CN1276045A

CN1276045A - Automatic transmission systems for humanly powered vehicles

Info

Publication number: CN1276045A
Application number: CN97182438A
Authority: CN
Inventors: 弗雷德里克·弗朗西斯·格兰特
Original assignee: Individual
Current assignee: Individual
Priority date: 1997-11-10
Filing date: 1997-11-11
Publication date: 2000-12-06
Anticipated expiration: 2017-11-10
Also published as: CN1151944C; EP1030983A4; WO1999024735A1; CA2309063C; CA2309063A1; JP2001522973A; EP1030983A1; WO1999024735A8; AU5433198A

Abstract

A shiftable bicycle transmission is automatically shifted by automatically sensing output power torque of the transmission, automatically converting sensed output power torque to transmission shifting motion, and automatically shifting the shiftable transmission with that transmission shifting motion. A shiftable bicycle driving power transmission has a transmission shifting element, a bicycle output power torque sensor, and an output power torque-to-transmission shifting motion converter having an output power torque input coupled to that output power torque sensor and having a transmission shifting motion output. Such transmission shifting element is coupled to the transmission shifting motion output of that converter.

Description

The automatic speed-changing system of human powered vehicle

The present invention relates to bicycle and other human powered vehicle, more specifically, relate to the automatic mixing speed variator system that this paper is referred to as the human powered vehicle of " bicycle ".

Before 40 years, in many people's eyes, the vehicle automatic transmission system is as their older generation's motorcar electric starter motor in the eyes.Although bicycle is the same with automobile with similar vehicles of long standing and well established, global cyclist does not also have to have their human powered vehicle the automatic speed-changing system of practical advantages.

The various automatic bicycle shift system that people propose all not have widely successfully.A nearest suggestion has added three counterweights on trailing wheel, separate with 120 degree angles, and these counterweights have increased resistance of air and the quality more than a kilogram to bicycle.Also have, these counterweights are made response by the effect of centrifugal force or centripetal force to the speed of trailing wheel, automatically the gear of conversion speed changer.In fact, the shifting of transmission of speed of response has its shortcoming.Situation when for example going up a slope by bike.At this moment, the cyclist will require great effort to pedal, with maintenance speed.When this just is deferred to gear shift effort and no longer can keeps speed to pedal certainly.Because this can lose speed, make the cyclist must make great efforts to go up a slope, also be like this even changed shelves.On the contrary, descending and enter the level land and then may not make brake difficult owing to do not gain shelves do not subtract down in speed before.

Therefore the cyclist continue manually to respond on the leg and pin on load be bicycle shift.Cause ceaselessly increasing the number of gears like this, increase the Transmission gear when making bicycle speed-varying unit in other words, especially like this when making mountain bike.Increase the cyclist how gear shift and the Operating Complexity of gear shift when after the gear of speed changer is many conversely, thereby make many people give up buying the thought of senior racing car or mountain bike.

This problem can be estimated by a kind of commercial eight fast bicycles, the variable Rate of this car in other words, the variation of velocity ratio is 22% from first grade to second grade, is 15% from second grade to third gear, being 18% from the third gear to the fourth speed, is 21% for five grades from fourth speed to the, is 20% from the 5th grade to the 6th grade, from the 6th grade to the 7th grade is 17%, is 22% from the 7th grade to the 8th grade.This problem of taking unusual ratio to occur can be from a kind of example analyses of modern ten eight-speed transmissions bicycles, this bicycle has preceding sprocket wheel control follower and back sprocket wheel control follower, provide following numerous velocity ratios to change altogether: is 22% from first grade to second grade, is 11% from second grade to third gear, be 3% from the third gear to the fourth speed, from fourth speed to the is 18% for five grades, does not change from the 5th grade to the 6th grade, by the compound action generation of preceding sprocket wheel and back sprocket wheel; From the 6th grade to the 7th grade, the tenth grade to the 11 grade, the 15 grade to the 16 grade respectively be 4%, 9%, the eight grade to the 9th grade respectively is 2% from the 7th grade to the 8th grade, is 5% from the 9th grade to the tenth grade; Is 7% from the 11 grade for 15 grades, the 17 grade to the 18 grade to the tenth second gear, the tenth second gear to the ten third gear, the tenth fourth gear to the; Only have 6% from the tenth third gear to the ten fourth gear; Is 13% from the 16 grade to the 17 grade.

Average calculation comes, and the conversion ratio of 18 speed transmissions is every grade 0.07166, and actual value distributes very inhomogeneous between 18 gears.As a result, more complicated when operating this speed changer, more will concentrate, this all needs cyclist oneself to go to carry out.

Known hub-type bicycle speed-varying unit with or two epicyclic gear system work, but whether automatically.

Other problem be from many Manpower drivers intrinsic moment variations produce, for example by bike the time, whenever pedal a circle car moment and descend twice, this is to pedal top and the bottom of alternately by its circular movement for the car of angular motion.So conversely, making the majority of exploitation automatic bike speed changer make great efforts all to run into gear shift uncertain problem on opportunity, mainly is because the above-mentioned moment variations of going round and beginning again causes.

As a result, a kind of newer method adopts the microprocessor gear shift, still, has got back on the old problem of power-assisted manual-type transmission of old-fashioned Hudson automobile in 1938.Obviously need a kind of new method, even the electric machinery technological scheme.

On environment and social economy's angle, formerly the technology end can solve automatic speed-changing device for bicycle and also makes us feeling unfortunate, because bicycle is than automobile considerably cheaper, and occupation of land much less, pressure to road is little, do not resemble contaminated air the automobile, the operating cost considerably cheaper, and the sort ofly by bike constantly help healthy motion purpose with what any automobile did not reach bicycle yet.

Main purpose of the present invention is to improve the automatic bike transmission system.

The invention reside in a kind of bicycle speed-varying unit of mobile gear shift, contain: the output torque of automatic perception speed changer, automatically the output torque of perception is transformed into shifting of transmission motion, and, more than combines automatically with the move gear of mobile variable speed device of speed changer.

But the present invention also is a kind of driving force for bicycles speed changer of gear shift, has a shifting of transmission element, contain a bicycle torque sensor output, with an output power moment one speed-change and gearshift converter, described transducer has an output torque input device that is coupled with described torque sensor output, and a shifting of transmission motion output is arranged, and this shifting of transmission element is coupled on the shifting of transmission motion output unit of transducer, more than unites use.

By preferred embodiments of the present invention will be described in detail with reference to the accompanying drawings, can more easily understand the purpose that the present invention relates to and its All aspects of, the same in the accompanying drawings identical or equal parts of label representative, in these accompanying drawings:

Fig. 1 is a relevant portion side view of representing the bicycle of bicycle, tricycle and other human powered vehicle in the scope of the invention, comprises the profile of automatic transmission according to an embodiment of the invention;

Fig. 2 is the schematic representation of automatic transmission according to an embodiment of the invention;

Fig. 3 is the longitudinal section of automatic transmission according to an embodiment of the invention;

Fig. 4 is a substep action gear shift functional schematic according to an embodiment of the invention;

Fig. 5 is the front view of gearshift mechanism details shown in Figure 3, shows cam 80 and axial from right to left associated member;

Fig. 6 is that Fig. 5 details shows the dynamical fashion according to the embodiment of the invention;

Fig. 7 is a shift hysteresis curve according to an embodiment of the invention;

Fig. 8 and Fig. 9 are the front views of a ratchet, the situation and the inoperative situation that work of expression respectively, and ratchet is axial 48 in Fig. 3.

Figure 10 is an overrunning clutch according to an embodiment of the invention, sees from right to left vertically to be positioned at 101 places in Fig. 3;

Figure 11 is the front view of auxiliary planetary gears according to an embodiment of the invention, sees from right to left vertically to be positioned at 110 places in Fig. 3;

Figure 12 is a gear stopper longitudinal section according to an embodiment of the invention, is the modification to Fig. 3.

