain will be in position 6 or position 5, and spring installation 250a then correspondingly is in position B or position A.If be in position 6/B, then anterior first increment of motion of dialling chain device 60 will make chain move to position 5 and make spring installation 250a move to position A.Proceed changing high-grade motion and will making chain laterally inwardly move to position 3/A through position 4/B of handle rotating element 290a, so that in reliably chain being moved on the chain link M from big chain link L; The high-grade rotation of further changing of handle rotating element 290a then moves to position 1/A with chain through position 2/B, so that reliably chain 50 is moved to chainlet ring S.
Therefore, in gear down and changing on the high-grade direction, the capital is closed by the sour jujube of ratchet spring spare 250a on axle 242a and is rotated and the automatic shelves more of realizing, in each gear shift action, the cyclist can select two chain positions, these two chain positions are in two relative nearsides of three chain links respectively, so that guarantee to eliminate the ability of chain friction.Second kind of shovel cams of the handle gear shift actuating device 66 of rear shifter
Second kind of shovel cams of the handle gear shift actuating device 66b of Figure 40-43 expression rear shifter, wherein, for the gear shift action of revolting the pull back spring power of dialling the chain device with for moving with changing of the pull back spring collaborative work of dialling the chain device is high-grade, click spring has only a fixing spring stiffness.In this second kind of form of the handle gear shift actuating device 66b of the rear shifter shown in Figure 40-43, be that the inclination angle of actuating device ratchet notches two opposite sides is poor in gear down and the main compensatory device of changing the pull back spring elastic force difference of rear shifter between the high-grade action.The above-mentioned tilt adjustable of the ratchet notches of actuating device is whole to adapt to any past, any rear shifter of the present and the future, so that compensation is higher than the pull back spring power of dialling the chain device of changing in the top grade in gear down, also be used for the gear shift displacement of each sprocket wheel of the compound free gear 52 in accurate adjustment rear portion.Click spring in second kind of form of the present invention who is now just describing can turn to gear down and change high-grade diverse location in the identical mode of click spring that first kind of form shown in Figure 19-31 dialled in the actuating device of chain device, thereby the compensation to lost motion in the steel cable system of rear shifter and the rear shifter is provided, and the increment of shelves more that the control steel cable motion of rear shifter is provided.
The structure of the gear shift actuating device 66b of the rear shifter shown in Figure 40-43 and mode of operation are all basic identical with the gear shift actuating device 66 of rear shifter shown in Figure 19-31, unique ratchet spring spare, shape of ratchet notches both sides gradient in ratchet spring spare axle bow-shaped recess and the handle rotating element of not being both.
Therefore, the gear shift actuating device 66b of rear shifter comprises a primary circle body 240b, is suitable for being fixed on the inboard of the right part fixed handle 226 of handle 222.Round 240b comprises an internal mandrel part 242b, and mandrel segment 242b has a circular central bore 243b can be sleeved on the handle 222 it.Radially adorn a location screw in the screw 244b for one on the axle 242b, preferably hexagonal-head screw is used for axle 242b is fixed on handle 222.
The basic complementary bow type spring spare 250b of dress in the bow-shaped recess 248b of the radial outward on axle 242b, spring installation 250b is preferably made by tough and tensile elastic resin such as Delrin, but also available other suitable resin or spring metal material are made.
Fixing round 240b also comprises the whole cover part 252b that forms and extend radially outwardly from it with axle 242b, and comprises flat substantially radial component 254b and outside cylinder flange portion 256b.Steel cable conduit 258b structure with the operation on all the steel cable conduit 258 with shown in Figure 20 is identical.
The difference of corresponding bow-shaped recess 248 is that it has a uninterrupted arc sliding surface 264b in first kind of form of bow-shaped recess 248b on axle 242b and rear shifter 66, and this makes bow type spring spare 250b have the unmodified spring stiffness.It has substantially radially shoulder 266b and 268b bow-shaped recess 248b.
Specifically describe now spring installation 250b, it has the toxoplasm part 274b of a basic and bow-shaped recess complementation, and its end label is 276b and 276b.Spring installation 250b has only a pair of rib that substantially radially inwardly points to, i.e. end rib 277b and 278b.In addition, the inside face of the toxoplasm part 274b of spring installation is continuous.The calibration projection 284b of rounding protrudes substantially radially outwardly from toxoplasm part 274b, and is basic in the end 276b of toxoplasm part 274b and the centre between the 276b.The outer handle rotating element of rear handle gear shift actuating device 66b
The handle rotating element 290b of second kind of form of rear handle gear shift actuating device 66b except that 2 with handle rotating element 290 in 66 first kinds of forms of structure and operating aspect and rear handle gear shift actuating device identical.First point, its ratchet notches change high-grade side in its gear down side than at it and have less inclination angle, thereby have compensated the bigger pull back spring power of rear shifter on the gear down direction.By fixing substituting around the steel cable flange, this point hereinafter will describe in detail for second point, the steel cable glissile segment 304 of actuating device 66.Therefore, back handle rotating element 290b comprises that one is rotatably supported in microscler round 292b on the handle 222 near fixing right handles 226 inboards, and on handgrip 222 direction outwardly, right handles 226 makes cylinder 292b axial location.One foamed rubber or poly-chloroprene rubber handle are sleeved on the cylinder rotatable 292b regularly, thereby feel comfortably cool when strengthening the radial dimension of rotating element 290b and hand being activated.
One steel cable activates flanged structure 296b and extends from cylinder 292b axial inner ends (with respect to handle) substantially radially outwardly.Steel cable activate flanged structure 296 comprise radial finger to the outside steel cable of plate-like partial sum activate a section 300b.Steel cable activates section 300b and comprises preferably identical with the steel cable cam path 302 of 66 first kinds of forms of a rear handle gear shift actuating device steel cable cam 302b, the shovel cam 303b that comprises similar profile, the entering part 308b of shovel cam 306b tool one transition, a cam ramps part 310b and a cam lobe part 312b.
In second kind of form 66b of gear shift actuating device, interior support axle 242b comprises that an axial ledge of fixing 350 sensing handle ends are also diametrically near handle 222.The axial ledge 350 of said fixing has substituted the steel cable glissile segment 304 of the handle rotating element 290 of first kind of form 66 of rear shifter.Therefore, the anchor portion of steel cable 236 just enters steel cable cam path 302b after on the fixing axial ledge 350, so just eliminated the friction of steel cable end, and the friction of steel cable end steel cable end and dial the feature of moving contact between the steel cable glissile segment 304 of handle rotating element 290 of first kind of form of chain device 66 just.
Steel cable activates the ratchet portions 314b that flanged structure 296b also comprises a basic semicircular in shape, array of spaced is arranged on it, the recess 322b that basic radial inward is opened wide, 7 this recesses have drawn among Figure 41, corresponding to 7 sprocket wheels of compound free gear 52, the calibration of rounding projection 284b one after the other is bonded on these ratchet notches 322b.Each ratchet notches 322b has less inclination angle, as about 30 °, be used for the calibration projection 284b of rounding is delivered on its steel cable pulling side 360, and have bigger inclination angle, as about 60 °, be used for the calibration projection 284b of rounding is delivered to its steel cable pine oil side 362.Inclination angle difference base between the steel cable pine oil side 362 of the steel cable of ratchet notches 322b pulling side 360 and ratchet notches 322b is average weighed each gear down motion of actuating device 66b and when respectively changing high-grade motion between pulling steel cable and pine oil steel cable the steel cable pull back spring power of rear shifter poor.As shown in figure 43, the calibration of rounding projection 284b has the angle less than 60 °, so that adapt to about 60 ° inclination angle of ratchet notches 322b steel cable pine oil side.Therefore, the steel cable pine oil angle of roll of calibration projection 284b is also less than about 30 °.If desired, the steel cable pulling side of the calibration of rounding projection 284b also can have bigger angle, but how much is less than 60 °.
Steel cable end in actuating device 60b ends at an end pearl 328b who is positioned at steel cable end bracket 324b, and carriage 324b and end pearl 328b can be identical with end pearl 328 with the carriage 324 of 66 first kinds of forms of rear handle gear shift actuating device.Perhaps, the steel cable end can pass outside the outer cover 252 by a hole on the plate-like part 254b of outer cover, and steel cable end pearl also is positioned at the outside.
Figure 44 is the scheme drawing of ratchet portions 314 of the handle rotating element 290 of rear handle actuating device 66, has provided the representative value of the number of degrees that steel cable pulling amount and handle rotating element 290 for each ratchet notches 322 rotate among the figure.In Figure 44, the ratchet portions 314 of handle rotating element is flattened so that clear and easy to understand.
Figure 45 is similar to Figure 44, but difference is the ratchet portions 314a of the handle rotating element 290a of the anterior group chain device 60 of expression, has also provided among the figure for the steel cable pulling amount of each recess 322a and the representative value of degree of rotation.The bobbin winder bracket form of handle gear shift actuating device
Before the bobbin winder bracket form of describing according to handle gear shift actuating device of the present invention, earlier recall shovel cams of the present invention briefly, just can understand the difference between bobbin winder bracket form and the shovel cams in the detailed description so below better.
First kind of shovel cams according to handle gear shift actuating device of the present invention is shown among Figure 19-39, utilize directly control steel cable that pulling and pine oil slidably dial the chain device implementing gear down respectively and to change top grade, the handle gear shift actuating device end of steel cable is fixed in the main body of actuating device.This main body is static with respect to handle.First kind of shovel cams has a columniform thin slipper rotates with the cam ramps part, and will cliding friction in a small amount be added on the relatively large cliding friction between cam lobe part and the steel cable.
The difference of second kind of shovel cam and first kind of shovel cam shown in Figure 40-43 is since with the fixing end of steel cable on a thin stationary pipes, thereby eliminated the glissile segment and the steel cable friction in a small amount thereof of shovel cam.
These two kinds of shovel cams of the present invention all require steel cable to pass gear shift actuating device main body with the sizable angle of common axis with respect to handle and gear shift actuating device, thereby the further friction of actuating device export structure is added on the steel cable of the gear shift actuating device of dialling the chain device.Because the steel cable friction force is less,, be better than the gearshift of dialling the chain device of the bicycle in the most prior art out and away so although there is above-mentioned steel cable friction area, the serviceability of these two kinds of shovel cams of gear shift actuating device dirt is still fine.
The form that is about to the gear shifting handle actuating device of description now is shown in Figure 46-74, and the applicant is referred to as " coiling posture " (jack spool) handle gear shift actuating device.From following description and accompanying drawing as can be known, the inherent characteristics of coiling rack and panel construction is that friction is little, rotate the cliding friction of in the conversion of steel cable translation, having eliminated steel cable at handle, and make the steel cable can be with desirable angle, preferably pass gear shift actuating device itself substantially parallel with handle, this has just reduced the discharging friction of steel cable widely.
Figure 46 is similar to Figure 19, and it is one wide slightly to the handle 402 that retreads that the leading section of expression mountain bike 400, mountain bike have.Common left and right side fixed handle 404 and 406 lays respectively at handle 402 two ends.The anterior handle gear shift actuating device 408 of dialling the chain device is being sleeved on the handle 402 near left side fixed handle 404 inboards.The handle gear shift actuating device 410 of rear shifter is contained on the handle 402 abutting against side fixed handle 406 inboards.The anterior handle gear shift actuating device 408 of dialling the chain device comprises one handle rotating element 412, and rear shifter gear shift actuating device 410 comprises one handle rotating element 413.Handle rotating element 412 and 413 expose portion preferably coat foamed rubber or foam neoprene, in order to grasping and gear-change operation cosily.
