CN104776183B - Continuously variable transmission - Google Patents

Abstract

The invention provides a continuously variable transmission. The change rate of the rotating radius of a crank-link mechanism to the rotating angle of a rotating disc is relatively high at the OD side. The continuously variable transmission (1) converts the rotation movement of an input shaft (2) into swing movement of a swing connecting rod (18) supported by an output shaft (3) through the rotating radius regulating mechanism (4). The rotating radius regulating mechanism (4) is provided with a cam disc (5), a pinion (70) and a rotating disc (6). The cam disc (5) rotates with the input shaft (2) in an eccentric state. The pinion (70) and the input shaft (2) rotate concentrically and oppositely. The rotating disc (6) is supported by the cam disc (5) to rotate freely in an eccentric state, and is provided with an internal rack (6b) engaged with the pinion (70). When the rotating radius (R1) is relatively large, pitch radii (70c, 6c) of the engaged positions of the pinion (70) and the internal rack (6b) are larger than pitch radii (70c, 6c) of the engaged positions when the rotating radius (R1) is relatively small.

Description

Buncher

Technical field

The present invention relates to the buncher of four-bar mechanism type, it is using the rotation being located in the center of rotation axis of input shaft Turn radius governor motion and adjust radius of turn, thus freely carry out speed change.

Background technology

In the past, it is known that possess the buncher of the four-bar mechanism type of following part：Input shaft, from being arranged at vehicle The driving force of the main driving source such as electromotor is passed to the input shaft；Output shaft, it is abreast configured with input shaft；Multiple rotations Radius governor motion, they are arranged in the center of rotation axis of input shaft；Multiple swing connecting bars, they are by e axle supporting in defeated Shaft；And connecting rod, the connecting rod is an end with the input for being rotatably coated at radius of turn governor motion Side annulus, another end of the connecting rod links (for example, referring to Japanese Unexamined Patent Publication 2013- with the swing end of swing connecting bar No. 24382 publications).

Above-mentioned infinitely variable speeds are corresponded in the 1st described in Japanese Unexamined Patent Publication 2013-24382 publications, the 2nd variator Device.The input shaft of the variator, output shaft, radius of turn governor motion, swing connecting bar and connecting rod constitute crank connecting link machine Structure.The one-way clutch that mechanism is prevented as single direction rotation, the one-way clutch are provided between swing connecting bar and output shaft Swing connecting bar is fixed on into output shaft when swing connecting bar will be rotated against relative to output shaft to side, the one-way clutch exists Swing connecting bar makes swing connecting bar dally relative to output shaft when rotating against to opposite side relative to output shaft.

Radius of turn governor motion is made up of following part：Discoid cam part, it is with relative to input eccentric shaft State integratedly rotates with input shaft；Little gear, the driving force for carrying out self-regulation driving source is passed to the little gear, the little tooth Wheel can with one heart be rotated against relative to input shaft；And discoid rotating part, it rotatably links with connecting rod. Rotating part by cam part with relative to the eccentric state support of cam part into rotating freely.It is provided with rotating part and is nibbled with little gear The internal gear of conjunction.

Radius of turn R1 of toggle is between the central point of rotating part and the center of rotation axis of input shaft Distance, it determines the gear ratio of buncher.Radius of turn R1 is by radius of turn governor motion using regulation driving source Driving force is adjusted.

That is, little gear be conditioned with driving source with the rotary speed same speed of input shaft drive in the case of, Rotating part integratedly rotates with cam part.In this case, radius of turn R1 is fixed, driving force by with constant gear ratio from Input shaft is transferred to output shaft.

In the case of there is difference between the rotary speed of input shaft and the rotary speed of little gear, rotating part is in cam part Around rotate.Radius of turn R1 changes corresponding to the angle, θ of the rotation.Therefore, by making little gear relative to input Axle faster or slower rotates and then recovers to same speed, can select anglec of rotation θ, changes radius of turn R1, control Gear ratio.

For example, make radius of turn R1 become minimum, such as zero anglec of rotation θ min by selection and be used as anglec of rotation θ, Gear ratio can be set as maximum or infinity.In addition, by selecting to make radius of turn R1 become maximum anglec of rotation θ Max, can be set as minimum by gear ratio.