Figure 13 is electric machinery speed changer longitudinal section and a skeleton diagram according to another embodiment of the invention; With

Figure 14 is the schematic representation of the formula that switches tracks automatic transmission according to still another embodiment of the invention.

Fig. 1 is a relevant portion side view of representing bicycle, tricycle and other human powered vehicle and bicycle in the scope of the invention.

Figure 1 shows that the part of bicycle frame 12, comprise the so-called car central sill 13 that the vehicle seat (not shown) is installed, its supporting saddle (not shown) is installed with seated connection pipe (not shown) adjustablely.Central sill 13 is reinforced by seat strut 14, by means of blockchain pillar 16 and 17 and a pair of wheel frame 18 seat strut 14 is installed on the rear-wheel spindle 15, thereby trailing wheel also is installed.

Be also shown in Fig. 1, bent axle 20 rotates on central sill 13, underbeam 19 and chain pillar 16 and 17 confluces in plain bearing; With one of two pedals 21 and two crank arms 22, the latter drives so-called hinge wheel 23, thereby drives blockchain 24, and blockchain 24 turns over rotating sprocket 25 and comes propelled bicycles 10.

Be also shown in the part of a cassette brake 26 among Fig. 1, act on the wheel rim 27 of trailing wheel 28, represent the manual brake system of bicycle or other human powered vehicle.

The either large or small parts of other significance that do not show among Fig. 1 comprise crossbeam on the man's bicycle or woman's bicycle from the reach out equivalent brace structure of breeches pipe of central sill 13.Brace or crossbeam are connecting underbeam 19 and front fork tube are being installed, and handlebar core (not shown) is installed in the front fork tube, drive bicycle with the angular motion by front-wheel, and front-wheel is installed between a pair of fork sheet of the so-called front fork that stretches out from the lower end of vertical handgrip.

Fig. 1 speed changer according to an embodiment of the invention that schematically draws at 30 places, the label of this speed changer in all the other each figure and following explanation all is 30.

Can adopt the rear wheel drive among front-wheel drive replacement Fig. 1 within the scope of the present invention, in the example of tricycle, also can adopt double rear wheel to drive.

In the embodiment in figure 1, crank arm 22 ends have pedal 21, by this pedal comprise leg and pin by cyclist's health and manpower power is provided.In this regard, bicycle and other human powered vehicle also all are known, and comprise within the scope of the invention.

The manual multi-speed transmission that can realize automation according to the present invention appears in the following patent, and is incorporated by reference at this paper:

Be presented to the U. S. Patent 832,442 of J.Archer, speed change rot on October 2nd, 1906;

Be presented to the U. S. Patent 2.301,852 of W.Brown, epicycle speed change rot November 10 nineteen forty-two;

Be presented to the U. S. Patent 3,021,728 of Keizo.Shimano, the three speed gear of bicycle on February 20th, 1962; With

Be presented to the Swiss Patent 258,751 of Hans Schneeberger, the three-speed gear of bicycle on December 15th, 1948.

These documents formerly comprise sun gear, planetary pinion and relational language, also use these terms in the open and description of drawings of this paper.

Basically, but the objective of the invention is automatically to measure the output torque of gear shift bicycle speed-varying unit.Thereby the present invention has avoided speed described in the previous technique background to measure the shortcoming of bicycle speed-varying unit.Thereby the present invention has automatically the bicycle speed-varying unit gear shift is helped the cyclist veritably, and though be the cyclist need moment be upward slope, descending, or the level land move reposefully.

The present invention automatically changes into shifting of transmission motion to the output torque of measuring, but and by automatically this shifting of transmission motion being applied on the shifting of transmission element of shift transmission, change without latency speed, do not make cyclist's Overexertion yet.

Fig. 2 is the schematic representation of speed changer of implementing one embodiment of the present of invention of these principles.Fig. 3 and Figure 13 are with case representation two related embodiment of the present invention.

Concrete going up said, a kind of automatic transmission of 30 expressions, and it has two

epicyclic gear systems

31 and 32, and each epicyclic gear system has a

sun gear

33 or 34 to be positioned on the rear-wheel spindle 15 shown in Fig. 1 and 3, and the latter is shown among Fig. 2 with signifying.Sun gear 33 usefulness keys are connected on the axle 15, shown in Fig. 3 and 13.

Epicyclic gear system

31 and 32 also has

planetary pinion

35 or 36 round

corresponding sun gear

33 or 34 and be engaged with.Each epicyclic gear system also has a

gear ring

37 or 38 in inner and corresponding

planetary pinion

35 or 36 engagements.Second is driving wheel hub 40 on the gear ring 38 of sensor planet gear train 32 in other words, is connecting the spoke 41 of trailing wheel on wheel hub, for example connects through emanant spoke grappling sheet 42.Certainly, in the scope that the present invention relates to, parts 40 can be represented the drive system of human powered vehicle.

Automatic transmission 30 shown in Figure 2 comprises one first ratchet 43, and it is connected to manpower sprocket wheel 25 on the ring gear 37 of first epicyclic gear system 31 in the input of speed changer 30, but except as described below when idle running.Speed changer 30 also comprises one second ratchet 44, and it interconnects the

planetary pinion

35 and 36 of two

epicyclic gear systems

31 and 32, and is also as mentioned below except when idle running.Speed changer 30 also has one the 3rd ratchet 46, and it can be thrown off by gearshift, shown in first 47 of the gear among Fig. 21,2,3, for example takes third gear.Speed changer 30 also comprises one the 4th ratchet 48, and it also can be thrown off by gearshift, shown in second 49 of the gear among Fig. 21,2,3.When engagement, the 3rd ratchet 46 is connected to sprocket wheel 25 on the planetary pinion 35 of first epicyclic gear system 31.Flexible or replenish ground, if when engagement, the 4th ratchet 48 or be connected on the sprocket wheel 25 through first ratchet 43, or gear ring 37 is connected on the planetary pinion 36 of second epicyclic gear system 32, and carry out different gear shift.

In the embodiment of Fig. 2 and Fig. 3, first and

second ratchets

43 and 44 mechanically interconnect through the ring gear 37 of first epicyclic gear system 31.This is some embodiments' an actual machine structure, and still, for example described gear ring can be in a public inside configuration of the first and the 4th ratchet 43 and 48.In other words, the first and the

4th ratchet

43 and 48 can directly be connected to each other, as long as they also are connected on the gear ring 37, for example transmits manpowers through first epicyclic gear system 31 on certain gear.Within the scope of the invention, the second and the

3rd ratchet

44 and 46 also can have similar structure, as long as they also are connected on the planetary pinion 35 of first epicyclic gear system 31, just can directly be connected to each other.

With regard to gear shift, first and second shifter assemblies 47 and 49 gear 1 show with solid outline, is illustrated in all drop out of gears of first grade (1) last second of automatic transmission and the 4th ratchet 46 and 48.Therefore, gear ring and the

planetary pinions

37 and 35, and planetary pinion 36 and gear ring 38 drive hubs 40 of ratchet 44 and second epicyclic gear system 32 of manpower sprocket wheel input 25 by ratchet 43, first epicyclic gear system 31.Described first gear (1) thus play a part to provide low-speed running to have high torque for bicycle or other human powered vehicle.

On the gear 2 in first shifter assemblies 47, the 3rd ratchet 46 also shows with solid line, and the 4th ratchet 48 shows with dotted line on the gear 2 in second shifter assemblies 49, second grade (2) last the 3rd ratchet 46 that is illustrated in automatic transmission still is a drop out of gear, but, the 4th ratchet 48 is not a drop out of gear, but the engagement in other words that plays a role.Therefore, manpower sprocket wheel input 25 is by first ratchet 43, the 4th ratchet 48 by engagement or through the gear ring 37 of first epicyclic gear system 31 and through the planetary pinion 36 and gear ring 38 drive hubs 40 of second epicyclic gear system 32 directly; On this position, 44 idle running of the 4th ratchet.Described second gear (2) thus rise to bicycle or other human powered vehicle and provide middling speed, the so-called of middle moment running directly to drive.