The control steel cable system 414 that the chain device is dialled in the front portion that forward handle gear shift actuating device is connected in anterior derailleur comprises control steel cable 415.Rear shifter control steel cable system 416 comprises the control steel cable 417 of rear shifter.Anterior group of chain device control steel cable system 414 is preferably identical with bicycle 10 system for use in carrying shown in Figure 1, anterior steel cable shell 418 ends at an adjustment reel similar to reel shown in Figure 5, anterior change gear transmission control steel cable 415 extends downwards and the leap bottom bracket along pipe under the master 420, shown in Fig. 3 and 4, as steel cable shell shown in Fig. 6 and 7, be the steel cable shell that does not have compression substantially.
The structure and the operational details of Figure 47-65 expression first kind of bobbin winder bracket form of the present invention, this bobbin winder bracket form are that to dial the handle gear shift actuating device 408 of chain device relevant with the front portion, and actuating device 408 is close in the left end of handle 402.Said structure and the operational details situation with the handle gear shift actuating device 410 of the rear shifter shown in Figure 66-69 substantially are identical, difference is that the front portion shown in Figure 47-65 dials and have in the structure of gear shift actuating device 408 of chain device and anterior corresponding three recesses of three chain links of dialling the chain device, and the actuating device of rear shifter gear shift shown in Figure 66-69 410 then has corresponding 7 recesses of 7 sprocket wheels with the free gear of rear shifter.In addition, the recess of each sprocket wheel gone up at interval can have some fine setting to change, and compared with dialling chain device handle gear shift actuating device 408 in the front portion, this point is applicable to the gear shift actuating device 410 of rear shifter more frequently.The anterior steel cable pulling pine oil driving system of dialling chain device gear shift actuating device
The anterior chain device handle actuating device 408 of dialling comprises that one is circular main body 421 substantially, is locked on the handle 402 by fixing screw 423.One balustrade deching 422 of main body 421 is bearing on the handle rotating element 412, shown in Figure 53.Almost circular bobbin winder bracket carrier ring 424 flushes with main body 421 in main body 421 inboards.Bobbin winder bracket carrier ring 424 is locked on the handle 402 by fixing screw 426.Between main body 421 and bobbin winder bracket carrier ring 424, provide the rotation interlocking, adorn the arc positioning convex on the carrier ring 424 of a complementation in the groove 428 by the arc detent 428 on the main body 421.Above-mentioned rotation interlocking is very important, this be because the power that relatively rotates between main body 421 and carrier ring 424 than main body 421 and carrier ring 424 each other and they are much bigger with respect to the axial force of handle 402.
Bobbin winder bracket cramp bar 432 is single-pieces with bobbin winder bracket carrier ring 424, from carrier ring 424 extend with the direction to the inside that is basically parallel to handle 402 and substantially handle 402 with respect to carrier ring positioning convex 430 peripheral reaction sides.The label of bobbin winder bracket itself is 436, can see its some details in Figure 49 and 50 first, and it comprises a shell 438.Bobbin winder bracket 436 is installed in the basic planar side 433 of cramp bar 432 swingably by a pivot bolt 440, and a packing ring 442 is arranged on the pivot bolt 440.Bobbin winder bracket 436 is basically parallel to cramp bar 432 and handle 402, as shown in the accompanying drawing of back, the anterior steel cable 415 of dialling chain device actuating device is tangentially stretched out from bobbin winder bracket 436, substantially parallel handle 402, this is that direction is stretched out in optimal antifriction to steel cable 415.The direction on the basic plane of bobbin winder bracket 436 is perpendicular to the direction on main body 421 and carrier ring 424 basic planes.
The anterior chain device handle driven pulley 444 of dialling is installed in the anterior medial end of chain device handle rotating element of dialling so that along with rotating element 412 rotates together.Driven pulley 444 is shown in Figure 49-53 and 60-65.Bobbin winder bracket 436 has the circular arc input slot 446 of a steel cable shown in Figure 49-52 and 58-65.One end of the moving steel cable 448 of a short pass of bobbin winder bracket is connected in actuating device handle rotating element driven pulley 444, and the other end is connected in bobbin winder bracket 416.Driving wire rope 448 has an end pearl 454 that is positioned at a recess 452 on the handle rotating element driven pulley 444, as Figure 49,51,52 and 60-65 shown in.There is a similar steel cable end pearl 454 to be arranged in a recess 456 on the bobbin winder bracket 436 at driving wire rope 448 other ends, as Figure 51, shown in 52 and 59.
The anterior control steel cable 415 of dialling the chain device is bonded in the steel cable output magazine 458 of bobbin winder bracket, and has an end pearl 460 that is positioned at the recess 492 on the bobbin winder bracket 436, schematically is shown in Figure 51 and 52, and concrete structure is shown in Figure 59.Steel cable output magazine 458 has nautilus shape cam face, the steel cable pulling force that increases gradually is provided in the gear down course of action, so that the chain device pull back spring power of dialling that compensation increases gradually, this situation describe in detail when will be described below the anterior mode of operation of dialling chain device handle actuating device 408.
For the ease of seeing the relative orientation of handle rotating element driven pulley 444 and bobbin winder bracket 436 pivots center clearly, in Figure 49-52, the line of centers label of handle rotating element driven pulley is 466, and bobbin winder bracket line of centers label is 468.
Figure 53 represents the outside cylindrical sleeve part 470 of stationary body 421, and the overlapping outside cylindrical sleeve part 472 of handle rotating element 412.Two sleeve parts 470 and 472 and whole handle gear shift actuating device 408 by outside retaining ring 474 restriction motions laterally, retaining ring is sleeved on the handle 402 and by fixing screw 476 and is connected in handle 402.The anterior ratchet system of dialling the handle gear shift actuating device 408 of chain device
Figure 60-66 expression is applicable to the ratchet system of the anterior gear transmission system of three chain links, be used for chain work is positioned each chain link of three chain links, be used for straining and pine oil each lost motion of gear transmission system and steel cable system thereof forwardly, and be used to provide the chain tension and the pine oil of shelves more.Figure 60 represents the anterior ratchet system of dialling the chain device on its top-gear position, on the minimum chain link of chain this moment in three chain links, lost motion and more shelves all by pine oil.This is the anterior chain device handle rotating element 412 anti-clockwise end position in one group of accompanying drawing 60-65 of dialling.From the pine oil shown in Figure 60, the gear down action that the minimal chain ring position begins is shown in Figure 61-63, anteriorly dials chain device handle rotating element 412 goes to Figure 63 from the position cw of Figure 60 position.This looks from top to bottom towards cyclist's motion from Figure 46 corresponding to the top of handle rotating element 412, and this is the rotating manner of the most comfortable nature of gear down, and some reasons are because to the less cause of the desired gear down power of cyclist.Be shown in Figure 64 and 65 from the top grade that changes of maximum chain hoop minimal chain ring, gear shifting handle rotating element 412 is looked from Figure 64 and 65 and is made anticlockwise motion, looks from Figure 46, and the top of rotating element 412 deviates from cyclist's motion from top to bottom.
The anterior ratchet system of dialling chain device actuating device comprises that as vital parts one is the arc ratchet structure 480 of single-piece with rotating element 412.The details of visible ratchet structure 480 in the sectional elevation of Figure 50-65, a little axial cutaway view of visible ratchet portions 480 among Figure 53.Three isolated, and radially outer ratchet notches 482 is arranged on the ratchet portions 480.Dial the handle rotating element 412 of chain device for the front portion, these ratchet notches generally are regular well-distributeds, but if desired, the space also can change slightly from its even interval location, thereby dials the chain device so that meticulous adjustment adapts to various front portions.
One is radially inner, and long bow type spring groove 484 is arranged on the fixing main body 421.Bow type spring groove 484 is spaced apart with arc ratchet structure 480 radially outwardly, aims at ratchet notches 482 substantially in the axial direction.Spring groove 484 have a radial finger to, be positioned at the end or the shoulder 486 of cw end (Figure 60-65), when gear down, spur the end stop of steel cable as ratchet spring spare (described below).Spring groove 484 left ends be anticlockwise direction end (Figure 60-65) similar shoulder 488 for ratchet spring spare during changing top grade as retainer.The dimpling 490 of rounding being that the shoulder 486 of clockwise direction end separates radially to inner process with right-hand member slightly, therefore, has formed the rounded grooves 492 as the part of spring groove 484 from spring groove 484 bottoms between dimpling 490 and shoulder 486.
Ratchet spring spare 494 is leaf springs, and it comprises a long bow type spring body 496, is arranged in bow type spring groove 484, basic and spring groove 484 complementations.The arcuate outer surface of bow type spring body 496 is radially inwardly spaced apart to adapt to the bending at ratcher function process medi-spring body 496 from the bottom surface of spring groove 484.This radial distance between the apparent surface of spring groove 484 and spring body 496 is by radially outward pointing on ratchet spring spare 494, the end rib 498 and 500 of rounding provides, therefore end rib 498 and 500 makes most of length of long spring body 496 radially inwardly spaced apart from the bottom surface of spring groove 484, provides the necessary gap between spring body 496 and the fixing main body 421 so that can do radially outer deflection when making 428 gear shift of the ratchet notches of spring body 496 in arc ratchet structure 480.Ratchet spring spare 494 comprises the ratchet projection of a rounding, and is radially inwardly outstanding from the midway location of long spring body 496.Ratchet projection 502 generally radially inwardly is pressed into the engage position of one of three ratchet notches 482 on the ratchet structure 480 by ratchet spring spare 494, shown in Figure 60-65, and when gear shift, do to cross over and move along the outside arch surface in the footpath of the ratchet structure 480 of 482 of ratchet notches.
The one high-grade stop column 504 that changes that radially extends is fixed on the main body 421, radially inwardly stretch into the rotation path of arc ratchet structure 480 from main body 421 shells, therefore, stop column 504 is in its top-gear position, promptly can run into arc ratchet structure 480 on the anti-clockwise end position time among Figure 60.Therefore, change high-grade stop column 504 and make ratchet structure 480 and handle rotating element 412 be stopped at its top-gear position, shown in Figure 60.One similar gear down stop column 506 is fixed on the main body 421, extends internally from the shell of main body 421, so that arc ratchet structure 480 and handle rotating element 412 are stopped at its lowest gear, i.e. and clockwise end position among Figure 63.The mode of operation of forward handle gear shift actuating device 408 steel cable pulling/pine oils
The anterior mode of operation of dialling chain device handle gear shift actuating device 408 will be considered from following three stages: (1) is between handle rotating element 412 and bobbin winder bracket 436, by the attended operation of the moving steel cable 448 of short pass, so that the anterior control steel cable 415 of dialling the chain device of tension and pine oil; (2) operation of the ratchet system between handle rotating element 412 and fixing main body 421, so that make cycle chain dial three chain loop mappings of chain device with respect to the front portion, and (3) in the ordinary course of things and cross over put during meticulous adjustment in case chain friction.