But, according to above-mentioned conventional buncher, radius of turn R1 is becoming relative to the variation characteristic of anglec of rotation θ Speed compares drastically than big θ min sides, in the little θ max sides of gear ratio than shallower.

Therefore, in the gear ratio of gear ratio little OD (overdrive) side, radius of turn R1 is relative to anglec of rotation θ Rate of change is little, therefore good response when cannot obtain speed change.In order to obtain good response, need and radius of turn R1 is less accordingly with higher speed driving pinion relative to the rate of change of anglec of rotation θ, makes regulation driving source Load increases.

The content of the invention

The present invention in view of the above problems, its object is to provide a kind of radius of turn of toggle relative to rotation The rate of change of the anglec of rotation of transfer part is in the also larger buncher in OD sides.

The buncher of the present invention is characterised by possessing：Input unit, the driving force for carrying out autonomous driving source is passed to The input unit；Output shaft, it is configured to parallel with the center of rotation axis of the input unit；Toggle, it has quilt The rotary motion of the input unit is converted to the swing fortune of the swing connecting bar by e axle supporting in the swing connecting bar of the output shaft It is dynamic；And single direction rotation prevents mechanism, it will be rotated against relative to the output shaft in the swing connecting bar to a direction When the swing connecting bar is fixed on into the output shaft, and to revolve to another direction is relative relative to the output shaft in the swing connecting bar Make the swing connecting bar relative to the output shaft idle running when turning, the toggle possesses：Radius of turn can freely be adjusted Radius of turn governor motion；And the connecting rod of the link radius of turn governor motion and the swing connecting bar, the rotation Turn radius governor motion to possess：Cam part, it is with relative to the eccentric state rotation of the center of rotation axis；Little gear, its Can rotate relative to the cam part with one heart with the center of rotation axis；And rotating part, it is with relative to described convex The eccentric state of wheel portion is supported to by the cam part and is rotated freely, and with the internal gear engaged with the little gear, the rotation Portion rotatably links with the connecting rod, both sections at the little gear and the intermeshing position of the internal gear Radius of circle increases corresponding to the increase of the radius of turn.

In present configuration, the amount of radius of turn R1 of toggle and the oscillating motion of swing connecting bar, i.e. without The gear ratio of level variator is corresponding.Also, in the rotary speed identical mode of the rotary speed of cam part and little gear In the case of driving regulation driving source, rotating part integratedly rotates with cam part, therefore radius of turn R1 is maintained perseverance It is fixed.

On the other hand, when making regulation there is poor mode between the rotary speed of cam part and the rotary speed of little gear When being driven with driving source, rotating part is rotated centered on the central point of cam part around cam part.Radius of turn R1 correspondence Change in the angle, θ of the rotation.That is, if the value of anglec of rotation θ radius of turn R1 is minimum or when being zero is set as 0 °, the value of anglec of rotation θ by radius of turn R1 when maximum be set as 180 °, then in the range of θ is from 0 ° to 180 °, rotation half Footpath R1 increases with the increase of anglec of rotation θ.

Now, in conventional buncher, the pitch radius of the pitch radius of little gear and the internal gear of cam part Be fixed while it is unrelated with anglec of rotation θ, therefore, radius of turn R1 relative to anglec of rotation θ rate of change when θ is larger ratio exist θ compared with it is little when it is little.Therefore, gear ratio is directed to the response of the drive volume of regulation driving source in the little low speed side of radius of turn R1 (UD sides) is relatively higher, in the big high-speed side of radius of turn R1 (OD sides) than relatively low.

On the other hand, in the present invention, pitch radius rw2 of the internal gear of pitch radius rw1 of little gear and cam part Position, i.e. radius of turn R1 that is meshed corresponding to these gears and change, and increase with the increase of radius of turn R1 Greatly.

Thereby, it is possible to make radius of turn R1 further increase in OD sides relative to the rate of change of anglec of rotation θ, and in UD sides Further reduce.Therefore, it is possible to realize the reduction of the speed of action of the regulation driving source in OD sides and the sound to speed change instruction The raising of answering property, and the load of the regulation driving source of UD sides can be reduced.

In the present invention, the increase of the pitch radius corresponding with the increase of the radius of turn can be gradual 's.Thus, radius of turn R1 is smoothened relative to the variation characteristic of anglec of rotation θ.