On the contrary, the gear 3 in first and second shifter assemblies 47 and 49 shows with dotted outline, be illustrated in drop out of gears not of the third gear (3) last second of automatic transmission and the

4th ratchet

46 and 48, in other words conj.or perhaps engagement or play a role.Therefore, manpower sprocket wheel input 25 by ratchet 46, first epicyclic gear system 31 planetary pinion 35 and gear ring 37, and through the planetary pinion 36 and gear ring 38 drive hubs 40 of ratchet 48, second epicyclic gear system 32; On this position,

ratchet

43 and 44 idle running.Described third gear (3) thus rise to bicycle or other human powered vehicle provides at a high speed, low moment running.

According to the gear difference, although

epicyclic gear system

31 and 32 participates in driven sprocket wheel input 25 to wheel 28 wheel hub 40 transmission torques in other words, second epicyclic gear system 32 can be thought the part of moment sensing system according to the preferred embodiment of the invention, because the main effect that this second epicyclic gear system 32 plays in the gear shift function of automatic transmission 30 is to detect output torque for automaitc shfit.

Therefore second epicyclic gear system 32 is connected on the torque transducer 51, as with as shown in the skeleton diagram that Fig. 2 remaining part combines, representative comprises any device of measuring output torque automatically in other words, as shown in arrow 52, the latter automatically converts the output torque of measuring the gear shift campaign of speed changer in corresponding gear shift steps to, 1,2,3 steps of one or a plurality of gear shift gears of representing as 47 and 49 places of Fig. 2.

Further point out as

dotted line

54 and 56, but but shift transmission 30 comes automaitc shfit by shifter assemblies with shift transmission gear shift campaign, as 1 in the three-speed gear, 2,3 steps.

Aspect hereto, although in Fig. 2, represented ratchet 46 and the shifter assemblies of opening in 48

minutes

47 and 48 respectively,, in fact can establish a shifter assemblies for whole speed changer, substantially the manual transmission in the patent of being quoted from as mentioned like that.

With Fig. 3 is example, and speed changer 30 can have an input rotor 60, and this rotor can be installed on the sprocket wheel 25 manpower is acted on the speed changer, thereby acts on the driving wheel 28.This rotor is coupled on the ratchet 59 of bias spring 61, and bias spring is the part of first ratchet 43.Second ratchet 44 also has 63 sentences spring pawl biased 62.This ratchet can be conventional can be at a direction transmission power and the single direction ratchet of bye in the opposite direction.

Therefore, manpower drive input rotor 60 through the gear ring 37 of first epicyclic gear system 31 and planetary pinion 35 by first and

second ratchets

43 and 44 and planetary pinion 36 and gear ring 38 by second epicyclic gear system 32 drive bicycles 10.This represents first gear (1) of above-mentioned low speed, high torque running.

Torque transducer 51 among Fig. 3 embodiment is automatically measured the output torque of speed changer 30 by the sun gear 34 of second epicyclic gear system 32.This speed changer has one to be connected in the end cap 66 at 67 places on the axle 15 with key, thus wheel hub 40 and other moving element transfixion relatively.The core component of torque transducer shown in Figure 3 is a torgue measurement spring 68, and this spring is fixed on the end cap 66 by a kind of annular spring capsule structure 69.On the whole, this spring can be one or the clock spring form of multi-turn, in fact also can be the spring of the form of springs formed of several wind springs.Spring that 68 places are used or spring system can be made and adapt to load or application system, even can be customized by car owner or user's voluntarily personal considerations, and make the travelling comfort optimum of gear shift.

Be coupled by the sun gear 34 with second epicyclic gear system, the inner of spring 68 is connected on the anchor ring 70.Described anchor ring and described sun gear are all done angular motion with respect to axle 15, therefore, the bicycle riding people not only drives cycle wheels 28 through gear ring 38, also through sun gear 34 tension springs 68 of second epicyclic gear system 32, thus the moment of measuring and be the shifting of transmission stored energy.

The present invention automatically converts the moment of measuring to the shifting of transmission motion, and is applied on the shifting of transmission element by automatically shifting of transmission being moved, but automatically to the shift transmission gear shift.For example, axle 15 can be to the hollow cylinder of small part, and the shifting of transmission element can be or comprise a push rod 72 in described hollow shaft.

Described push rod comprises that rides over pushing away rod 73 and handled by it on 74 on the cam, and this pushes away rod can be the axial action type.Figure 4 shows that the key component unfolded drawing in the plane of cam 74, Figure 5 shows that the front view of cam 74, alternately increase or reduce the smooth or tilting

section

75,76,77,78,79 of height in the expression axially, the sun gear 34 that depends on second epicyclic gear system 32 give with the rotation degree.Preferably, on cam 74, radially be provided with similar section group 75 to 79, as shown in Figure 5 with organizing described period of the first time 75 to 79 opposite places.

On the contrary during pull-off spring 68, anchor ring 70 makes cam 74 do angular motion then in the output torque tensioning of measuring.

Cam ramp

76 and 78 acts on and pushes away on the rod 73, and then acts on the push rod 72 and gear shift between several position is for example such in the position shown in 1,2,3 in conjunction with Fig. 2.

In fact, auto-shifting device may overreaction, with the moment of cyclist's effect and the gear shift action a chain of effect (chasing or spurious oscillation) repeatedly mutually that is produced, makes it complexity and turns to disagreeable automatic transmission and do not stop gear shift up and down.In the scope that the present invention relates to, can adopt the buffer of some type to alleviate this problem.But the preferred embodiments of the present invention would rather adopt the mode of some hysteresis to avoid " chasing " problem in the automatic transmission.In fact this hysteresis can be by interior dress the gear shift damping of automatic transmission realize.

For example, for this reason can be with a kind of gear shift control wheel hub or cam 80, as Fig. 3 and shown in Figure 5.This cam can be collaborative with the running roller 81 that pivot on pivotable frame 82 props up, and is perhaps collaborative with other cam follower, for example, rides over the follower on cam 80 peripheries.For example, shown in Figure 3, can be used as to hold and be fixed on this pivotable frame of joint pin 83 supporting in the ring structure 69 with support spring is used.A stage clip 85 can act on the running roller support arm 82, is used for pressing running roller 81 to such an extent that contact with cam 80.

Cam 80 can be the radial action type, and wherein in pairs cam projection is promptly swelled and 87 and 88 realized that desired gear shift damping reaches in other words and discover the purpose that meshes less than " chasing " with running roller 81 is collaborative.As shown in Figure 6, within the scope of the invention, can be with single cam follower 81 with pair of cams protuberance 87 and 88.Yet Fig. 6 can also regard the amplification of cam 80 circumference areas as, and it comprises the fringe area of same radial symmetric.

Fig. 6 represents the action schematic representation of running roller or cam follower 81, and the edge of expression cam 80 is to this running roller relative movement.In an illustrated embodiment, at cam follower along circumferential transfixion and when

only response protuberance

87 and 88 was done radial motion, this cam was done angular motion just.Fig. 6 has polar character, and associated Fig. 4 is a rectangular system, and the radially extension of its cam 80 and the high scale of cam 74 are moment of momentum h and amount of expansion d.

In Figure 4 and 5, zero angle is arranged in the district for 0 °, for example is in gear shown in Figure 2 (2).Preventing that automatic transmission stagnates the uncompleted stagnation of gear shift in other words between gear, the

protuberance

87 and 88 of cam 80 is effectively in occupation of the neutral position.In fact the 87 and 88 anti-effectively thrust rods 73 that swell rest on cam ramp 76 or the cam ramp 78.The protuberance 87 of

cam

80 and 88 collaborative can release pushing away in the positive and negative 7 ° scope on second plane 77 that rod 73 rests on cam 74, this for example represents gear (2),

In further example, above-mentioned first gear (1) can corresponding to the plane 75 of cam 74 and from 77 representatives of plane the angular region between 30 °-23 ° of district's counterclockwise direction.The shifting of transmission device could move in any one direction between gear (1) and (2) after must overcoming protuberance 87.