The F/s of operation relates to bonded assembly tension and pine oil between handle rotating element 412 and the bobbin winder bracket 436, clearly is shown in Figure 49-52,58 and 59, but also can finds out in Figure 60-65.Figure 51,52 and 59 importance is, their drawn parrot cam facies of bobbin winder bracket steel cable output magazine 458, this output magazine 458 provides the moment of torsion of increase to dial the opposite force that chain device pull back spring increases with compensation in gear down direction front portion gradually, and this output magazine 458 provides the moment of torsion that reduces changing the opposite force of dialling the minimizing of chain device pull back spring on the high-grade direction with compensation gradually in contrast.
Mainly consult Figure 51 now, 52 and 59, at first study the operation of the pulling of gear down direction and pine oil at handle rotating element driven pulley 444 and bobbin winder bracket 436.Figure 51,52 and 59 expression driven pulleies 444 and bobbin winder bracket 436 are on the part gear down position.The further gear down of driven pulley 444 is rotated the moving steel cable 448 of (be anticlockwise direction) pulling bobbin winder bracket short pass in Figure 51 and 52A, make bobbin winder bracket 436 with Figure 51, among 52B and the 52C and clockwise direction rotation among Figure 59.This has just produced the gear down tension translation of control steel cable 415, as Figure 51, shown in the 52C and 59.
For change the high-grade steel cable pine oil that carries out from the position of part gear down be by each parts with Figure 51, the rotation of the direction that rotational arrow is opposite in 52 and 59 is finished; Driven pulley 444 is actuated to clockwise direction rotation among Figure 51 and the 52A, and bobbin winder bracket 436 is actuated to Figure 51, the anticlockwise motion among 52B and the 52C and 59.
Nautilus cam face such as Figure 51 of bobbin winder bracket steel cable output magazine 458 (the anterior chain device control steel cable 415 of dialling leads therein), shown in the 55c and 59, it is a smooth continuous curve, from in the locational minimum of maximum chain link of dead slow ratio, the highest turn round short tangential control steel cable go out port radius until the most at a high speed than, maximum on the minimal chain ring position, minimumly turn round short tangential control steel cable and go out port radius.Therefore, nautilus shape bobbin winder bracket steel cable output magazine 458 is at Figure 51, clockwise direction rotates and provides the radius that reduces gradually so that increase the pulling moment of torsion of gear down gradually on steel cable 415 among the 52c and 59, and nautilus shape bobbin winder bracket steel cable output magazine 458 is at Figure 51, anticlockwise direction provides cumulative radius with rotation among the 52c and 59, so that reducing gradually on control steel cable 415 changed high-grade pulling moment of torsion.
Therefore, the basic full remuneration of nautilus cam face of bobbin winder bracket steel cable output magazine 458 and balanced the increase gradually of variable gear pull back spring pulling force forwardly from the gear down process of the maximum chain link of minimal chain hoop, and from the reducing gradually of variable gear pull back spring pulling force forwardly of changing the high-grade process of maximum chain hoop minimal chain ring.
With regard to the steel cable range of movement of linearity, common front portion dial the chain device generally from minimum chain link to the gear down of chain link require bigger linear steel cable pulling amount, and therefrom the gear down of the big chain link of chain hoop requires less linear steel cable pulling amount, and this is just in time opposite with the requirement to moment of torsion of carrying out above-mentioned gear down.Because than much bigger steel cable motion of translation amount is provided between middle chain link and maximum chain link, thereby the requirement of the front portion being dialled the steel cable motion of translation of chain device is compensated by the steel cable motion of translation that nautilus shape bobbin winder bracket steel cable output magazine 458 provides substantially between minimum chain link and middle chain link for the nautilus shape of bobbin winder bracket output magazine 458.In other words, for at the gear down increment between minimum chain link and the middle chain link with for the gear down increment between middle chain link and maximum chain link, the amount of spin of handle rotating element 412 and driven pulley 444 thereof roughly is identical (and the pull back spring pulling force of dialling the chain device this moment and increasing is gradually compensated by the nautilus shape of bobbin winder bracket steel cable output magazine 458 fully).So just can make the basic uniformity of arc spacing between the ratchet notches 482 in succession, shown in Figure 60-65, this operation for the cyclist is very convenient and natural, but this spacing also can change as required, adapts to concrete front portion and dials the chain device so that accurately adjust.The chain device of steel cable motion of translation dial to(for) common front portion requires and the compensation done by the nautilus shape of bobbin winder bracket steel cable output magazine 458 and simultaneously a kind of real harmonious interoperation of compensation that chain device pull back spring tension variations is done is dialled in the front portion.
In order to simplify handle gear shift actuating device 408, we are recommended in the nautilus cam face of describing in conjunction with the accompanying drawings above the sort of in the bobbin winder bracket steel cable output magazine 458 now.This nautilus cam face also can adopt in the driven pulley 444 of handle actuating device or in bobbin winder bracket steel cable input slot 446, and still, this can unnecessarily make device complicated.No matter for different gears, the relative rotation position of handle gear shift actuating device driven pulley 444 and bobbin winder bracket steel cable input slot 446 how, makes both circumference have the unmodified spacing, so relatively the structure of simplification device.The zygophase of forward handle gear shift actuating device 408 mode of operation
Consult the zygophase that accompanying drawing 60-65 describes forward handle gear shift actuating device 408 mode of operation in detail now.Arc ratchet structure 480 is a single-piece so that play rotation with one with anterior group chain device handle rotating element.In Figure 60, arc ratchet structure 480 is in the top-gear position corresponding to minimum chain link in three chain links, Figure 60 to Figure 66 all processes of gear down that drawn.Ratchet structure 480 shown in Figure 60 is in the anti-clockwise end position, shown in the rotational arrow among Figure 60-63, go to lowest gear corresponding to the clockwise direction end among Figure 63 of maximum chain link three chain links from the top-gear position clockwise direction of its Figure 60.In this gear down rotation process of ratchet structure 480, the moving steel cable 448 of bobbin winder bracket short pass connects 450/452 by steel cable end pearl/transmission recess on driven pulley 444, with the rotation of arc ratchet structure 480 harmoniously by 412 pullings of handle rotating element.The main body 421 that ratchet spring spare 494 is arranged with in it all is maintained fixed motionless on all engage positions.
Top-gear position at arc ratchet structure 480, be on the anti-clockwise end position, ratchet spring spare 494 is in its left side, the anti-clockwise end position, shown in Figure 60, this position is that fwd changes high-grade action and takes to, and the ratchet projection 502 of spring installation is in the recess of anticlockwise direction end in its three ratchet notches 482 when changing top grade, shown in Figure 64.Therefore, on Figure 60 position, the end shoulder 488 of the right-hand member of ratchet spring 494 on the main body 421, the left side that 498 on the right-hand member rib of spring installation 494 is positioned at the dimpling 490 on the main body is the anticlockwise direction side.In Figure 60, the ratchet projection 502 of spring installation is arranged in the recess of three ratchet notches 482 clockwise direction ends.Gear down
First increment that the gear down of ratchet structure 480 moves clockwise is shown in Figure 60 to Figure 61, clockwise direction by ratchet spring spare 494 is that right shift limits, end rib 498 on the spring installation is crossed dimpling 490 on the main body and is entered groove 492 on the main body during this period, is that the clockwise direction end abuts against on the end shoulder 486 on the main body and the displacement of spring installation 494 is stopped at the right-hand member of groove 492 medi-spring spares 494.Spring installation ratchet projection 502 joint in the recess 482 of end in the clockwise direction is more firm against the sort of slicker and more sly more shallow joint of dimpling 490 than spring installation end rib 498, thereby takes advantage.Therefore, on the displacement of first shown in Figure 61 incremental counter, though spring installation 494 has moved to the end position of its up time meter direction, ratchet structure 480 does not produce the rotation with respect to spring installation 494.The first displacement increment pulling bobbin winder bracket driving wire rope 48 from Figure 50 to Figure 61, thereby also spurred the anterior chain device control steel cable 415 of dialling, so that eliminate the anterior lost motion of dialling in chain device and the control steel cable system 414 thereof, the more important thing is, will control steel cable and be pulled to P PARK Position P more.It should be noted that the conter clockwise end of arc ratchet structure 480 is low by changing high-grade stop column 504 among Figure 60, the end that this first increment of while gear shift campaign makes ratchet structure 480 is spaced apart from changing high-grade stop column 504.
Figure 61 to Figure 62 illustrates second increment that arc ratchet structure gear down clockwise rotates, and this second increment has formed the anterior gear shift actuating of chain device between little chain link and middle chain link of dialling.In this second gear down increment, the moment of torsion of the clockwise direction driving torque of ratchet structure 480 during greater than first increment of motion of Figure 60 to Figure 61, be enough to make the biasing force of the ratchet projection 502 resistance spring bodies 496 of spring installation to leave the ratchet notches 482 of clockwise direction end radially outwardly, therefore, spring installation ratchet projection 502 moves the ratchet notches 482 of entering the centre until 502 interlocks of spring ratchet projection along the arcuate outer surface of ratchet structure 480 subsequently, and this moment, chain was positioned on the intermediate link.Above-mentioned interlock between ratchet projection 502 and middle ratchet notches 482 makes cyclist's sense of touch of renting reliably know the location of chain on intermediate link.
Last gear down increment is shown in Figure 62 to Figure 63, the further clockwise direction that relates to handle rotating element 412 and arc ratchet structure 480 rotates, this radially outward skids off spring installation ratchet projection 502 from middle ratchet notches 482, move to once more on the arcuate outer surface of ratchet structure 480, ratchet projection 502 moves until spring installation ratchet projection 502 along the arcuate outer surface of ratchet structure 480 and snaps at last in the recess of anticlockwise direction end in three ratchet notches 482 then, shown in Figure 63, it is maximum that this also can be felt that chain is positioned at this moment by the cyclist, on the minimum chain link of speed ratio.Arc ratchet structure 480 clockwise end butt gear down stop columns have prevented the further clockwise rotation of arc ratchet structure 480 and handle rotating element 412.
Though in the ratchet system of chain device actuating device is dialled in the front portion shown in Figure 50-65, do not express, but obviously, by adopting with reference to accompanying drawing 22,24-26, the system of the 28 and 29 the sort of click spring dual spring rates that describe in detail or adopt the sort of ratchet notches gear down system different with changing high-grade angle of roll that describes in detail with reference to accompanying drawing 41-43, the cyclist can be gear down and the power of changing the identical size of top grade use in the ratchet system of Figure 50-65.
If in the order of gear down, the cyclist wants to make chain to stay on the intermediate link, so in front, when the power of cyclist's pine oil on gear shifting handle rotating element 412, the more shelves motion of control steel cable 415 will be by pine oil, and therefore, chain will move with middle chain link and aim to change high-grade direction.On the other hand, if gear down relates to from little chain link in proper order by the gear shift campaign of intermediate link to big chain link, so, also get over the shelves motion by this order, and when cyclist's release handle rotating element 412, thereby the motion of shelves more of steel cable will accurately be aimed at chain with big chain link by pine oil.Equally, therefrom chain link when cyclist's release handle rotating element 412, also can be got over the shelves motion by pine oil to the gear down of big chain link.