Description of the drawings

Fig. 1 is the explanatory diagram of an embodiment of the buncher that the present invention is illustrated with partial cross section.

Fig. 2 is the explanatory diagram of the toggle for illustrating present embodiment.

Fig. 3 A to Fig. 3 D are the explanatory diagrams of the change of the radius of turn for illustrating present embodiment.Fig. 3 A show radius of turn Maximum state, Fig. 3 B show radius of turn be in state, Fig. 3 C show the little state of radius of turn, and Fig. 3 D show Radius of turn is 0 state.

Fig. 4 A to Fig. 4 C are the swing models of the swing connecting bar corresponding with the change of radius of turn for illustrating present embodiment The explanatory diagram of the change enclosed.Fig. 4 A show the hunting range in the state of radius of turn R1 maximum, and Fig. 4 B show rotation half Footpath be in the state of hunting range, Fig. 4 C show radius of turn it is little in the state of hunting range.

Fig. 5 A and Fig. 5 B are the pitch circles half of the little gear in the radius of turn governor motion for illustrate present embodiment and internal tooth The explanatory diagram in footpath.The state that little gear is engaged with internal tooth when Fig. 5 A show that radius of turn R1 is 0, Fig. 5 B show radius of turn The state that little gear is engaged with internal tooth when R1 is maximum.

Fig. 6 A to Fig. 6 E are that anglec of rotation θ of rotating disk in the radius of turn governor motion for illustrate present embodiment often changes The explanatory diagram of the change at the position that little gear is engaged with internal tooth when 45 °.State when Fig. 6 A show that anglec of rotation θ is 0 °, figure State when 6B shows that anglec of rotation θ is 45 °, state when Fig. 6 C show that anglec of rotation θ is 90 °, Fig. 6 D show rotation State when gyration θ is 135 °, state when Fig. 6 E show that anglec of rotation θ is 180 °.

Fig. 7 is the rotation corresponding with anglec of rotation θ of rotating disk of the radius of turn governor motion for illustrating present embodiment Turn the chart of the variation characteristic of radius R1.

Fig. 8 A and Fig. 8 B be little gear in the radius of turn governor motion for illustrate another embodiment of the invention with The explanatory diagram of the pitch radius of internal tooth.The state that little gear is engaged with internal tooth when Fig. 8 A show that radius of turn R1 is 0, Fig. 8 B show The state that little gear is engaged with internal tooth when radius of turn R1 is maximum is gone out.

Label declaration

1：Buncher；2：Input shaft；3：Output shaft；4：Radius of turn governor motion；5：Cam disc (cam part)；6、 76：Rotating disk (rotating part)；6b：Internal tooth (internal gear)；6c、70c、75c、76c：Pitch circle；14：Regulation driving source；15：Connection Bar；17：One-way clutch (single direction rotation prevents mechanism)；18：Swing connecting bar；20：Toggle (four-bar mechanism)；70、 75：Little gear；P1：Center of rotation axis；P2：The central point of cam disc；P3：The central point of rotating disk；R1：Offset (rotation Radius)；Ra：The distance between center point P 1 and P2；Rb：The distance between center point P 2 and P3；Rw1, rw2, rwa~rwh：Section Radius of circle.

Specific embodiment

Referring to figs. 1 to Fig. 7, an embodiment of the buncher of the four-bar mechanism type of the present invention is illustrated. The buncher of present embodiment is can to make gear ratio h (rotary speed of the rotary speed/output shaft of h=input shafts) be Infinitely great (∞) is so that the rotary speed of output shaft is variator, i.e. so-called IVT (the Infinity Variable of " 0 " Transmission：Limitless speed variator) one kind.

With reference to Fig. 1, the buncher 1 of four-bar mechanism type possesses：Input shaft end 2a, from electromotors such as internal combustion engines or The driving force of main driving source ENG such as motor is passed to input shaft end 2a, so as to input shaft end 2a to rotate in Rotate centered on heart axis P1；Output shaft 3, its be configured to it is parallel with center of rotation axis P1, and via eliminating the difference of diagram Rotary power is transferred to moving gear the driving wheel (omitting diagram) of vehicle；And 6 radius of turn governor motions 4, their quilts It is located in center of rotation axis P1.Also, power transmission shaft can also be arranged to replace differential gearing.