Otherwise, above-mentioned gear (3) can corresponding to the plane 79 of cam 74 and from 77 representatives of plane the angular region between 30 °-23 ° of district's clockwise directions.The shifting of transmission device could perhaps move behind gear (2) from gear (3) from gear (2) to gear (3) reach after must overcoming protuberance 88.

In this regard, the preferred embodiments of the present invention have been introduced desired hysteresis, and for example as seen from Figure 7, wheel 28 is that the function of the moment T of wheel 28 also is the function of the moment S of sensor spring 68 to the radius R of pedal 22 among the figure.From Fig. 7 as seen, between neutralization high-grade (2) and (3), there is one to lag behind 190, between low and middle-grade (1) and (2), has another to lag behind 191.Other parameter that can regulate stage clip 85 and this system realizes that the optimum under all given purposes lags behind.

Thereby the preferred embodiments of the present invention provide stable and accurate gear shift method for the utmost point cosily carries out gear shift with the manpower that uses the cyclist.

This type of first and

second ratchet

43 and 44 idle running ratchet are known.Mechanical alternans ground engagement and drop out of gear ratchet also are known, and can be used for having the automatic transmission 30 of the gear-changing component 72 (push rod) etc. of this device of driving.

In this respect, the rotor 60 of manpower promotion had both driven first ratchet 43 and had also driven the 3rd ratchet 46 that can replace.In Fig. 3, these ratchets all are

ratchet

59 and 64 internal clickworks in the inboard, also are that ratchet is within the ratchet row of these ratchets.

The planetary pinion 35 of first epicyclic gear system 31 drives second ratchet 44, and this ratchet is ratchet outside in Fig. 3, and promptly its ratchet 62 is outside the ratchet array of this ratchet.This actually the 4th ratchet 48 be arranged in its second ratchet 44 around.

In Fig. 3, the 4th ratchet 48 is internal clickworks that ratchet row drive ratchet 164, as the arrow indication of Fig. 8 and 9, is subjected to the control of ratchet drop out of gear device 91 in other words of a ratchet transposer.As shown in Figure 3, ratchet 164 is arranged in the groove of output rotor 116, and rotor 116 can be second planetary carrier of the planetary pinion 36 of moment sensing epicyclic gear system 32 in other words.

Fig. 8 and Fig. 9 represent the partial section of the 4th ratchet 48 for example, the feasible embodiment of also having represented first, second, third ratchet shown in Fig. 3, the exception part is that first and

second ratchets

43 and 44 do not have the ratchet transposer or say drop out of

gear device

90,91, first and

second ratchets

43 and 44 can be described as the mirror image of the 4th ratchet on configuration, promote ratchet by ratchet, the 3rd ratchet is an outer ratchet as mentioned above.

The ratchet bias spring only is expressed as moment 165 in Fig. 8 and 9.Each core that can replace ratchet is the ratchet transposer 90 of the 3rd ratchet 46 and the ratchet transposer 91 of the 4th ratchet 48.These elements are

ratchet

46 or 48 axial drop out of gears, as among Fig. 9 to shown in the 4th ratchet 48, reach drop out of gear by the movable end of ratchet 146 is pressed from corresponding hook tooth 93.Therefore in state shown in Figure 3, third and

fourth ratchet

46 and 48 drop out of gears and can not transmit any power.

Otherwise, as Fig. 8 to shown in the ratchet 48, ratchet

transposer

90 and 91 is at its axial position, allow these ratchets turn to ratchet 46 or 48 at the effect backspin of

bias spring

65 or 165 by avoiding

ratchet

64 or 164, the movable end that rotates these ratchets 64 of back or 164 up to ratchet 46 or 48 slightly is placed into the position that engages with hook tooth 93.

This transposition for example, can act on the contrary to push away on the rod 73 and realize by above-mentioned cam 74 and a corresponding bias spring 95, thus the latter then passing center transposition bar 72 and promote ratchet transposer 90 push away rod 96 and ratchet transposer 91 push away rod 97.

Ratchet

46 and 48 passive and initiatively situation respectively in Fig. 3 with solid line be shown in dotted line.This respect can be with reference to the shifter assemblies 47 of figure 2 and 49 and to their running explanation.In the scope of the present invention, ratchet

transposer

90 and 91 can have different width or thickness to reach different transposition effects, shown in the shifter assemblies among Fig. 2 47 and 49.

In the scope of the present invention, can adopt different configurations or different types of ratchet in requisite ratchet, perhaps described ratchet herein can adopt the clutch of ring washer type or other form.

According to one embodiment of present invention, the input torque to speed changer is exactly that every pin of cyclist is coupled on the pedal of bicycle.For this reason, the pedal that every pin of cyclist is coupled to bicycle can link with automatic transmission.The example that this pin is coupled pedal sees 99 on the figure, and can represent the toe folder and the toestraps of yacht of familiar racing car and other standard bicycle, and other is connected to the pedal on cyclist's footwear.This pin makes not only pedal the following application of force in angular motion of the skilled cyclist who is absorbed in to being coupled of pedal, and between other moving period, for example goes up in angular motion and angular motion application of force when passing through to pedal circuit top and bottom.In conjunction with automatic transmission of the present invention, this is in fact helpful to the error gear shift that prevents automatic transmission.

As a supplement or more typical accommodation, a preferred embodiment of the present invention has increased an anti-error gearshift in inside on automatic transmission, and it is for more lagging behind to up gear shift to descending gear shift accordingly.For instance, can with a kind of as shown in figure 10, torque transducer or the overrunning clutch in torque transducer 51 are arranged with respect to descending gear shift and the up gear shift that lags behind.

For example, this clutch 100 can act on second in other words on the sun gear 34 of sensing epicyclic gear system 32.On clutch can extend, and itself can constitute or be included in one on the auxiliary sun gear 101 that rotates on the described cylindrical extension, shown in Fig. 3,10,11 outside described sun gear cylindrical.

The clutch element that overrunning clutch 101 can comprise unidirectional biasing is running roller 102 in other words.In the embodiment shown in fig. 10, clutch has an internal surface to be parallel to gear shaft and at the band tip degree cavity 103 of the axle elongation line upper shed of sun gear 34.Running roller 102 be arranged in this cavity and by spring 104 bias voltage apical graftings in this extension, thereby the extension of running roller 102, sun gear 34 and auxiliary sun gear 101 are joined together in relative movement, shown in arrow among the figure 106.The running roller 102 of being setovered on the contrary, can be thrown off from jointing state in angular motion 107.Like this, the not right up gear shift that overrunning clutch 100 just can lag behind and take place when strength rises and falls to pedal, the perhaps up gear shift of misoperation that the drive mechanism medi-spring-the quality vibration causes.

Clutch 100 or its sun gear 101 can be the parts of another planetary gears 110, shown in Fig. 3 and 11.Because second sun gear 112 is wrapping first sun gear 101 in Figure 11.Need see clutch 100 in first sun gear 101 with reference to Figure 10.

Can also can use the even number planetary pinion with odd number in any epicyclic gear system among the present invention.For example, there is the even number planetary pinion in the sun gear system shown in Fig. 3 and Figure 13 31,32 and 110.Figure 11 shows that the odd number planetary pinion on the other hand, be appreciated that also available even number planetary pinion here.

Except this first sun gear, gear mechanism 110 can comprise second sun gear 112, and sun gear 112 can be connected on the axle 15 with key and reach static relatively.This second sun gear 112 preferably diameter greater than the diameter of first sun gear 101.Preferably minor diameter sun gear 101 has planetary pinion 113, and preferred major diameter sun gear 112 has other planetary pinion 114, the latter each preferably less than the diameter of each planetary pinion 113.