In conjunction with shovel cams of the present invention shown in Figure 19-43, the front has been described the various aspects of shelves more, be included in before the shelves more description to the initial tension of lost motion, relate to the description that relevant nose of cam divides the motion of shelves more of height, and make chain return with sprocket wheel or chain link aligned position, the description of the pine oil of shelves more when shift end, all these descriptions are equally applicable to all bobbin winder bracket forms of the present invention shown in Figure 46-74, also will consult above-mentioned all descriptions when describing bobbin winder bracket form of the present invention.Change top grade
First increment that each parts changes high-grade motion is shown in Figure 63 to Figure 64, and relate to the first anticlockwise direction increment that arc ratchet structure 480 rotates, dominant firm engagement in the recess of spring installation ratchet projection 502 anticlockwise direction end in three ratchet notches has overcome the more weak joint of spring installation right-hand member rib 498 after dimpling 490 during this period, making spring installation 494 is left that anticlockwise direction moves to position shown in Figure 64, on this position, the left end of spring installation 494 is against playing body end shoulder 488.Do not cause any substantial gear shift campaign of chain from above-mentioned first increment that changes top grade of Figure 63 to Figure 64 from maximum chain hoop medium chain ring, and forwardly dial any lost motion in chain device and the steel cable system thereof still for relaxed state, such during release handle rotating element 412 when the gear down motion finishes just as the cyclist.
The further anticlockwise direction gear shift of arc ratchet structure 480 is rotated, make chain chain link from big chain link is shifted to, shown in Figure 64 to Figure 65, spring ratchet projection 502 skids off from the ratchet notches 482 of anticlockwise direction end and moves so that the ratchet notches 482 in the middle of snapping into along the arcuate periphery face of ratchet structure 480 during this period, thereby make chain enter engagement state with intermediate link, the lost motion that dial chain device and steel cable system thereof this moment still is a relaxed state.The above-mentioned joint of ratchet projection 502 in middle ratchet notches 482 also can be felt by the cyclist.
Handle rotating element 412 and arc ratchet structure 480 with respect to the last increment that changes high-grade anticlockwise motion of stationary body 421 as shown between Figure 65 and Figure 50.This increment comprises spring installation ratchet projection 502 and skids off from the ratchet notches of centre, slide along the arcuate periphery face of ratchet spring spare 494, spring installation ratchet projection 502 recess that snaps into clockwise direction end in three ratchet notches 492 changes the top-gear action to finish then.Above-mentioned when changing high-grade release, the lost motion of forwardly dialling in chain device and the steel cable system thereof still is that the pine oil state is so that the suitable aligning on the minimum chain link of chain in three chain links, the anticlockwise direction end butt of ratchet structure 480 is fixed on the high-grade stop column 504 that changes in the main body 421, has prevented the further anticlockwise motion of ratchet structure 480 and gear shifting handle rotating element 412.Anterior group chain device prevents the accurate adjustment of chain friction
Consult Figure 60 and 61 now, ratchet spring spare 494 has two discrete specific positions on stationary body 421 as shown in the figure.In Figure 60, spring installation 494 is in the top-gear position of the anticlockwise direction end on the main body 421.And in Figure 61, spring installation 494 is in the gear down position of the clockwise direction end on the main body 421.The anticlockwise direction side that above-mentioned two discrete positions are resisted against the dimpling 490 on the main body by spring installation end rib 498 promptly left side (Figure 60) and in groove 492 the clockwise direction side against dimpling 490 be that right side (Figure 61) limits.Because spring installation ratchet projection 502 is all strong joint in spring installation end rib 498 against dimpling 490 either sides of joint in any in three ratchet notches 482, thereby handle rotating element 412 in the clockwise direction a little amount of spin will make spring installation 494 move to its Figure 61 position from its Figure 60 position, and handle rotating element 412 in the counterclockwise direction a little amount of spin will make spring installation 494 move to its Figure 60 position from its Figure 61 position.The above-mentioned motion of spring installation 494 in main body 421 can realize and unlikely chain is moved to another chain link from a chain link by the cyclist, and this is because the joint of all strong dimpling 490 in spring installation end rib 498 against main body of the joint in spring installation ratchet projection 502 any one recess in three ratchet notches 482.The specific position of above-mentioned two rotations of spring installation 494 in main body 421 is transferred to control steel cable 415 by arc ratchet structure 480 and bobbin winder bracket 436, makes the cyclist horizontal position of two alternative cycle chains all be arranged to avoid chain friction for arbitrary chain link in three chain links.No matter the horizontal position of chain rear portion on compound free gear how, promptly in conjunction with Figure 14 and 15 " the parallel storings " described or " cross over and put ", the cyclist can select in these two horizontal positions and avoid chain friction.Rear handle gear shift actuating device 410
Figure 66-69 draws relevant operation and the structure with rear shifter handle gear shift actuating device 410 with bobbin winder bracket form of the present invention, and rear handle gear shift actuating device 410 is positioned near the right-hand member of handle 402.The details of said structure and operation is identical with anterior group chain device handle gear shift actuating device 408 substantially, difference is, shown in Figure 66, arc ratchet structure 480a does not have 7 recesses corresponding to 7 sprocket wheels of rear shifter free gear, not but resemble anterior three recesses dialling in the chain device gear shift actuating device 408.
Rear portion variable gear gear shift actuating device 410 is shown in Figure 66, Figure 66 is basic identical with the Figure 48 that draws anterior group chain device gear shift actuating device 408, difference is, each structure gear shift actuating device 410 is positioned near handle 402 right-hand members, and rear handle rotating element 413 extends to common right side fixed handle 406 laterally.Therefore, fixing main body 421a has a balustrade deching 422a, is rotary as a part of handle rotating element 413, and main body 421a is locked on the handle 402 by fixing screw 423a.Bobbin winder bracket carrier ring 424a also is locked on the handle 402 by a location screw 426a.Main body 412a and carrier ring 424a prevent to relatively rotate by the interlocking between the arc positioning convex 430a on last arc detent 428a of main body 421a and the carrier ring 424a.Bobbin winder bracket cramp bar 432a and carrier ring 424a are single-pieces, extend on direction to the inside.Promptly extend in the left side in Figure 66, is basically parallel to handle 402.Main body 421a and carrier ring 424a further prevent moving laterally by a retaining ring identical with retaining ring shown in Figure 53 479.
Bobbin winder bracket assembly 434a comprises bobbin winder bracket 436a, bobbin winder bracket shell 438a, and a bobbin winder bracket pivot bolt 440a who is bearing in regularly on the cramp bar 432a.
Specifically consult Figure 67 now, the handle rotating element 413 of rear shifter has position driven pulley 444a thereon, and bobbin winder bracket 436a has position steel cable input slot 446a thereon.The moving steel cable 448a of bobbin winder bracket short pass interconnects handle rotating element 413 and bobbin winder bracket 436a, is driven on driven pulley 444a, and extends into the steel cable input slot 446a of bobbin winder bracket.Driving wire rope 448a has an input end pearl 450a and is arranged in transmission recess 452a on the handle rotating element 413, now consults Figure 68 and 69, also has a mouth pearl 454a, is bonded among the recess 456a on the bobbin winder bracket steel cable input slot 446a.The bobbin winder bracket steel cable output magazine 458a of rear shifter control steel cable 417 is shown in Figure 67, but in Figure 68 and 69, see clearlyer, the nautilus cam face of Figure 68 and 69 expression bobbin winder bracket steel cable output magazine 458a, it is when gear down turning handle rotating element 413, the radius that reduces gradually is provided, thereby makes torque cumulative, and when changing high-grade turning handle rotating element 413, the radius that increases gradually is provided, thereby moment of torsion is reduced gradually.Shown in Figure 68 and 69, rear shifter control steel cable 462a has steel cable export structure 464a, and it comprises an adjustment reel that is used for rear shifter control steel cable 417.
Specifically consult Figure 67 now once more, have corresponding to 7 of the compound free gear of 7 sprocket wheels radially outward unlimited spaced ratchet notches 492a for the arc ratchet structure 480a of single-piece with rear shifter handle rotating element 413.Ratchet notches 482a can be spacedly distributed substantially around the periphery of bow-shaped structural 480a, but also can distribute by unequal interval according to following needs: (1) changes the rate of reversing of handle rotating element 413 with the moment of torsion that gradually increase of compensation in the gear down direction, perhaps compensate and changing the moment of torsion that reduces gradually of high-grade direction, (2) compensate for rearward is dialled the irregularity of chain device on free gear sprocket wheel scope, and (3) compensate the variation on the free gear sprocket wheel spacing of each concrete manufacturers produce.
The bow-shaped recess 484a that radially outward points on stationary body 421a, its two ends have stop shoulder 486a and 488a, so that spring installation is provided gear down stop respectively and changes high-grade stop, bow-shaped recess 484a comprises that also close on gear down end shoulder 486a one radially inwardly points to, the dimpling 490a of rounding is among the groove 492a of a rounding that forms between dimpling 490a and shoulder 486a.Ratchet spring spare 494a comprises a long bow type spring body 496a, and spring body 496a has rounding, radially outward the end rib 498a and the 500a of Zhi Xianging.The ratchet projection 502a and the spring body 496a of rounding are single-piece, and be radially inwardly outstanding, so that sequentially engage with ratchet notches 482a in gear-change operation.
Figure 67 represents to be in each parts of the moving device 410 of the locational rear shifter gear shift of top-gear actuating device, and wherein arc ratchet structure 480a is resisted against changing on the high-grade stop column 504a on the stationary body 421a changing on the high-grade stop position.On above-mentioned top-gear position, ratchet spring spare 494a is on the clockwise direction end position in main body 421a, spring installation 494a clockwise direction end is against shoulder 488a, and spring installation end rib 498a is the right side against the clockwise direction side of dimpling 490a.On this position of each parts, the ratchet of spring installation projection 502a is bonded in the recess of the anticlockwise direction end among 7 ratchet notches 482a on the ratchet structure 480a.
In the first gear down increment (in Figure 67, seeing it is anti-clockwise) of handle rotating element 413 motions, ratchet spring 494a anticlockwise direction in groove 484a of ratchet structure 480a promptly is moved to the left, thereby the anticlockwise direction end that makes spring installation 494a moves the shoulder 486a on main body, and spring installation end rib 498a ' leap dimpling 490a enters end recesses 492a.The above-mentioned first anticlockwise direction increment pulling bobbin winder bracket driving wire rope 448a of handle rotating element 413 and ratchet structure 480a motion and enough amount of rear shifter control steel cable are moved with the void in whole that eliminates in rear shifter and the control steel cable system 416 thereof, and provide ideal shelves amount of exercise more to rear shifter control steel cable 417.
Continue anticlockwise direction (Figure 67) gear down turning handle rotating element 413 and arc ratchet structure 480a, to make all the other 6 ratchet notches 482a move into the position of aiming at spring installation ratchet projection 502a in succession, make the chain of bicycle shift to maximum free gear sprocket wheel in succession downwards from minimum free gear sprocket wheel, on this position, the anticlockwise direction end of arc ratchet structure 480a will be against gear down stop column 506a to prevent handle rotating element 413 or the further gear down motion of chain voluntarily.