See figures.1.and.2, each radius of turn governor motion 4 possesses as the cam disc 5 of cam part and as rotating part Rotating disk 6.Cam disc 5 is discoid, and cam disc 5 is eccentric from center of rotation axis P1, also, cam disc 5 is with relative to 1 rotation Turn radius governor motion 4 and be arranged at each radius of turn governor motion 4 as in the way of 1 group by 2.In addition, arranging on cam disc 5 There is the through hole 5a of the direction insertion along center of rotation axis P1.In addition, clearance opening 5b is provided with cam disc 5, the breach Hole 5b relative to center of rotation axis P1 to eccentric direction opening in opposite direction, and make cam disc 5 outer peripheral face and Constitute the inner peripheral surface connection of through hole 5a.

Per 1 group of cam disc 5 with phase place differ respectively 60 degree so as to 6 groups of cam discs 5 around center of rotation axis P1 circumference The mode of one week is configured.

Cam disc 5 is integrally formed one-piece type convex so as to constitute with the cam disc 5 of adjacent radius of turn governor motion 4 Wheel portion 5c.One-piece type cam part 5c can be formed by being integrally formed, or 2 cam parts can also be welded with It is integrally formed.2 of each radius of turn governor motion 4 mutually fix for 1 group of cam disc 5 each other by bolt (omitting diagram). Most forming as one with input shaft end 2a by the cam disc 5 of main driving source in center of rotation axis P1.So, by being input into Shaft end 2a and multiple cam discs 5 constitute the input shaft 2 of the input unit as the present invention.

Input shaft 2 possesses and inserts hole 60, and this inserts hole 60 and is constituted by making the through hole 5a of cam disc 5 be connected.Thus, Input shaft 2 constitute based on driving source ENG opposition side one end open and the other end closing hollow shaft shape.Positioned at main driving The cam disc 5 of the other end of source forms as one with input shaft end 2a.As making the cam disc 5 and input shaft end 2a shapes The method being integrally formed, can be using being integrally formed, alternatively, it is also possible to cam disc 5 and input shaft end 2a are welded together And realize integration.

In addition, being cased with possessing the collecting for housing cam disc 5 so that eccentric state is rotatably outer per 1 group of cam disc 5 The discoid rotating disk 6 of hole 6a.

As shown in Fig. 2 rotating disk 6 is eccentric relative to cam disc 5 in the following manner：If the central point of cam disc 5 is P2, if The central point of rotating disk 6 is the distance between P3, center of rotation axis P1 and center point P 2 Ra and center point P 2 and center point P 3 The distance between Rb it is equal.

The position between 1 group of cam disc 5 of the accepting hole 6a of rotating disk 6 is provided with internal tooth 6b.

Inserting in hole 60 in input shaft 2, is configured in the way of rotating against freely with the input shaft 2 with cam disc 5 There is little gear 70, the little gear 70 is concentric with center of rotation axis P1 and positioned at the corresponding position of internal tooth 6b with rotating disk 6.It is little Gear 70 forms as one with pinion shaft 72.Also, little gear 70 can be constituted with the split of pinion shaft 72, and by flower Bond is closed and links up little gear 70 with pinion shaft 72.In the present embodiment, simply referred to as little gear 70 when, be defined as bag Include pinion shaft 72.

Little gear 70 is engaged via clearance opening 5b of cam disc 5 with the internal tooth 6b of rotating disk 6.Pinion bearing 74 is located at Pinion shaft 72 is arranged between adjacent little gear 70.Pinion shaft 72 is via the supporting input shaft 2 of pinion bearing 74. In addition, the differential attachment 8 being made up of planetary gears etc. is connected with pinion shaft 72.Adjust with the driving force quilt of driving source 14 Little gear 70 is transferred to via differential attachment 8.

In the case of rotary speed identical of the rotary speed of the input shaft 2 of cam disc 5 with pinion shaft 72 is fixed with, Rotating disk 6 integratedly rotates together with cam disc 5.Between the rotary speed of input shaft 2 and the rotary speed of pinion shaft 72 In the case of there is difference, rotating disk 6 is rotated centered on the center point P 2 of cam disc 5 in the periphery of cam disc 5.

Due to rotating disk 6 relative to cam disc 5 with apart from Ra and eccentric apart from Rb equal mode, it is thus possible to enough make The center point P 3 of rotating disk 6 is located at on center of rotation axis P1 identical axis, makes center of rotation axis P1 and center point P 3 The distance between, i.e. offset R1 be " 0 ".