Planetary pinion

113 and 114 interconnects with synchronous rotation, and is installed in planetary pinion 36 and second in other words between the planetary carrier 116 of this planetary pinion 36 of moment sensing epicyclic gear system 32.Described planetary carrier can play the output rotor of the second and the

4th ratchet

44 and 48, and can be used for different embodiments of the invention, does not have even among the embodiment of equipment gear mechanism 110.

Concrete going up says that planetary pinion 114 has the pivot 119 of the planetary pinion 36 that connects the planetary carrier 116 and second epicyclic gear system 32, in order to rotate around its static sun gear 112 synchronously with them.Planetary pinion 113 be connected on these planetary pinions 114 with their rotations synchronously and lentamente on the direction 107 opposite with the rotation 106 of planetary carrier 116 angle rotate sun gear 101.

In the embodiment shown, but the pitch line velocity of sun gear 101 is opposite with the proportional direction of the speed at 106 places, is multiplied each other and is removed by the radius of planetary pinion 113 by the difference of the radius of planetary pinion 113 and 114.According to a preferred embodiment of the present invention, select the velocity ratio of equipment gear mechanism 110, in each maximum moment of each pedal between 1/4th refundings, thereby guarantee in the sun gear 101 clutch 100 hysteresis sun gears 34 and through being coupled 52 angular motions that stop cams 80, automatic transmission can up gear shift when little moment like this.

The preferred embodiment of the present invention shown in Fig. 3,10,11 lags behind up gear shift and does not influence descending gear shift.

In fact, when the automatic transmission system applied moment, second sun gear 34 made it energy storage through being coupled 52 pairs of spring energized squares of sensor, and reaches a point the cyclist, at this point,

cam

74 and 80 moves speed changer through transposition bar 73 and element 74 to descending gear shift.Two so descending gear shift illustrate in succession by the arrow that refers to down in Fig. 7.Although the clockwise angular motion with respect to auxiliary sun gear 101 shown in Figure 10 is carried out in the extension of sensing sun gear 34, thereby heading on the bias of spring 104, withdraws from clutch running roller 102 any locked position on the surface 103, but, not influence of auxiliary planetary gears 110 and 100 pairs of this descending gear shift of clutch thereof.

By the output torque of measuring, sensing spring 68 stores the energy that is added in above it.If the added moment of cyclist has reduced, originally be stored in energy in the sensing spring 68 and be tending towards such as illustrated in fig. 10 counter-clockwise ditch and move sun gear 34.When not having clutch 100, as long as the moment that the cyclist applies reduces, this will realize the up gear shift of speed changer by

cam

74 and 80.

But as long as bicycle is being gone ahead, auxiliary epicyclic gear system 110 just rotates its sun gear 101 on the direction of arrow 107.Because the effect of clutch 100 is no matter be that sensing sun gear 34 can be faster than auxiliary sun gear 101 on counterclockwise direction or be coupled 52.As a result, after the up gear shift of

cam

74 and 80 was lagged behind sensing spring 68 energy stored or resulting energy and the output torque balance of measuring, this marked in succession with the arrow that makes progress in Fig. 7, the situation of two gear-change operations of expression.

The preferred embodiments of the present invention of discussing convert in the shifting of transmission motion automatically in the output torque of measuring now, metering is stored in the energy in the sensing spring 68, so that the spring that takes place in the system-quality is vibrated even without obtaining stopping also to be subjected to damping, the fluctuating that in the running of bicycle, can occur inevitably, when for example driving moment reduced when pedal moves on the summit, also unlikely reaching carried out error gear shift to automatic transmission.

For instance, energy stored measurement be used for the lagging behind up gear shift of gearshift of speed changer 30 and 230 in the sensing spring 68.In this respect, can measure the degree that sensing springs 68 be emitted its energy with clutch 100 and auxiliary planetary gears 110, as by means of Fig. 3,10,11 above disclosed.Aspect device, the torque sensor output 51 of bicycle can comprise an output torque energy storing device 68 of measuring, and outputting power moment comprises a stored energy measuring device 101,110 to shifting of

transmission converter

70,74,80.This stored energy measuring device can be a unidirectional up shift hysteresis device, as the form of overrunning clutch 100 or comprise its form.

According to a further advantageous embodiment of the invention, can be locked in a given gear to automatic transmission.This can be called hand shift lock 123, can do to such an extent that act on the part of automatic transmission, for example acts on the element of its torque transducer 51.

To this aspect, Figure 12 represents that a warp is coupled element accordingly, and for example pin 125 and chamber 126, corresponding hole act on the auxiliary anchor ring 124 on the sensor anchor ring 70.The quantity in chamber, hole can be corresponding to the quantity of gear, perhaps the quantity on the plane shown in Fig. 4 to 6 75,77,79.

This element that is coupled can be manual control.For example, the bias that can be used to head on spring 128 of the backguy transmission 53 used of technology formerly keeps auxiliary anchor ring 124 to throw off with sensed system anchor ring 70.Can discharge auxiliary anchor ring 124 when discharging backguy transmission 53, the bias of spring 128 makes pin 125 mesh chamber, hole 126, thereby sensing sun gear 36 no longer can rotate anchor rings 70 with respect to static lid 66.If the time spent is done in the automaitc shfit of wanting to recover speed changer 30, operate backguy transmission 53 again shift lock element 125 is pulled away from sensing anchor ring 70.

In the scope of the present invention, can electrical sensing moment, also can the electricapparatus mode drive automatic transmission.For example, Figure 13 shows an electric embodiment.The mechanical part of this electricapparatus speed changer 130 for example can comprise the input rotor 60 of chain wheel drive, first epicyclic gear system 31 and be coupled planetary pinion respectively and the ratchet of

gear ring

35,37 43,44,46,48, ratchet

transposer

90 and 91, one similar to above-mentioned output rotor 116, but the more direct output rotor 216 that is coupled on the cycle hub 40 reaches the mechanical part that Fig. 3 and Figure 13 have.

Electricapparatus speed changer 130 also comprises an electric part, and for the ease of understanding, these parts have added hundred bit digital on the similar parts label in the embodiment of Fig. 1 to Figure 11, and this just is not in order to limit to some extent for example certainly.

The moment of Figure 13 is measured and can be comprised an electrical measurement table, and for example resistance strain gauge 134, measure moment from axle 15, and axle 15 is to be promoted restraining of axle two ends and applied moment by sun gear 33.This resistance strain gauge is preferably mounted on the opposite end of axle 15, becomes miter angle with the axis of axle 15.The curved component of axle has been cancelled, the torsion that the sun gear 33 of the epicyclic gear system 31 that manpower promotes is applied can be added on the electrical measurement torque transducer 151, the latter can comprise a resistance strain gauge reference amplifier, and this amplifier serves as the resistance strain gauge signal conversion digital signal of the manpower moment measured of expression in the known mode of strain sensing technos.

This electrical measurement torque signals 171 can equal the moment that anchor ring 70 shown in Figure 3 transmits.Similar with the cam structure 80 shown in Fig. 4 to 6 to Fig. 3, the circuit among Figure 13 can comprise the circuit 180 of a routine, the peak value of its response signal 171, thus only read peak value.For example, circuit 180 can comprise a moment size resolving device, with the conventional element of this schmitt trigger circuit and so on, torque signals 171 is converted to three steady switching signals.Can avoid unstability by the peak signal that only detects output torque, and, can usage counter in circuit, as 151, number goes out above-mentioned recurrent moment and rises and falls, to prevent error gear shift.