In contrast, top-gear position from above-mentioned each parts, handle rotating element 413 and arc ratchet structure 480a change high-grade rotation increments with first of clockwise direction among Figure 61 (opposite with rotation arrow) motion will make ratchet spring spare 494a clockwise direction move to position shown in Figure 67, the clockwise direction end of spring installation 494a is against stop shoulder 488a, and spring installation end rib 498a is against the clockwise direction side of dimpling 490a.The lost motion pine oil in rear shifter and the steel cable system 414 thereof has been fallen when when gear down finishes, loosening the handle gear shift actuating device 410 of rear shifter.Clockwise direction ground continues to change high-grade turning handle rotating element 413 and arc ratchet structure 480 rear shifter control steel cable 417 will be loosened gradually in Figure 67, thereby make cycle chain before the free gear sprocket wheel, one after the other change top grade, until reaching the position of top-gear shown in Figure 67, this moment, spring installation ratchet projection 502a was bonded in the recess of anticlockwise direction end among a series of ratchet notches 482a, and ratchet structure is against changing high-grade stop column 504a.
Continue to consult Figure 67, as shown in the figure, ratchet spring spare 494a has two discrete rotation specific positions in stationary body 421a, be clockwise top-gear position and anti-clockwise gear down position, promptly move to this gear down position at the first gear down increment medi-spring spare 494a of handle rotating element 413 and arc ratchet structure 480a motion.Above-mentioned two discrete positions are limited by the two opposite sides that spring installation end rib 498a is positioned at the dimpling 490a on the main body.Because all strong joint in spring installation end rib 498a against dimpling 490a both sides in protruding 502a junction surface in arbitrary recess in 7 ratchet notches 486a of spring installation ratchet, thereby an a small amount of rotation of handle rotating element 413 will make between above-mentioned two positions of spring installation 494a in main body 421a mobile.Situation in forwardly dialling chain device actuating device, the above-mentioned motion of spring installation 494a in main body 421a can and not cause chain from the gear shift of a free gear sprocket wheel to another free sprocket wheel by cyclist's enforcement, and this is because the strong cause in spring installation end rib 498a against the joint of dimpling 490a in junction surface of spring installation ratchet projection 502a arbitrary recess in 7 ratchet notches 482a.The specific position of above-mentioned two rotations of spring installation 494a in main body 421a is transferred to rear shifter control steel cable 417 by arc ratchet structure 480a and bobbin winder bracket 436a, thereby make the cyclist all can select two horizontal positions of cycle chain, so that avoid chain friction for any sprocket wheel in 7 free gear sprocket wheels.For avoiding these two horizontal chain choice of location of chain friction, the sprocket wheel of rear shifter is not resembled to anterior chain link and need carry out continually, but be useful especially in the situation but be seated in leap.
The gear down of the bobbin winder bracket 436a of Figure 68 and 69 expression clockwise directions (among Figure 68 and 69) is rotated, and it rotates corresponding to the gear down of the indicated arc ratchet structure 480a of directional arrow among Figure 67.The gear down of handle rotating element 413 is rotated will be by the bobbin winder bracket driving wire rope 448a on the joint pulling bobbin winder bracket steel cable input slot 464a of steel cable mouth pearl 454a in recess 456a, thereby cause the clockwise gear down rotation of bobbin winder bracket 463a, shown in Figure 68 and 69.Figure 69 represents that bobbin winder bracket 463a rotates rotation displacement has taken place from position shown in its Figure 68 owing to above-mentioned gear down.This gear down of bobbin winder bracket 463a is rotated and is made synchronously clockwise direction gear down rotation of bobbin winder bracket steel cable output magazine 458a thereby the linearity pulling that produces rear shifter mechanism controls steel cable 417 by the joint of steel cable end pearl 460a in recess 462a.Ratchet spring spare 494a moves to main body shoulder 486a rest position from its Figure 67 position, can perception the initial above-mentioned pulling of control steel cable 417, what follow generation is the elimination and the shelves motion more of lost motion in rear shifter and control steel cable system 416 thereof.Then, the further pulling of control steel cable 417 will cause actual gear down action.Gear transmission bobbin winder bracket embodiment
Figure 70 and 71 expressions a kind of bobbin winder bracket form of the present invention, wherein, forward handle gear shift actuating device 408b drives bobbin winder bracket 436b by its handle rotating element 412b by a pair of bevel gear, during described bevel gear is paid, one is mounted in rotating element 412b upward by the driving bevel gear 514 of its driving, and another is the driven bevel pinion 516 as a bobbin winder bracket part.
The gear-driven form of the anterior group chain device gear shift actuating device 408b of the present invention shown in Figure 70 and 71 is basic identical in structure and operation with the short steel rope type of belt drive of consulting Figure 46-65 detailed description, difference is in form shown in Figure 70 and 71, and the bevel gear transmission of bobbin winder bracket has replaced the short steel rope transmission of bobbin winder bracket.Therefore, Figure 70 and the gear-driven gear shift actuating device 408b shown in 71 can have ratchet system structure and the mode of operation identical with consulting forward handle gear shift actuating device that Figure 60-65 describes in detail 408, equally, the handle gear shift of the rear shifter shown in Figure 66-69 activates 410 also can have and the short steel rope transmission of the sort of bobbin winder bracket gear transmission shown in Figure 70 and 71 with the bobbin winder bracket of replacement Figure 66-69, in addition with shown in Figure 66-69 have identical structure and mode of operation with the situation of consulting Figure 66-69 detailed description, comprise the structure and the mode of operation of the ratchet system of rear shifter shown in Figure 67.
Therefore, the handle gear shift actuating device 408b that the chain device is dialled in front portion shown in Figure 70 and 71 comprises the handle rotating element 412b that can rotate around handle 402, be fixed in the main body 421b of handle 402, and the circular body cover plate 422b that rotates with handle rotating element 412b.Main body 421b is fixed in handle 402 by fixing screw 423b and retaining ring, and described retaining ring is identical with retaining ring shown in Figure 53 474.
Bobbin winder bracket carrier ring 424b is fixed in handle 402 by fixing screw 426b, and carrier ring 424b and main body 421b lock in case relatively rotate by the mode that the bow-shaped recess 428b on the main body 421b is engaged in the arcuate convex 430b on the carrier ring 424b.Bobbin winder bracket cramp bar 432b be with carrier ring 424b be single-piece, with substantially parallel handle 402 ground to the inside direction extend.Bobbin winder bracket assembly 434b comprises bobbin winder bracket 436b, and bobbin winder bracket 436b can rotate on pivot bolt 440b, and pivot bolt 440b is installed on the cramp bar 432b.
Bobbin winder bracket transmission gear 514 is fixedly mounted in handle rotating element 412b and goes up with the coaxial rotation of handle rotating element 412b.Driving gear 514 has the basic side annular rack of direction to the inside, and its inclined-plane common pivot axis line about and gear 514 and handle rotating element 412b is 45 °.Therefore the tooth bar inclination angle of driving gear 514 with depart from about 45 ° from the basic plane of driving gear 514.
Bobbin winder bracket driven gear 516 is fixed on and is installed on the bobbin winder bracket 436, and its axis is basic and 514 rotation axis of driving gear are rectangular.Driven gear 516 has annular rack, departs from roughly 45 ° with turning cylinder, is mutually complementary angle relation and engagement with the annular rack of driving gear 514.Therefore, the annular rack of driven gear 516 is also measured about 45 ° with the basic plane of driven gear 516.The basic plane of this of driven gear 516 is identical with the basic plane of bobbin winder bracket 436b, is basically parallel to handle 402, and this is the anterior recommended orientation that chain device control steel cable 415 stretches out from bobbin winder bracket 436b of dialling.
Though be the driving gear 514 and the driven gear 516 of about 45 ° of tooth bars shown in Figure 70 and 71, but, obviously other suitable complementary angle degree also can be used for the present invention, the oblique angle with respect to pivot center of for example master and slave gear 514/516 is respectively 60 ° and 30 °, or 30 ° and 60 °, perhaps any other suitable complementary angle degree.As an alternative, if desired, the tooth bar of driving gear 514 also can be the flat rack circle of the internal side direction of basic side, and the rack circle of driven gear 516 is mutual surplus cylindrical spur gear; Perhaps in contrast, on driven gear 516, flat substantially tooth bar can be arranged, and be columniform spur gear substantially at driving gear 514.
Figure 71 represents the gear down rotation direction of gear 514 and 516, and the gear down of driving gear 514 turns to and is anticlockwise direction, and the gear down of driven gear 516 turns to and is clockwise direction.The anterior chain device control steel cable 415 of dialling engages with bobbin winder bracket steel cable output magazine 458b, output magazine 458b has the nautilus shape, therefore, the pulling of steel cable will make the pulling radius reduce gradually when bobbin winder bracket 436b clockwise rotates gear down, corresponding moment of torsion increases gradually, and loosening of steel cable will make its radius increase gradually when changing top grade, and corresponding moment of torsion reduces gradually.The gear-driven form that the direct ratchet of bobbin winder bracket engages
Figure 72-76 represents another kind of gear transmission bobbin winder bracket form of the present invention, and it is different from the form shown in Figure 70 and 71 both ways, the arrangement that first ratchet engages, and it two is to eliminate lost motion and the mechanism of shelves more is provided.In the form shown in Figure 72-76, ratchet is bonded on bobbin winder bracket itself and with respect between the fixing structure of handle 402.This engages compared with previously described ratchet is that of the present invention form relevant with handle rotating element 412b come, and tricing line and the anterior chain device of dialling of dialling the chain device for the front portion provide slightly directly a little, but more the failure-free ratchet engages.Eliminating lost motion and the mechanism of getting over shelves is provided is direct and bobbin winder bracket cooperating.Because it is directly directly related with bobbin winder bracket rather than handle rotating element that ratchet engages, thereby requirement all has the failure-free transmission turning at two between handle rotating element and the bobbin winder bracket, and this requirement is realized by gear system.
At first consult Figure 72 and 73 now, forward handle gear shift actuating device 408c comprises handle rotating element 412c.Because ratchet device is located in the bobbin winder bracket, rather than is located in the fixing main body resembling in the aforementioned forms of the present invention, thereby does not have similar stationary body in this form.Bobbin winder bracket mechanism is supported on fixing support 424c, and bearing support 424c has replaced the carrier ring in the aforementioned forms.Support 424c is a split type, shown in Figure 72, thereby can slide on handle 402, and be clamped on the handle 402 by a pair of fastening bolt 520 and 522.Bobbin winder bracket erection column 524 constitutes the integral part of support 424c, erection column 524 from the axis of handle 402 with radially outer substantially direction projection.
The rotatable longitudinal axis that is basically perpendicular to handle 402 of bobbin winder bracket 436c.One driving bevel gear 526 coaxially is installed in rotating element 412c and goes up so that with its rotation.The part that one exterior bevel gear ring 528 is bobbin winder bracket 436c, and by gear 526 drivings, being in transmission connection between gear 526 and 528 is used for according to the gear down of handle rotating element 412c or changes high-grade the rotation and realize anterior tension and the pine oil that the chain device is controlled steel cable 415 of dialling.
The inner rotation driven torus part 530 of bobbin winder bracket 436c is located coaxially in the ring gear 528, and has bobbin winder bracket steel cable output magazine 458c on its circumference.Face diagram and the mode described are anchored among the steel cable output magazine 458c on the ring gear 528 before the coiling frame end of anterior variable gear control steel cable 415, and be basically parallel to handle 402 ground and pass steel cable export structure 464c to the inside, dial chain device control steel cable system 414 by the front portion then and extend to the anterior chain device of dialling.Steel cable export structure 464c is installed on the arm 532, and arm 532 integrally extends with direction to the inside substantially from support 424c, and laterally stretches out from handle 402, shown in Figure 72.Perhaps, export structure 424c also can be installed on the independent carriage (not shown), and this carriage is bearing on the handle 402 in support 424c inboard.Steel cable output magazine 458c has the nautilus shape that detailed earlier herein is crossed, and has identical mode of operation and advantage.