Connecting rod 15 possesses the input side annulus 15a in big footpath (side of an input shaft 2) end, and (defeated at another The side of shaft 3) end possesses the outlet side annulus 15b of the diameter path less than the diameter of input side annulus 15a, the connecting rod 15 input side annulus 15a is enclosed within the periphery of rotating disk 6 via connecting rod bearing 16 is rotatably outer, wherein, it is described Connecting rod bearing 16 with the ball bearing of 2 as 1 group by being constituted, and 2 ball bearings are axially aligned.On output shaft 3, via list 6 swing connecting bars 18 are accordingly provided with to clutch 17 and connecting rod 15.

One-way clutch 17 is arranged between swing connecting bar 18 and output shaft 3, in swing connecting bar 18 relative to output shaft 3 Will to side rotate against when, swing connecting bar 18 is fixed on output shaft 3 (stationary state) by one-way clutch 17, and is being swung Connecting rod 18 relative to output shaft 3 will to opposite side rotate against when, one-way clutch 17 makes swing connecting bar 18 relative to output shaft 3 Idle running (idling conditions).

Swing connecting bar 18 is formed as ring-type, is provided with thereunder and the outlet side annulus 15b links of connecting rod 15 Swing end 18a.A pair of tab 18b are provided with end 18a is swung, the pair of tab 18b is clamping in the axial direction output The mode of side annulus 15b is projected.It is provided through on a pair of tab 18b corresponding with the internal diameter of outlet side annulus 15b Patchhole 18c.The connecting pin 19 as swinging axle is inserted with patchhole 18c and outlet side annulus 15b.Thus, even Extension bar 15 and swing connecting bar 18 are attached at together.

Fig. 3 A to Fig. 3 D show the state for making the offset R1 (radius of turn) of radius of turn governor motion 4 change Under pinion shaft 72 and rotating disk 6 between position relationship.Fig. 3 A show the state for making offset R1 " maximum ", little gear Axle 72 chord rotating disk 6 is in arranges the center point P 3 of center of rotation axis P1, the center point P 2 of cam disc 5 and rotating disk 6 Position in alignment.Gear ratio h now is minimum.

Fig. 3 B show make offset R1 be it is less than Fig. 3 A " in " state, Fig. 3 C show makes offset R1 be than figure The state of 3B less " little ".In figure 3b, gear ratio h be gear ratio h than Fig. 3 A it is big " in ", in fig. 3 c, gear ratio h It is gear ratio h than Fig. 3 B big " big ".Fig. 3 D show the state for making offset R1 be " 0 ", center of rotation axis P1 and rotation The center point P 3 of rotating disk 6 is located at concentric position.Gear ratio h now is infinitely great (∞).The infinitely variable speeds of present embodiment Device 1 changes offset R1 using radius of turn governor motion 4, so that the radius of turn of radius of turn governor motion 4 can be certainly As adjusted.

Fig. 4 A to Fig. 4 C show make radius of turn governor motion 4 offset R1 change when swing connecting bar 18 swing The change of scope.The hunting range of the swing connecting bar 18 when Fig. 4 A show that offset R1 is maximum, Fig. 4 B show offset The hunting range of the swing connecting bar 18 when R1 is middle, Fig. 4 C show the hunting range of the swing connecting bar 18 of offset R1 hours. Understand that, as offset R1 diminishes, hunting range narrows according to Fig. 4 A to Fig. 4 C.Also, when offset R1 is changed into " 0 ", pendulum Dynamic connecting rod 18 does not swing.

In the present embodiment, crank connecting link is constituted by radius of turn governor motion 4, connecting rod 15 and swing connecting bar 18 Mechanism 20 (four-bar mechanism).Also, the rotary motion of input shaft 2 is converted to into swing connecting bar 18 using toggle 20 Oscillating motion.The buncher 1 of present embodiment possesses 6 toggles 20 altogether.If not being in offset R1 Rotate input shaft 2 when " 0 " and pinion shaft 72 is rotated with same speed with input shaft 2, then 60 degree every time of each connecting rod 15 Ground changes phase place, while alternately promoting swinging end to output shaft 3 between input shaft 2 and output shaft 3 based on offset R1 Portion 18a and enter to swing the action of end 18a to the layback of input shaft 2 and repeat the alternating movement, so that swing connecting bar 18 swings.