The torque signals of measuring 171 is handled the back by circuit 180 and is delivered to a switching circuit 174 that is similar to the gear-changing component 72 of Fig. 3 with a lead 173, the latter play a part optionally to replace third and fourth ratchet 46 and 48.For this reason, switching circuit 174 applies switching signal by the

manipulator

196 and 197 to the ratchet transposer, occurs in the torque signals that the response at 173 places was handled.For example, such manipulator can comprise magnet driver, and switching circuit 174 can comprise a magnet driver selector, and it can be a gear-changing component that is similar to mechanical type gear-changing component 72 shown in Figure 3 substantially.

In this respect, magnet driver 196 alternately is electromagnet 200 separately and 201 power supplies, is provided with the ratchet transposer 90 of the 3rd ratchet 46 between these electromagnet.Similarly, magnet driver 197 alternately is electromagnet 202 separately and 203 power supplies, is provided with the ratchet transposer 91 of the 4th ratchet 48 between these electromagnet.For example, magnet driver 197 can be high one low-grade driver, gear shift between height and low grade, and magnet driver 196 can be in the bay driver, to or carry out gear shift from middle-grade.

Therefore, for electromagnet 201 power supplies the 3rd ratchet 46 is replaced and remain on the drop out of gear state through driver 196.Similarly, for electromagnet 203 power supplies the 4th ratchet 48 is replaced and remain on the drop out of gear state through driver 197.

On the contrary, for electromagnet 201 power supplies the 3rd ratchet 46 is replaced and remain on engagement through driver 196.The 4th ratchet 48 is switched and remains on extension for electromagnet 202 power supplies through driver 197 and nibble state.

According to a preferred embodiment of the present invention, ratchet

transposer

90 and 91 is or comprises permanent magnet, thereby can or repel its

corresponding ratchet transposer

90 or 91 for electromagnet 200,201,202,203 power supplies or attraction.Preferably, electromagnet 201,202 has soft iron core, thereby each

ratchet transposer

90 or 91 can remain in the electromagnet that sucts at last, up to being reversed the electromagnet power supply.In this case, described electromagnet of being powered needn't be powered for the switching ratchet is remained on switching state, because the permanent magnet of

ratchet transposer

90 and 91 can maintain the soft iron core on the adjacent electromagnet.

In fact, can be implemented in the switching mode shown in switch square frame Figure 47 and 49 on magnet driver selector 174 and magnet driver 195 and 197, be used for to realize gear shift with reference to figure 2 and described mode such as following.Magnet driver selector 174 can be for this reason or the programming of the switching mode of any other hope.

There is the ratchet transposition activity of negative function to compose with bi-stable character by above-mentioned circuit 180.Flexible or replenish ground, can be provided with and have with Fig. 4 to the

bending spring

205 and 206 of the analog structure of one of protuberance shown in Figure 6 87 and 88 to strengthen the bistability of each ratchet ex-situ operations.Aspect this, in machinery type shown in Figure 3, spring 95 provides vitality, and

mobile ratchet transposer

90,91 to ratchet transposition action is finished.In the electricapparatus mode, can provide electromagnetism field boundary power to extend with spring 205,206 etc., be used in the short time that Fig. 8 and 9 example ratchets move postpones, coming

mobile ratchet transposer

90,91 between its position.

Be the manual locking device shown in simulation Figure 12 etc., the embodiment of Figure 13 can comprise a shift lock device, as the form of the switch 223 between torque transducer 151 and solenoid actuated selector.This switch is a normally closed switch, is offset to the position of closing in other words, is measuring the gear shift that responds when output torque changes.

Flexible ground, the switch 223 use-cases wiring 53 or other the manual mode application of force 153 as shown in Figure 12 opened.Can interrupt in this way providing shift signal, at this moment electricapparatus speed changer 130 manually is locked in any advantage gear to magnet driver.Can be released in the position of closing to switch 223, then recover the automatic switchover of speed changer.

Automatic transmission 130 can with powered battery also can dynamo lighting set etc. other power generation system power supply of usefulness.

The embodiment of Figure 13 has adopted several balls, needle bearing or other conventional bearing.

Although explain and preferred planetary pinion or hub-type integration speed changer, the present invention and embodiment's shown in Figure 2 etc. principle also can be used to the formula shift transmission that switches tracks.

For instance, Figure 14 represents a kind of automatic transmission 230, wherein, has replaced first epicyclic gear system 31 of

gear transmission

30 and 130 with the formula shift transmission 231 that switches tracks.

The formula shift transmission of switching tracks is known and comprises Idle wheel and the guide wheel (not shown), takes turns and the gear train (not shown) around the chain of trailing wheel 28 with at the sky in sprocket wheel 25 zones.The same with Fig. 2, the input of sprocket wheel also is designated as 25 in the drawings.

Moment sensing and transmission shift system comprise second epicyclic gear system 32 and torque transducer 51, also can be provided with according to a preferred embodiment of the present invention; At this moment, for being applied to the output torque of the formula shift transmission 231 that switches tracks on the wheel hub 40 and (b) measuring this output torque, (a) be the formula shifting of transmission that switches tracks, shown in dotted line 154.

Within the scope of the invention, speed changer 130 can mix, and is for example both can automatic or manual dual-purpose, also can be from moving gear and manually switch tracks type and usefulness.

Although this paper discloses with detailed embodiment and the present invention relates to its All aspects of, the present invention neither is subjected to the restriction of these details, also is not subjected to the restriction of its form of implementation.On the contrary, open and specification above has pointed out the extensive use that the present invention relates to and has far exceeded the variable general character that this paper is the described element of help understanding with the bottom.Therefore " for example " speech will be understood that it is to propose each specific or digital statement or prompting.

According to an aspect that the present invention relates to, the output torque of the present invention by automatically measuring speed changer, automatically the moment of measuring is converted to the gear shift campaign and automatically uses described gear shift campaign shift transmission, thereby be the bicycle speed-varying unit gear shift of shift.

For reaching this purpose, a shift driving force for bicycles speed changer 30,130,230 can have a shifting of transmission element, as 72,154,174, and comprise, 51,151 and output torques of a bicycle torque sensor output are to shifting of transmission converter 68,74,180, the latter has an output torque input that is coupled to torque sensor output, as 52 or 171, also has a shifting of transmission motion output 73,173.Gear-changing component 72,174 is coupled in the gear shift campaign output of described transducer.

Mechanically perception output torque, torque sensor output 51 can be output

mechanical torque sensors

34,42,68.In addition, also electrically perception output torque is as adopting resistance strain gauge 134 at 151 places.Torque sensor output is preferably in the inner sensing of speed changer, and torque sensor output 51,134,151 is preferably in the inside of speed changer 30,130,230.

Can occur corresponding to the variable to output torque in the speed changer, output torque is from this variable sensing.Torque sensor output 51,151 can comprise that other sensing such as sun gear 34, resistance strain gauge 134 is corresponding to the device of output torque variable in the speed changer 30,130,230, with a spring 68, resistance strain gauge reference amplifier 151, moment size resolving device 180 and other device from described variable sensing output torque.

In speed changer 30 or 230, can comprise a planetary pinion 32, and above-mentioned variable can obtain from this planetary pinion.Torque sensor output 51 can be coupled to described planetary pinion, shown in Fig. 2,3,14 52.This torque sensor output 51 can be coupled on the sun gear 34 of described epicyclic gear system 32, and perhaps above-mentioned variable can also obtain from the sun gear 34 of this epicyclic gear system 32.

First and second

epicyclic gear systems

31 and 32 can differently be contacted with speed changer, and above-mentioned variable can obtain from one of these epicyclic gear systems, for example, waits until from epicyclic gear system 32.Speed changer can comprise first and second

epicyclic gear systems

31 and 32 of different polyphones, and torque sensor output 51 is coupled to one of these epicyclic gear systems, as is coupled to second epicyclic gear system 32.

The gearshift mechanism of speed changer can comprise through first epicyclic gear system and carries out reversing of transmission torque, as in a gear from gear ring 37 to planetary pinion 35 (for example, when third and

fourth ratchet

46 and 48 is not driven), and as in another gear from planetary pinion 35 conversely again to gear ring 37 (for example, when third and

fourth ratchet

46 and 48 modes with the described torque transmitting of reversing are driven).