Bobbin winder bracket ratchet system 534 is shown in Figure 72, in 73 and 74.Ratchet system 534 is located at bobbin winder bracket annular inner portion 530 and bobbin winder bracket is installed between main 524.A pair of basic relative arc ratchet recesses 536 fully was arranged on the interior week of bobbin winder bracket annular inner portion 530, the basic relative solid section 537 fully of annular inner portion 530 extends between ratchet recesses 536, these two solid sections 537 become in gear down direction and the end stop of changing the ratchet ball of high-grade direction, shown in Figure 74-76.Every ratchet recessed 536 contains 3 ratchet notches 538, this three recess regular distribution accurately among the figure, and two recesses 538 are positioned at 537, the three recesses of solid section of using near stop and are positioned at central authorities.As other form of the present invention,, can adjust in this spacing of ratchet notches for the purpose of accurately adjusting.
One diametric hole 540 is passed fixing erection column 524, with respect to erection column 524 and bobbin winder bracket annular inner portion 530, aims at ratchet recesses 536 in the axial direction.A pair of ratchet ball 542 is placed on the two ends in hole so that forming from the hole 540 two ends radially outward stretches out and ratchet recesses 536, more particularly the ratchet projection that engages as ratchet with ratchet notches 538.One helical compression spring passes hole 540 so that ball 542 is pressed into the position that engages with relevant ratchet notches 538.Therefore, each in the two ratchet balls is all with respect to two relevant ratchet recesses 536 and the identical detent function of ratchet notches 538 performances thereof.Though recommend to use two ratchet balls 542 and relative ratchet notches 538 so that the best ratcher function of performance obviously if desired, also can have only a ratchet ball 542 and relative ratchet notches 538.Hereinafter will talk about, the layout of a this ratchet ball recommends to be used for the handle gear shift actuating device of rear shifter.
Figure 74-76 represents a lost motion and gets over a shelves compensator 550, this compensator 550 is preferably used between active umbrella ring gear 528 and the bobbin winder bracket annular inner portion 530 so that eliminate the lost motion of forwardly dialling in chain device and the control steel cable system 414 thereof, and the increment of motion of shelves more when being provided at gear down, on the other hand, the above-mentioned lost motion of pine oil reaches a shelves increment more when changing top grade.In Figure 74-76, the whole bobbin winder bracket 436c that is in its clockwise direction end position is shown, comprise ring gear 528 and annular inner portion 530, this is corresponding to the P PARK Position P of each parts.This top-gear position is limited against ratchet ball 542 by the solid section of end stop.
Lost motion and more shelves compensator 550 be included in the bow-shaped recess 552 that radially outward opens wide on the cylindrical annular inner portion 530.Bow-shaped recess 552 has the arch surface 554 of radial outward, arch surface 554 end at groove 552 radial fingers to the end shoulder.Article one, the bow-shaped recess 556 of oppositely directed radial inward is arranged on the ring gear 528.Though bow-shaped recess 556 is substantially oppositely aimed at bow-shaped recess 552, on arc length, be longer than the latter.Bow-shaped recess 556 has the arc sliding surface 558 of a radial inward, and sliding surface 558 ends at the longitudinal end shoulder of groove 556.The dimpling 560 of one rounding is in the projection radially inwardly from the sliding surface 558 of the central authorities between bow-shaped recess 556 two ends.
Lost motion and more plate washer spring 562 be placed in two bow-shaped recess 552 and 556 cavitys that form.Leaf spring 562 has a long bow type spring body 564, and the end rib 566 and 568 of its radial dilatation all passes through the entire depth of groove 552 and 556 substantially.The dimpling 570 of one rounding is radially outward central from elastic body 564 projections between two end ribs 566 and 568.Dimpling 576 on this leaf spring diametrically with ring gear on dimpling 560 overlapping.
Leaf spring end rib 566 and 568 lays respectively near the both ends shoulder of bow-shaped recess 552 of radial outward, therefore, does not have substantial relative motion between lost motion leaf spring 562 and bobbin winder bracket annular inner portion 530.Yet the bow-shaped recess 556 of radial inward in arcuate range but than lost motion with more plate washer spring 562 is long a lot, therefore, at lost motion with more in the work of shelves compensator 550, there is significant arc space between this or that shoulder leaf spring 562 in two shoulders of bow-shaped recess 556.
Lost motion and the mode of operation of getting over shelves compensator 550 are described now.Figure 74 represents that each parts is in its top-gear position, promptly clockwise end position.This moment, thereby the solid section 537 of annular inner portion 530 was stopped at its clockwise end position against ratchet ball 542, thereby and the anti-clockwise end shoulder of the bow-shaped recess 556 on the gear 528 is stopped at its clockwise end position against the end rib 566 of leaf spring.Dimpling 560 on the ring gear is positioned at the clockwise direction side of the dimpling 570 on the leaf spring.
When the gear down of handle rotating element 412c is rotated the input beginning, handle rotating element 412c turns to the cyclist from top to bottom shown in directional arrow downward in Figure 72 and 73, cycle chain is on little chain link, gear 528 shown in directional arrow among Figure 73-76 with respect to increment of annular inner portion 530 anticlockwise motions, clockwise shoulder moves to the position that leaf spring end rib 568 engages in its bow-shaped recess 556 in annular inner portion 530, and the elasticity of dimpling 560 resistance spring bodies 564 is shifted to the anticlockwise direction side of the dimpling 570 on the leaf spring.Make the anterior chain device of dialling of ring gear 528 pullings that 415 1 enough amounts of steel cable are forwardly dialled the lost motion chain device and the control steel cable system 414 thereof and provided a desirable front portion to dial the chain device with elimination the amount of exercise of shelves more is provided from position shown in Figure 74 to first increment of motion of the position shown in Figure 75, and do not make chain move apart little chain link.The retention force of ratchet ball 542 in its ratchet notches 538 do not move thereby gear down does not take place in first increment of motion greater than the elastic pressure on dimpling 570.
Handle rotating element 412 rotates towards cyclist's further gear down from top to bottom, corresponding to further rotating counterclockwise of ring gear 528, eliminate lost motion, and make leaf spring 562 and annular inner portion 530 anticlockwise directions get over shelves, thereby the gear down that makes ring gear 528 and annular inner portion 530 rotate as one man revolt the engaging force of ratchet ball 542 in case make ratchet ball 542 from shown in Figure 74 and 75 the most at a high speed than shifting to intermediate speed ratio position shown in the Figure 76 that limits by middle ratchet notches 538 in the position, make chain move to intermediate link thereby ring gear 528 spurs steel cables 415.Continue to do such rotation and will make ratchet ball 542 move into the ratchet notches 538 of dead slow ratio, chain is moved to big chain link thereby ring gear 538 spurs steel cables 415.Cyclist's pine oil handle gearshift 408c can make more that shelves and invalid tension pine oil fall on above-mentioned two gear down positions, so as to make chain accurately with relevant chain link aligning.
Compare the position from above-mentioned position dead slow, handle rotating element 412c leaves cyclist (reverse with directional arrow among Figure 73-76) from top to bottom so that begin to change top grade, this will at first make ring gear 528 with respect to annular inner portion 530 clockwise directions retract its relative positioning shown in Figure 74, change in the first high-grade increment of motion process at this, the lost motion of forwardly dialling in chain device and the control steel cable system 414 thereof keeps the pine oil state.Then, the further clockwise direction of ring gear 528 rotates, and will keep identical relative position among their Figure 74 with annular inner portion 530, ratchet ball 542 then in succession by ratchet notches 538 get back to shown in Figure 74 the most at a high speed than the position.
Gear-driven form of the present invention shown in Figure 72-76, resemble consult that Figure 60 and 61 described in detail the selection of same lateral chain displacement also is provided, this is because bobbin winder bracket ring gear 528, all has the specific position of identical two rotations for bobbin winder bracket annular inner portion 530 the arbitrary position in three ratchet ball bond positions of annular inner portion 530.The joint of ratchet ball is eager to excel and is fixed in the joint of the dimpling 570 of dimpling 560 on the leaf spring on the ring gear, thereby in above-mentioned three gears any one, the cyclist can forward and backward turning handle rotating element 412c and ring gear 528 is being moved around between the position shown in position shown in Figure 74 and Figure 75 and 76, on position shown in Figure 74, the clockwise direction side of the dimpling 570 of dimpling 560 on leaf spring is the right side, and on position shown in Figure 75 and 76, the anticlockwise direction sidepiece of the dimpling 570 of the dimpling 560 on the ring gear on leaf spring left side.Bobbin winder bracket ring gear 528 changes into the cross travel motion of chain with respect to arbitrary chain link at chain place in three chain links with respect to the specific position of above-mentioned two rotations of bobbin winder bracket annular inner portion 530 by control steel cable 415, thereby can select and avoid chain friction.
Though the form middle gear of the present invention inclined-plane shown in Figure 72-76 is 45 °, obviously also can adopt other suitable wheel word describing in detail as consulting Figure 70 and 71, this does not exceed scope of the present invention yet.Equally, though gear-driven form shown in Figure 70-76 is to be applicable to the anterior gear shift actuating device 408 of dialling the chain device, gear transmission bobbin winder bracket form is equally applicable to the gear shift actuating device 410 of rear shifter shown in obvious Figure 70-70.
The structure of an aforementioned ratchet ball can make ratchet recesses 536 make long arcuate range, in view of need the more ratchet notches of number 538 for the rear shifter gear shift, so the escapement shown in Figure 72-76 is more suitable for the gear shift actuating device of rear shifter.Groundwork characteristics of the present invention are equally applicable to bobbin winder bracket form and shovel cams
Front Figure 39 describes in conjunction with the anterior actuating device 60 of dialling the chain device of the shovel cam-type shown in Figure 19 and the 33-38, and Figure 39 has described one the three anterior gear transmission system gear down of chain link and changed high-grade order.The actuating device 408 of chain device is dialled in the front portion that Figure 39 and explanation thereof are equally applicable to Figure 46-65, and the bobbin winder bracket form of the actuating device 408c of chain device is dialled in the front portion that the actuating device 408b of chain device mechanism and Figure 72-74 are dialled in Figure 60 and 71 front portion.Therefore, Figure 39 and describing in detail in this article also as to Figure 46-65,70-71, and the part of the disclosure of chain device bobbin winder bracket form is dialled in the front portion of 72-76.Thereby shown in Figure 39 and explanation thereof, for all bobbin winder bracket forms of the present invention, in gear down with change under high-grade two kinds of situations, ratchet spring spare is (at Figure 46-65, shown in 70 and 71 in the form label be 494, and label is 562 in form shown in Figure 72-76) rotation more shelves all automatically are provided, and in both cases, the cyclist can select in two chain positions, this two positions respectively near three chain two opposite sides, thereby can under " parallel storing " and " cross over and put " two kinds of situations, all can avoid chain friction.The rotational angle of the rear shifter handle rotating element 290 shown in Figure 19-30 and the representative value of steel cable pulling amount are shown among Figure 44.Representative value shown in Figure 44 is equally applicable to the bobbin winder bracket form of all rear shifters of the present invention, the actuating device 410 that comprises Wound-rotor type rear shifter shown in Figure 66-69, and corresponding to the anterior actuating device form of the gear type shown in Figure 70-71 and the 72-76.