The outlet side annulus 15b of connecting rod 15 links with swing connecting bar 18, and the swing connecting bar 18 is via one-way clutch 17 are arranged at output shaft 3, therefore, if swing connecting bar 18 is connected the push-and-pull of bar 15 and swings, only swing connecting bar 18 to When any one side of press direction side or draw direction side rotates, output shaft 3 just rotates, and rotates to opposite side in swing connecting bar 18 When, the power of the oscillating motion of swing connecting bar 18 is not passed to output shaft 3, and swing connecting bar 18 dallies.Each radius of turn is adjusted Mechanism 4 is configured by phase place in the way of 60 degree, therefore, output shaft 3 is rotated successively by each radius of turn governor motion 4.

In addition, the buncher of present embodiment possesses the control unit (omitting diagram) of control and regulation driving source 14. Control unit is the electronic unit being made up of CPU or memorizer etc., and the control journey for keeping in memory is performed by using CPU Sequence, and control and regulation driving source 14 is played, so as to adjust the effect of the offset R1 of radius of turn governor motion 4.

Fig. 5 A and Fig. 5 B show pitch radius rw1 of the little gear 70 in radius of turn governor motion 4 and rotating disk 6 Pitch radius rw2 of internal tooth 6b.In fig. 5, the little gear in GN (geared neutral) states of the offset R1 for " 0 " is shown Pitch radius rwa of the little gear 70 at 70 positions engaged with internal tooth 6b and pitch radius rwb of internal tooth 6b.

In figure 5b, show that little gear 70 is engaged with internal tooth 6b in offset R1 maximum OD (overdrive) states Position little gear 70 pitch radius rwc and pitch radius rwd of internal tooth 6b.

As fig. 5 a and fig. 5b, internal tooth 6b is arranged on the scope that offset R1 is changed to required for " maximum " from " 0 " It is interior.Scope of the scope corresponding to the central angle of 180 ° centered on the center point P 2 of cam disc 5 (Fig. 2 references).Little gear 70 are configured to for the internal tooth 6b of the scope is with less than the scope correspondence of a circle (360 °).

The part that pitch radius rw1 of the pitch circle 70c of little gear 70 is engaged when being " 0 " from the offset R1 of Fig. 5 A is to Fig. 5 B Offset R1 the part engaged gradually increase when being " maximum ".It is corresponding, pitch radius rw2 of the pitch circle 6c of internal tooth 6b The another side that the offset R1 of the side to Fig. 5 B engaged when from the offset R1 of Fig. 5 A being " 0 " is engaged when being " maximum " by It is cumulative big.

That is, pitch radius rw1 of the little gear 70 at intermeshing position and pitch radius rw2 of internal tooth 6b are corresponded to Radius of turn R1 of toggle 20 is offset R1 and changes.Also, pitch radius rw1 and rw2 are in offset It is bigger than offset R1 hours when R1 is big, and gradually increase corresponding to the increase of offset R1.

In Fig. 6 A to Fig. 6 E, change anglec of rotation θ of the rotating disk 6 relative to cam disc 5, while illustrating that radius of turn is adjusted Pitch radius rw1 at the position that the little gear 70 in section mechanism 4 is meshed with internal tooth 6b and the change of rw2.In Fig. 6 A~figure In 6E, respectively illustrate anglec of rotation θ be 0 °, 45 °, 90 °, 135 °, 180 ° when the position that is meshed with internal tooth 6b of little gear 70 Pitch radius rw1 and rw2 at place.

Carry out when i.e., in fig. 6, for geared neutral (GN) that offset R1 is " 0 " (gear ratio is infinity) Diagram.It is shown during in fig. 6b, big for gear ratio low speed rotation (UD).In figure 6 c, for speed change It is shown than the situation of the high-speed drive (TD) of little (vehicle can be travelled at full throttle).In Fig. 6 E, for speed change It is shown than the situation of minimum overdrive (OD).