Above-mentioned variable can apply strain to an element in the speed changer, then from this strain sensing output torque.For example, torque sensor output can comprise a resistance strain gauge on element in speed changer, as shown in figure 13.This element can be the axle 15 that has added strain on it, and resistance strain gauge 134 can be installed on this axle.

Another example of such element is the spring 68 shown in Fig. 3, is added with strain on it, for example by being coupled 52 strains that applied by sun gear 34.Torque sensor output 51 can comprise a spring 68 that is connected on the speed changer 30.

In speed changer, can comprise switch tracks a formula speed changer 231 and a gear mechanism 32.As shown in Figure 14.Output torque can be from these gear mechanism 32 sensings.The formula speed changer of switching tracks can move gear shift with above-mentioned shifting of transmission, shown in 154 among Figure 14, and switch tracks a formula speed changer 23 1 and the gear mechanism 32 between the output of this switch tracks formula speed changer and speed changer 230 shown in the figure.Torque sensor output 51 is coupled on these gears, and as the gear at 52 places, shifting of transmission element 154 is coupled on the formula speed changer that switches

tracks.Gear

34,34,38 can be arranged in the epicyclic gear system.

Speed changer can be upper and lower to gear shift, and can upper and lower to gear shift between add the preceding paragraph in the automaitc shfit and lag behind 190,191, as shown in Figure 7.Go up to can comprise the cam 74 that acts on gear-changing component 72 and ratchet 46 and 48 and lagging device can include the cam 80 of

protuberance

87,88 etc. to selector down.

The output torque energy of measuring can store, mechanically deposit spring 68 in or electrically exist in the circuit 180 as existing, and, this energy stored can be measured in the automatic switch of shifting of transmission motion in moment, and in fact this energy stored can measure the gear shift with hysteresis shift transmission 30,130,230.For example, measuring energy can discharge by the auxiliary planetary gears 110 that has overrunning clutch 100, and this planet gear mechanism also plays hysteresis.Preferably with respect to the descending gear shift up gear shift that more lags behind.For example, the output torque of measuring is being converted to the up gear shift that lags behind when shifting of transmission moves.Speed changer 30,130 can comprise up gear shift transposer and descending

gear shift transposer

90,91 and shift hysteresis device 87,88,100,180.

According to a preferred embodiment of the present invention, the moment of measuring automatically converts the shifting of transmission motion to, its step is corresponding to the gear of speed changer, (1), (2) and (3) shelves for example, and, in described step, this shift speed changer is by automatically with the gear shift automatically of moving of described shifting of transmission.The moment of speed changer can comprise a step switch converter 74,80,180 to the shifting of transmission converter, and they have the shifting of transmission motion output of substep at 73 or 173 places.

In this mode and any alternate manner in the scope of the present invention, automatic transmission preferably has different gears, (1), (2), (3) shelves for example, corresponding with different output torques, and the conversion of output torque preferably lags behind to the moment measured when reaching numerical value corresponding to the different shift point of speed changer.Be worth accordingly as long as the moment of measuring reaches with the different shift point of speed changer, just automatically send the output torque conversion, this shift switches by described speed changer being applied the shifting of transmission motion and automatically carries out.This respect, shifting of transmission element 72,174 has different shift point, and is corresponding with the different output torques on being applied to speed changer.And transducer can have a

ratchet

87,88, the conversion of output torque to the shifting of transmission motion is used to lag behind, thereby the gear shift of hysteresis speed changer reaches the corresponding value of different shift point with the shifting of transmission element up to the output torque of measuring, as the enforcement by circuit 180.

The shifting of transmission element can be a displacement variable speed transmission gear-changing component 72, and the input of its output torque is a rotation

output torque input

34,52,70,74 that is coupled with a torque sensor output 51,68.Shifting of transmission motion output can be a displacement variable speed transmission gear shift campaign output 73 that is coupled with described rotary output torque input.Displacement variable speed transmission gear shift 72 can be coupled with displacement variable speed transmission gear shift campaign output 73.

Speed changer typically has different high and low gears corresponding with different output torques, and automatically the lagged behind output torque measured of the conversion of output torque reaches a corresponding value of different gears with described speed changer.Be worth accordingly with the different gears of speed changer as long as the moment of measuring reaches one, just automatically send the conversion of output torque.Preferably, the conversion of this output torque automatically lags behind and sends after time of a delay, from output torque, from low-grade location to a high tap position with have different shift point from high tap position to a low-grade location, as shown in Figure 7.Variable gear gearbox automaticallyes switch at different shift point like this.

From output torque, the shift point of gear is preferably lower than the shift point of gear from high to low from low to high, for example as shown in Figure 7.Shifting of transmission element 72 preferably has different height gears, corresponding with the different height and the low output torque that act on respectively on the speed changer, and

transducer

74,80 has arresting device 87,88,100, be used to lag behind output torque to the conversion of shifting of transmission motion, and make from low grade to high-grade be shifting of transmission to low grade at different shift point from top grade.

But shift bicycle speed-varying unit 30,130,230 can be locked in any gear.For example can on speed changer, be coupled a hand shift lock 123,223, as first-class by the shift lock device being coupled to torque transducer 51,151.

This paper has done open widely with many examples of machinery and electrical form, the one of ordinary skilled in the art can make various modification changes and not exceed the spirit and scope of the present invention in the scope of the present invention and All aspects of thereof.

Claims

1. one kind is the method for bicycle shift shifting of transmission, combines to comprise:

Automatically measure the output torque of described speed changer;

Automatically the output torque of measuring is converted to the shifting of transmission motion; And

Automatically be described shift shifting of transmission with described shifting of transmission motion.

2. the described method of claim 1 is characterized in that, described output torque is mechanically measured.

3. the described method of claim 1 is characterized in that, described output torque is electrically measured.

4. the described method of claim 1 is characterized in that, described output torque is measured in described speed changer.

5. claim 1,2,3 or 4 described methods is characterized in that, produce the variable corresponding to described output torque in described speed changer; And described output torque is to measure from described variable.

6. the described method of claim 5 is characterized in that, described variable is to produce by means of teeth parts in the described speed changer.

7. the described method of claim 5 is characterized in that, comprises a planetary gears in described speed changer; And described variable obtains from described planetary gears.

8. the described method of claim 7 is characterized in that, described variable is that a sun gear from described planetary gears obtains.

9. the described method of claim 5 is characterized in that, first and second planetary gears are contacted in described speed changer changeably, and described variable obtains from one of described planetary gears.

10. the described method of claim 9 is characterized in that, described gear shift comprises through described first planetary gears transmission torque that reverses.

11. the described method of claim 9 is characterized in that, described variable obtains from described second planetary gears.

12. the described method of claim 5 is characterized in that, described variable is added in strain on the element in the described speed changer; And described output torque is measured from described strain.

13. the described method of claim 12 is characterized in that, described element is an axle that applies described strain on it.

14. the described method of claim 12 is characterized in that, described element is a spring that applies described strain on it.

15. claim 1,2,3 or 4 described methods is characterized in that, comprise switch tracks a formula speed changer and a gear mechanism in speed changer; Described output torque is measured from described gear mechanism; And the described formula speed changer that switches tracks moves gear shift with described shifting of transmission.

16. the described method of claim 15 is characterized in that, described gear mechanism is arranged in the epicyclic gear system.

17. claim 1,2,3 or 4 described methods is characterized in that, described speed changer can up gear shift and descending gear shift; And the described automaitc shfit between described up gear shift and descending gear shift gear shift applies a hysteresis.

18. claim 1,2,3 or 4 described methods is characterized in that, store the energy of the described output torque of measuring; And in the automatic conversion that the output torque of measuring is converted to the shifting of transmission motion, measure described stored energy.

19. the described method of claim 18 is characterized in that, measures described stored energy with the up gear shift in the described shift shifting of transmission that lags behind.