Figure 45 is similar to Figure 44, but has provided each rotational angle of the anterior chain device handle rotating element 290a of dialling and the representative value of steel cable pulling amount.The similar representative value of rotational angle and steel cable pulling amount is applicable to the anterior bobbin winder bracket form of dialling chain device actuating device, comprises the form of Figure 46-65, and Figure 70 and 71 and Figure 72-76 shown in gear-driven form.
For Figure 46-65,70 and 71, and the bobbin winder bracket form of chain apparatus is dialled in the front portion shown in the 72-74, and the bobbin winder bracket form of the rear shifter actuating device shown in Figure 66-69, the nautilus cam face of bobbin winder bracket has been described in the front, it can provide cumulative moment of torsion changing the pull back spring power that group chain device reduces gradually on the high-grade direction to dial the cumulative pull back spring power of chain device on the compensation gear down direction, also can provide on the other hand the moment of torsion that reduces gradually with what compensate.Equally, dial the chain device for the front portion, the front has been described this bobbin winder bracket cam-shaped and the steel cable motion of translation that is provided can have been compensated anterior requirement of dialling the chain device to the motion of steel cable line, promptly the gear down of chain link requires relatively large steel cable motion of translation from the minimal chain hoop, and therefrom the gear down of the big chain link of chain hoop then requires steel cable motion of translation in a small amount.These identical basic compensation also are applicable to shovel cam embodiment of the present invention shown in Figure 19-43.
The nautilus shape that the front equally also is applicable to bobbin winder bracket form of the present invention to described other advantage of nautilus shape cam face and the feature of shovel cam embodiment of the present invention, comprise: (1) bobbin winder bracket nautilus cam face provides the suitable spirit property used to various commercially available in recent years gratifying rear shifters, bobbin winder bracket nautilus cam less and be suitable for any past, the desired steel cable amount of exercise of the present and the future's concrete rear shifter than the difference between major diameter; (2) bobbin winder bracket nautilus cam face can make any desirable amount of spin of handle gear shift actuating device produce the linear pulling amount of corresponding ideal control steel cable (for example, the handle rotating element rotates about 136 ° and produces about 1.6 inches steel cable pulling amount); (3) compare with banked winding posture actuating device, bobbin winder bracket nautilus cam face can make actuating device handle rotating element rotate the bigger any desirable number of degrees and obtain accordingly than the great machinery benefit; (4) bobbin winder bracket nautilus shape cam makes ratchet notches spaced apart as far as possible ideally, so that accurately the classification gear shift engages the wearing and tearing that also reduce ratchet notches to greatest extent.
Though above the most practical preferred embodiment is described, obviously can modifies and do not exceed scope of the present invention.The technology contents that the present invention is not limited to describe in detail above, scope of the present invention is defined by the claims.
Claims (89)
1. bicycle shift system comprises:
Has at work gearshift with the derailleur of the pull back spring device of bicycle rear interoperation;
Be installed in bicycle handle bar handle gear shift actuating device on hand;
Described gear shift actuating device comprises can be around manually operated handle wheel word basic and the first axle rotation that handle is coaxial;
Described handle wheel word selectively rotates with the gear down direction or rotates with the opposite high-grade direction of changing; And
One end is fixed in described gear shift actuating device, and the other end is connected in the control steel cable device of described group of chain device formula gearshift at work, described control steel cable device by described pull back spring device bias voltage to described group of chain device formula gearshift;
It is characterized in that:
Described gear shift actuating device also comprise can around with the winding bracket unit of second rotational of described primary shaft angle offset;
Described winding bracket unit can the gear down direction rotate, make winding bracket unit spur described control steel cable device so that make described derailleur gearshift gear down, and change high-grade direction and rotate with oppositely directed, make described winding bracket unit pine oil described control steel cable device so that make described derailleur gearshift change top grade; And
Work between described handle wheel word and described winding bracket unit connects, make the gear down of described handle wheel word rotate the synchronous gear down rotation that causes described winding bracket unit, the high-grade top grade that changes synchronously that causes described winding bracket unit that rotates of changing of described handle wheel word is rotated.
2. according to the described bicycle shift of claim 1 system, it is characterized in that: described second axis and described first axle angle offset are about 90 °.
3. according to the described bicycle shift of claim 1 system, it is characterized in that: it is a kind of mechanical connection that described work connects.
4. according to the described bicycle shift of claim 3 system, it is characterized in that: it is that a kind of steel cable connects that described work connects.
5. according to the described bicycle shift of claim 3 system, it is characterized in that: it is that a kind of gear connects that described work connects.
6. according to the described bicycle shift of claim 5 system, it is characterized in that: it is that a kind of bevel gear connects that described gear connects.
7. according to the described bicycle shift of claim 2 system, it is characterized in that: it is that a kind of steel cable connects that described work connects.
8. according to the described bicycle shift of claim 2 system, it is characterized in that: it is that a kind of gear connects that described work connects.
9. according to the described bicycle shift of claim 8 system, it is characterized in that: it is that a kind of bevel gear connects that described gear connects.
10. according to the described bicycle shift of claim 1 system, it is characterized in that: described handle wheel word is sleeved on the bicycle handle outside substantially in the inboard of handle one end.
11. according to the described bicycle shift of claim 1 system, it is characterized in that: described control steel cable device is basically parallel to bicycle handle ground and extends from described winding bracket unit.
12. according to the described bicycle shift of claim 1 system, it is characterized in that: have cam gear on the device in described handle wheel word and described winding bracket unit, the profile of cam gear makes that on the gear down direction of described derailleur gearshift described bobbin winder bracket control steel cable gear down pulling force compensates the power that increases gradually of described pull back spring device substantially.
13. according to the described bicycle shift of claim 1 system, it is characterized in that: have cam gear on the device in described handle wheel word and described winding bracket unit, the profile of cam gear makes the pulling when described bobbin winder bracket is controlled the steel cable gear down compensate the lost motion in described derailleur and described control steel cable device substantially.
14. according to the described bicycle shift of claim 1 system, it is characterized in that: on one of described handle wheel word and described Winder, have cam gear, the profile of cam gear makes described derailleur gearshift cycle chain be surpassed enough amount of shelves more of target sprocket wheel of the gearshift of described derailleur in gear down action, thus chain can with change the identical direction convergence target sprocket wheel of high-grade action.
15. according to the described bicycle shift of claim 14 system, it is characterized in that: the amount of exercise that the profile of described cam gear makes cycle chain cross described target sprocket wheel is not enough to cause and changes folk art term.
16. according to the described bicycle shift of claim 14 system, it is characterized in that: described target sprocket wheel is the maximum sprocket wheel of described gearshift, and the profile of described cam gear make cycle chain cross described target sprocket wheel hypomotility so that chain come off from described target sprocket wheel.
17. according to the described bicycle shift of claim 14 system, it is characterized in that: the hypomotility that the profile of described cam gear makes cycle chain cross described target sprocket wheel is crossed the next sprocket wheel of described target sprocket wheel to cause chain friction.
18. according to the described bicycle shift of claim 12 system, it is characterized in that: described cam gear is on described winding bracket unit.
19. according to the described bicycle shift of claim 12 system, it is characterized in that: described control steel cable means for engaging is on described cam gear.
20. according to the described bicycle shift of claim 13 system, it is characterized in that: described cam gear is on described winding bracket unit.
21. according to the described bicycle shift of claim 20 system, it is characterized in that: described control steel cable means for engaging is on described cam gear.
22. according to the described bicycle shift of claim 14 system, it is characterized in that: described cam gear is on described winding bracket unit.
23. according to the described bicycle shift of claim 22 system, it is characterized in that: described control steel cable means for engaging is on described cam gear.
24. according to the described bicycle shift of claim 22 system, it is characterized in that: described cam gear is on described winding bracket unit.
25. according to the described bicycle shift of claim 24 system, it is characterized in that: described control steel cable means for engaging is on described cam gear.
26. according to the described bicycle shift of claim 24 system, it is characterized in that: described cam gear is on described winding bracket unit.
27. according to the described bicycle shift of claim 26 system, it is characterized in that: described control steel cable means for engaging is on described cam gear.
28. according to the described bicycle shift of claim 17 system, it is characterized in that: described cam gear is on described winding bracket unit.
29. according to the described bicycle shift of claim 28 system, it is characterized in that: described control steel cable system engages is on described cam gear.
30. according to the described bicycle shift of claim 1 system, it is characterized in that: have the escapement that is bonded on respect to the fixed sturcture of bicycle handle and the regulation of the gear between the turntable, described turntable is one of described handle wheel word and described winding bracket unit.
31. according to the described bicycle shift of claim 30 system, it is characterized in that: described escapement has ratchet male means and the spring installation device on one of described rotatable means of described fixed sturcture, and in another structural ratchet notches arcuate array spaced apart of above-mentioned two structures, the described ratchet male means of described spring installation device bias voltage is against described arcuate array.
32. according to the described bicycle shift of claim 30 system, it is characterized in that: described ratchet male means and described spring installation device are positioned at described fixed sturcture, and described arcuate array is positioned at described turntable.
33., it is characterized in that according to the described bicycle shift of claim 32 system: described ratchet male means and described spring installation device be positioned at substantially described arcuate array radially outside side.
34. according to the described bicycle shift of claim 32 system, it is characterized in that: it is that a kind of steel cable connects that described work connects.
35. according to the described bicycle shift of claim 32 system, it is characterized in that: described ratchet male means and described spring installation device are positioned at the radially inner side of described arcuate array substantially.
36. according to the described bicycle shift of claim 35 system, it is characterized in that: it is that a kind of gear connects that described work connects.
37. according to the described bicycle shift of claim 30 system, it is characterized in that: described escapement is bonded between described fixed sturcture and the described handle wheel word.
38. according to the described bicycle shift of claim 32 system, it is characterized in that: it is that a kind of steel cable connects that described work connects.
39. according to the described bicycle shift of claim 30 system, it is characterized in that: described escapement is bonded between described fixed sturcture and the described winding bracket unit.
40. according to the described bicycle shift of claim 39 system, it is characterized in that: it is that a kind of gear connects that described work connects.
41. according to the described bicycle shift of claim 31 system, it is characterized in that: described ratchet male means and described spring installation device are positioned at described fixed sturcture, and described arcuate array is positioned at described turntable.
42. according to the described bicycle shift of claim 41 system, it is characterized in that: it is that a kind of steel cable connects that described work connects.
43. according to the described bicycle shift of claim 31 system, it is characterized in that: described ratchet male means and described spring installation device are positioned at described fixed sturcture, and described arcuate array is positioned at described winding bracket unit.
44. according to the described bicycle shift of claim 43 system, it is characterized in that: it is that a kind of gear connects that described work connects.
45. according to the described bicycle shift of claim 31 system, it is characterized in that: described ratchet male means and described spring installation device can be on one of described two structures, move along arcuate array together between a second place of changing a high-grade primary importance and a gear down.
46. according to the described bicycle shift of claim 45 system, it is characterized in that: the lost motion in described derailleur gearshift and described control steel cable device, on described primary importance,, and on the described second place, be tightened up by pine oil.
47. according to the described bicycle shift of claim 45 system, it is characterized in that: one of the motion of a described derailleur gearshift shelves increment more by pine oil, and is tightened up on the described second place on described primary importance.