As described above, when offset R1 changes, rotating disk 6 rotates around little gear 70, and make little gear 70 (defeated Enter axle 2) the distance between the center point P 2 of center of rotation axis P1 and cam disc 5 Ra and center point P 2 and rotating disk 6 in The distance between heart point P3 Rb equal (with reference to Fig. 2).Now, with regard to anglec of rotation θ, if value when being " 0 " by offset R1 Used as 0 °, then when offset R1 is " maximum ", anglec of rotation θ is 180 °.

Also, due to fixing apart from Ra, therefore, in the case where offset R1 is changed to " maximum " from " 0 ", such as Fig. 6 A~ Fig. 6 E so, the amount identical amount that pitch radius rw2 of internal tooth 6b is also gradually increased with pitch radius rw1 with little gear 70 by It is cumulative to add.

In the figure 7, anglec of rotation θ when being " 0 " by offset R1 be set as 0 ° offset R1 is shown with rotating disk 6 The corresponding variation characteristic of anglec of rotation θ.In the figure 7, the feelings of the present embodiment that pitch radius rw1 and rw2 gradually increase Variation characteristic under condition is represented with diagram curve 73 (solid line).In addition, in order to be compared, pitch radius rw1 and rw2 do not change It is conventional in the case of variation characteristic represented with diagram curve 71 (dotted line).

As shown in diagram curve 71, in the case of in the past, pitch radius rw1 and rw2 of little gear and internal gear are fixed And it is unrelated with anglec of rotation θ, therefore, the rate of change corresponding with anglec of rotation θ of the offset R1 ratio when anglec of rotation θ is less It is larger and smaller when anglec of rotation θ is larger.Therefore, gear ratio is relative to the regulation response of the drive volume of driving source 14 Property it is relatively higher in the less low speed sides of offset R1 (UD sides), in offset R1 larger high-speed side (OD sides) than relatively low.

Therefore, in the case where any measure is not taken, in the gear ratio of OD (overdrive) side, it is impossible to for low Gear shift etc. obtains the good response of gear ratio.In order to obtain good response, need with offset R1 relative to The rate of change of anglec of rotation θ is little accordingly with higher speed driving pinion 70, and the load for making regulation driving source 14 increases Greatly.

In addition, in the gear ratio of UD (low speed rotation) side, compared to the response of transmission ratio, more requiring to keep high Driving torque.It is therefore preferable that making the change of the offset R1 corresponding with the change of anglec of rotation θ gentle.In this case, Also the load of regulation driving source 14 can be reduced.But, with the requirement conversely, as described above, offset R1 is relative to rotation The variation characteristic of angle, θ compares drastically in UD (low speed rotation) side.

On the other hand, according to present embodiment, as shown in diagram curve 73, pitch radius rw1 of little gear 70 and rotation The i.e. offset R1 in position that pitch radius rw2 of the internal tooth 6b of disk 6 is meshed with these gears accordingly changes, and in bias Amount R1 is big, and when ratio is big in offset R1 hours.

Thus, offset R1 becomes much larger relative to the change of anglec of rotation θ in OD sides, becomes less in UD sides.Thus, Offset R1 becomes more rectilinearity relative to the variation characteristic of anglec of rotation θ.Therefore, it is possible to realize that the regulation of OD sides drives The reduction of the speed of action in source 14 and the raising of the response that speed change is indicated, and the regulation driving of UD sides can be reduced The load in source 14.

Fig. 8 A and Fig. 8 B show the radius of turn governor motion of the buncher of another embodiment of the invention In little gear 75 pitch radius rw1 and rotating disk 76 internal tooth 76b pitch radius rw2.In fig. 8 a, show The section of the little gear 75 at the position that little gear 75 is engaged with internal tooth 76b when offset R1 is geared neutral (GN) state of " 0 " Pitch radius rwf of radius of circle rwe and internal tooth 76b.

In the fig. 8b, little gear 75 and internal tooth 76b when offset R1 is maximum overdrive (OD) state are shown Pitch radius rwg of the little gear 75 at the position of engagement and pitch radius rwh of internal tooth 76b.

As shown in Figure 8 A and 8 B, internal tooth 76b is arranged on the scope that offset R1 is changed to required for " maximum " from " 0 " It is interior.Scope of the scope corresponding to the central angle of 180 ° centered on the center point P 2 of cam disc 5 (Fig. 2 references).Little gear 75 are configured to corresponding with the scope of close 1 circle (360 °) for the internal tooth 76b of the scope.