20. claim 1,2,3 or 4 described methods is characterized in that, described speed changer can up gear shift and descending gear shift; And described up gear shift more lags behind with respect to described descending gear shift gear shift.

21. the described method of claim 20 is characterized in that, the described moment of measuring is being converted to the described up gear shift that lags behind when shifting of transmission moves.

22. claim 1,2,3 or 4 described methods is characterized in that, with the gear of described speed changer corresponding progressive rapid in, the described moment of measuring is changeed and is automatically changed the shifting of transmission motion into; And by in described step, coming to be the automaitc shfit of described shift speed changer with described shifting of transmission motion automaitc shfit.

23. the described method of claim 22 is characterized in that, described speed changer can up gear shift and descending gear shift; And described up gear shift more lags behind with respect to described descending gear shift.

24. the described method of claim 23 is characterized in that, the described moment of measuring is being converted to the described up gear shift that lags behind when shifting of transmission moves.

25. claim 1,2,3 or 4 described methods is characterized in that, described speed changer has and the corresponding different gears of different output torques; The conversion of the described output torque that automatically lags behind reaches one up to the described output torque of measuring and is worth accordingly with the different gears of described speed changer; After the described output torque of measuring reaches a corresponding value of the different gears with described speed changer, the conversion of just automatically sending described output torque; Automatically is described shift shifting of transmission with sending described conversion back by apply a shifting of transmission motion to described speed changer.

26. claim 1,2,3 or 4 described methods is characterized in that, described speed changer has and corresponding different up gear shift of different output torques and descending gear shift gear; The conversion of the described output torque that automatically lags behind reaches with the different gear of described speed changer up to the described output torque of measuring and to be worth accordingly; After the described output torque of measuring reaches a corresponding value of the different gears with described speed changer, the conversion of just automatically sending described output torque; The conversion of output torque is lagged behind and is discharged by a certain hysteresis, make from a low-grade location to a high tap position with from a high tap position to a low-grade location in different shift point release output torques; And automatically be the shift shifting of transmission at different shift point.

27. the described method of claim 26 is characterized in that, from output torque, the shift point from a low-grade location to a high tap position is lower than the shift point from a high tap position to a low-grade location.

28. claim 1,2,3 or 4 described methods is characterized in that described shift bicycle speed-varying unit can be locked in arbitrary gear.

29. claim 1,2,3 or 4 described methods is characterized in that, are applied to input torque on the described speed changer by balance on the pedal that every pin of cyclist is coupled in bicycle.

30. the driving force for bicycles shift speed changer with a shifting of transmission element combines and comprises:

A bicycle torque sensor output; With

An output torque converts the transducer of shifting of transmission motion to, has an output torque input device and a shifting of transmission motion output unit that is coupled on the described torque sensor output; Described gear-changing component is coupled on the described shifting of transmission motion output unit of described transducer.

31. the described speed changer of claim 30 is characterized in that, described torque sensor output is the torque sensor output of a machinery.

32. the described speed changer of claim 30 is characterized in that, described torque sensor output is an electric torque sensor output.

33. the described speed changer of claim 30 is characterized in that described torque sensor output is in described speed changer.

34. claim 30,31,32 or 33 described speed changers is characterized in that, described torque sensor output is included in and measures a device corresponding to the variable of described output torque in the described speed changer; With the device that described output torque is measured from described variable.

35. claim 30,31,32 or 33 described speed changers is characterized in that described torque transducer comprises the teeth parts in described speed changer.

36. claim 30,31,32 or 33 described speed changers is characterized in that described speed changer comprises a planetary gears; And described torque sensor output is coupled with described planetary gears.

37. the described speed changer of claim 36 is characterized in that, a sun gear in described torque sensor output and the described planetary gears is coupled.

38. the described speed changer of claim 36 is characterized in that, described speed changer comprises first and second planetary gears of polyphone changeably; And one of described torque sensor output and described planetary gears are coupled.

39. the described speed changer of claim 38 is characterized in that, comprises through being coupled in the reverse device of output torque of described first planetary pinion on the described shifting of transmission element.

40. the described speed changer of claim 38 is characterized in that, described torque sensor output is coupled on described second planetary gears.

41. claim 30,31,32 or 33 described speed changers is characterized in that, described torque sensor output comprises a resistance strain gauge on the element that is added in the described speed changer.

42. the described speed changer of claim 41 is characterized in that, described element is an axle; And described resistance strain gauge is contained on the described axle.

43. claim 30,31,32 or 33 described speed changers is characterized in that, described torque sensor output comprises a spring that part is coupled with described speed changer.

44. claim 30,31,32 or 33 described speed changers is characterized in that, comprise a formula speed changer and at this gear mechanism between the output of formula speed changer and described speed changer of switching tracks of switching tracks, described torque sensor output and described gear mechanism are coupled; And be coupled the shifting of transmission element on the described formula speed changer that switches tracks.

45. the described speed changer of claim 44 is characterized in that, described gear mechanism is in an epicyclic gear system.

46. claim 30,31,32 or 33 described speed changers is characterized in that, described speed changer comprises up gear shift and descending gear shift gear shift transposer; And the device that on described up gear shift and descending gear shift transposer, applies a hysteresis.

47. claim 30,31,32 or 33 described speed changers is characterized in that, described bicycle torque sensor output comprises an output torque energy accumulating device of measuring; And the transducer that output torque converts the shifting of transmission motion to comprises a stored energy measuring device.

48. power right profit requires 47 described methods, it is characterized in that described stored energy measuring device is a unidirectional up shift hysteresis device.

49. claim 30,31,32 or 33 described speed changers is characterized in that, described speed changer comprises up gear shift and descending gear shift gear shift transposer; And the shift hysteresis device optionally is coupled with described up gear shift transposer.

50. claim 30,31,32 or 33 described speed changers is characterized in that, are being a step switch converter that the shifting of transmission motion output of stepping is arranged to described transducer.

51. the described speed changer of claim 50 is characterized in that, described speed changer comprises up gear shift transposer and descending gear shift transposer; With the device that on described up gear shift and descending gear shift transposer, applies a hysteresis.

52. the described method of claim 50 is characterized in that, described speed changer comprises up gear shift transposer and descending gear shift transposer; And described shift hysteresis device optionally is coupled on the described up gear shift transposer.

53. claim 30,31,32 or 33 described speed changers is characterized in that, described shifting of transmission element have be applied to described speed changer on the corresponding different gears of different output torques; Described transducer has an arresting device, is applicable to the described output torque that lags behind to the shifting of transmission movement conversion, reaches one and is worth accordingly with the different gears of described speed changer up to the described output torque of measuring.

54. claim 30,31,32 or 33 described speed changers is characterized in that, described shifting of transmission element is a displacement gear-changing component; The output torque input device is a rotation output torque input device that is coupled to described torque sensor output; Described shifting of transmission motion output unit is a displacement variable speed transmission gear shift campaign output unit that is coupled on the described rotation output torque input device; And described displacement variable speed transmission gear-changing component is being coupled described displacement variable speed transmission gear shift campaign output unit.

55. claim 30,31,32 or 33 described speed changers is characterized in that, described shifting of transmission element have respectively be applied to described speed changer on different low and the corresponding different low and high tap position of high output torque; And described transducer has an arresting device, is applicable to the conversion of hysteresis output torque to shifting of transmission motion, for from a low-grade location to a high tap position with by different shift point described speed changer is carried out gear shift from high tap position to a low-grade location.

56. claim 30,31,32 or 33 described speed changers is characterized in that, are coupled a manual gear lock on described speed changer.

57. the described speed changer of claim 56 is characterized in that, comprises that one is coupled to device on the described torque transducer to described gear lock.

58. claim 30,31,32 or 33 described speed changers is characterized in that, every pin of cyclist is coupled on the pedal of bicycle, the latter is connecting described speed changer.