48. according to the described bicycle shift of claim 45 system, it is characterized in that: by handling described handle wheel word, described ratchet male means and described spring installation device can move around between the described primary importance and the second place on the selected arbitrarily gear of described escapement together selectively, thereby avoid chain friction.
49. according to the described bicycle shift of claim 48 system, it is characterized in that: have second escapement that can between one of described spring installation device and described two structures, engage, so that on any selected gear of described escapement, selectively described ratchet male means and described spring installation device are remained on the described primary importance or the described second place together selectively.
50. according to the described bicycle shift of claim 48 system, it is characterized in that: described derailleur gearshift is anterior derailleur gearshift.
51. according to the described bicycle shift of claim 48 system, it is characterized in that: described derailleur gearshift is a rear portion derailleur gearshift.
52. according to the described bicycle shift of claim 49 system, it is characterized in that: described derailleur gearshift is anterior derailleur gearshift.
53. according to the described bicycle shift of claim 49 system, it is characterized in that: described derailleur gearshift is a rear portion derailleur gearshift.
54. according to the described bicycle shift of claim 49 system, it is characterized in that: described spring installation device has lower spring stiffness in the described second place than in described primary importance, thereby compensates the bigger derailleur pull back spring power during gear down substantially.
55. according to the described bicycle shift of claim 31 system, it is characterized in that: described ratchet recesses has different gear downs and changes high-grade slope, inclination angle, high-grade recess slope is changed less than described in the inclination angle on described gear down recess slope, thereby compensates bigger derailleur pull back spring power during the gear down substantially.
56. according to the described bicycle shift of claim 31 system, it is characterized in that: described spring installation device is long leaf spring device.
57. according to the described bicycle shift of claim 56 system, it is characterized in that: described ratchet male means and described leaf spring device are single-pieces.
58. according to the described bicycle shift of claim 57 system, it is characterized in that: described ratchet male means and described spring installation device are positioned at described fixed sturcture, and described arcuate array is positioned at turntable.
59. according to the described bicycle shift of claim 57 system, it is characterized in that: described turntable is described handle wheel word.
60. according to the described bicycle shift of claim 59 system, it is characterized in that: it is that a kind of steel cable connects that described work connects.
61. according to the described bicycle shift of claim 31 system, it is characterized in that: described ratchet male means is the ratchet ball device.
62. according to the described bicycle shift of claim 61 system, it is characterized in that: described spring installation device is a compression spring device.
63. according to the described bicycle shift of claim 61 system, it is characterized in that: described ratchet ball device and described spring installation device are arranged in described fixed sturcture, and described arcuate array is positioned at described turntable.
64. according to the described bicycle shift of claim 63 system, it is characterized in that: described turntable is described winding bracket unit.
65. according to the described bicycle shift of claim 64 system, it is characterized in that: it is that a kind of gear connects that described work connects.
66. according to the described bicycle shift of claim 31 system, it is characterized in that: described turntable is described winding bracket unit, and described work connection is a kind of gear connection;
Described winding bracket unit has the ring gear device, and described work connection is that the gear between described handle wheel word and described ring gear device connects, and a described end of described control steel cable device is fixed in described ring gear device;
Described winding bracket unit also has the driven torus device that is driven rotationally by described ring gear device, and described escapement is bonded between described fixed sturcture and the described driven torus device; And
Lost motion between described ring gear device and described driven torus device connects, and described lost motion connects can move described ring gear device rotationally with respect to described driven torus device between a second place of changing a high-grade primary importance and a gear down.
67. according to the described bicycle shift of claim 66 system, it is characterized in that: the lost motion in described derailleur gearshift and described control steel cable device, and is tightened up in the described second place by pine oil in described primary importance.
68., it is characterized in that according to the described bicycle shift of claim 66 system: one of the motion of described derailleur gearshift more the shelves increment in described primary importance by pine oil, and be tightened up in the described second place.
69., it is characterized in that: be arranged in the described ring gear device according to the described bicycle shift of claim 66 system described driven torus device essentially concentric.
70. according to the described bicycle shift of claim 66 system, it is characterized in that: by handling described handle wheel word, described wheel word can move around between described first and second positions on any selected gear of described escapement selectively, so that avoid chain friction.
71. according to the described bicycle shift of claim 70 system, it is characterized in that: have second escapement that can be bonded between described ring gear device and the described driven torus device, so that on any selected gear of described escapement, described ring gear device and described driven torus device are remained on described first and second positions selectively.
72. according to the described bicycle shift of claim 70 system, it is characterized in that: described derailleur gearshift is anterior derailleur gearshift.
73. according to the described bicycle shift of claim 70 system, it is characterized in that: described derailleur gearshift is a rear portion derailleur gearshift.
74. according to the described bicycle shift of claim 71 system, it is characterized in that: described derailleur gearshift is anterior derailleur gearshift.
75. according to the described bicycle shift of claim 71 system, it is characterized in that: described derailleur gearshift is a rear portion derailleur gearshift.
76. the gear shift method of a bicycle shift system, described bicycle shift system has the derailleur gearshift with the bicycle rear cooperating, and has a pull back spring device, handle gear shift actuating device with wheel word, have cam gear on the wheel word, and control steel cable device, control steel cable device first end is connected in described gear shift actuating device, be connected in described derailleur gearshift in the second end work, described gear shift method may further comprise the steps:
Described control steel cable is bonded on the described cam gear near its described first end;
It is characterized in that further comprising the steps of:
The winding bracket unit that can be driven in rotation is included in the described wheel word;
Described wheel word is installed in bicycle handle bar on hand, is in substantially in described handle one end;
First end of described control steel cable device is fixed on the winding bracket unit, and
A kind of profile is provided on described cam gear, make cam gear described cam gear when the rotation of gear down direction spur described steel cable device, so that cause the gear down action of described gearshift, and cam gear is changing the high-grade direction described steel cable device of described cam gear pine oil when rotating, so that cause the high-grade action of changing of described gearshift.
77., it is characterized in that: on described cam gear, provide a kind of profile, so that the power that basic compensation increases gradually at the above pull back spring device of gear down direction according to the described method of claim 76.
78., it is characterized in that: on described cam gear, provide a kind of profile, so that compensate the lost motion in described derailleur gearshift and described steel cable device substantially according to the described method of claim 76.
79. according to the described method of claim 76, it is characterized in that: a kind of profile is provided on described cam gear, in gear down action, make described gearshift that cycle chain is crossed enough amount of shelves more of target sprocket wheel of described gearshift, thus make chain with change high-grade action equidirectional trend target sprocket wheel.
80. according to the described method of claim 79, it is characterized in that: a kind of profile is provided on described cam gear, and the described hypomotility that makes cycle chain cross described target sprocket wheel changes folk art term to cause.
81. according to the described method of claim 79, it is characterized in that: a kind of profile is provided on described cam gear, and the described hypomotility that makes cycle chain cross described target sprocket wheel changes folk art term to cause.
82. according to the described method of claim 79, it is characterized in that: described target sprocket wheel is the maximum sprocket wheel of described gearshift, and a kind of profile is provided on described cam gear, make cycle chain directed overshoot sprocket wheel described hypomotility so that chain come off from described target sprocket wheel.
83. according to the described method of claim 79, it is characterized in that: a kind of profile is provided on described cam gear, and the described hypomotility that makes cycle chain directed overshoot sprocket wheel is to cause the next sprocket wheel of chain friction directed overshoot sprocket wheel.
84., it is characterized in that further comprising the steps of according to the described method of claim 76:
A handle wheel word that is contained on the turning handle is included in the described wheel word;
Rotate described handle wheel word around described handle; And
Connect the described winding bracket unit of driving by the short steel rope between described wheel word and described winding bracket unit.
85., it is characterized in that further comprising the steps of according to the described method of claim 76:
A handle wheel word that is contained on the turning handle is included in the described wheel word;
Rotate described handle wheel word around described handle; And
Connect the described winding bracket unit of driving by the gear between described wheel word and described winding bracket unit.
86. according to the described method of claim 76, it is characterized in that: described winding bracket unit can be around a rotational about 90 ° with the handle axis angle offset.
87., it is characterized in that: pass described steel cable device from described handle gear shift actuating device, make described steel cable device be basically parallel to described handle, so that reduce the steel cable friction to greatest extent according to the described method of claim 86.
88., it is characterized in that: pass described steel cable device from described handle gear shift actuating device, meet at right angles substantially with the turning cylinder of described winding bracket unit according to the described method of claim 85.
89., it is characterized in that: by engaging to determine that with respect to the ratchet between the fixing and described wheel word of bicycle handle which sprocket wheel of described derailleur gearshift is meshed by cycle chain according to the described method of claim 76.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| US853,442 | 1992-03-18 | ||
| US07853442 US5197927B1 (en) | 1991-03-20 | 1992-03-18 | Bicycle derailleur cable actuating system |
Related Parent Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 93102614 Division CN1030829C (en) | 1992-03-18 | 1993-03-17 | Bicycle derailleur cable actuation system |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1123754A CN1123754A (en) | 1996-06-05 |
| CN1057055C true CN1057055C (en) | 2000-10-04 |
Family
ID=25316045
Family Applications (2)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 93102614 Expired - Fee Related CN1030829C (en) | 1992-03-18 | 1993-03-17 | Bicycle derailleur cable actuation system |
| CN95106053A Ceased CN1057055C (en) | 1992-03-18 | 1995-05-16 | Bicycle derailleur cable actuating system |
Family Applications Before (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 93102614 Expired - Fee Related CN1030829C (en) | 1992-03-18 | 1993-03-17 | Bicycle derailleur cable actuation system |
Country Status (1)
| Country | Link |
|---|---|
| CN (2) | CN1030829C (en) |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5590564A (en) * | 1995-11-20 | 1997-01-07 | Shimano, Inc. | Bicycle control device |
| US9243692B2 (en) * | 2013-02-19 | 2016-01-26 | Sram, Llc | Electric bicycle transmission |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4504250A (en) * | 1981-07-03 | 1985-03-12 | Establissements Le Simplex | Control device which provides a plurality of pre-established and controlled positions, more particularly for use with the speed gear shifting devices for cycles and the like |
| US4599079A (en) * | 1985-03-04 | 1986-07-08 | Chappell Gilmore H | Automatic derailleur shifter |
-
1993
- 1993-03-17 CN CN 93102614 patent/CN1030829C/en not_active Expired - Fee Related
-
1995
- 1995-05-16 CN CN95106053A patent/CN1057055C/en not_active Ceased
Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4504250A (en) * | 1981-07-03 | 1985-03-12 | Establissements Le Simplex | Control device which provides a plurality of pre-established and controlled positions, more particularly for use with the speed gear shifting devices for cycles and the like |
| US4599079A (en) * | 1985-03-04 | 1986-07-08 | Chappell Gilmore H | Automatic derailleur shifter |
| US4693700A (en) * | 1985-03-04 | 1987-09-15 | Chappell Gilmore H | Derailleur shifter |
Also Published As
| Publication number | Publication date |
|---|---|
| CN1081981A (en) | 1994-02-16 |
| CN1030829C (en) | 1996-01-31 |
| CN1123754A (en) | 1996-06-05 |
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| C14 | Grant of patent or utility model | ||
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| C41 | Transfer of patent application or patent right or utility model | ||
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