The value of pitch radius rw1 of the pitch circle 75c of little gear 75, in the corresponding internal tooth 76b of central angle with above-mentioned 180 ° In the range of the part corresponding with the scope of half degree that the part engaged from Fig. 8 A starts in for rwe, with arrive It is rwg in the corresponding part of second half scope till the part engaged up in Fig. 8 B.That is, pitch circle 75c is configured to be saved Radius of circle for rwe part and pitch radius for rwg part substantially decile.It is corresponding, the pitch circle 76c of internal tooth 76b By the part substantially decile that pitch radius rw2 is rwf and pitch radius rw2 is rwh.

Even if in this case, the section of pitch radius rw1 of the little gear 75 at intermeshing position and internal tooth 76b Radius of circle rw2 also corresponds to offset R1 and changes, and big in offset R1 hours in the big when ratios of offset R1.But, its Change turns to 2 grades.

In this case, it is also possible to realize the regulation of OD sides with the reduction of the speed of action of driving source 14 and to speed change The raising of the response of instruction, and the load of the regulation with driving source 14 of UD sides can be reduced.In addition, little gear 75 and internal tooth Pitch radius rw1 and rw2 of 76b is changed in the way of 2 grades, therefore, it is possible to form little gear 75 and internal tooth with comparalive ease 76b。

More than, embodiments of the present invention are illustrated, but the present invention is not limited to embodiment.For example, exist In above-mentioned embodiment, following structures are illustrated：Input shaft 2 is constituted by input shaft end 2a and multiple cam discs 5, Input shaft 2 possess by make the through hole 5a of cam disc 5 connect and constitute insert hole 60.But, the input shaft of the present invention is simultaneously Not limited to this.

For example, as input shaft component parts, or：The shape for having that one end open and the other end are closed is set Insert the hollow input shaft core in hole, and form through hole must be bigger than present embodiment, so as to by input shaft Core is inserted in discoid cam disc, each cam disc is combined with the outer peripheral face spline of input shaft core, so as to constitute tool The input shaft of standby multiple cam discs.

In this case, clearance opening is set corresponding to the clearance opening of cam disc in hollow input shaft core.Also, insert Enter to the little gear in input shaft core via the clearance opening of input shaft core and the clearance opening of cam disc with rotating disk in Tooth is engaged.

In addition, in the above-described embodiment, mechanism is prevented as single direction rotation, employ one-way clutch 17, but this The single direction rotation of invention prevents mechanism from being not limited to this, for example, it is also possible to be bidirectional clutch, consisting of being capable of free switching Torque can be transferred to the direction of rotation relative to output shaft of the swing connecting bar of output shaft from swing connecting bar.

In addition, anglec of rotation θ of the rotating disk 6 when offset R1 is maximum can not be 180 °.For example, merely with to rotation In the case of gear ratio when gyration θ is 150 °, when maximum offset R1 can be set as into anglec of rotation θ is 150 ° Value.

Furthermore it is possible to make input unit be little gear, the driving force for making main driving source is transferred to little gear, drives regulation The driving force in source is transferred to cam disc.

Claims (2)

1. a kind of buncher, it is characterised in that possess：

Input unit, the driving force for carrying out autonomous driving source is passed to the input unit；

Output shaft, it is configured to parallel with the center of rotation axis of the input unit；

Toggle, it has by e axle supporting in the swing connecting bar of the output shaft, by the rotary motion of the input unit Be converted to the oscillating motion of the swing connecting bar；And

Single direction rotation prevents mechanism, and it will when the swing connecting bar will be rotated against relative to the output shaft to a direction The swing connecting bar is fixed on the output shaft, and when the swing connecting bar will be rotated against relative to the output shaft to another direction The swing connecting bar is made relative to the output shaft idle running,

The toggle possesses：The radius of turn governor motion of radius of turn can freely be adjusted；And link described The connecting rod of radius of turn governor motion and the swing connecting bar,

The radius of turn governor motion possesses：

Cam part, it is with relative to the eccentric state rotation of the center of rotation axis；

Little gear, it can rotate with one heart with the center of rotation axis relative to the cam part；And

Rotating part, it is rotated freely with being supported to by the cam part relative to the eccentric state of the cam part, and with institute The internal gear of little gear engagement is stated, the rotating part rotatably links with the connecting rod,

Both pitch radius at the little gear and the intermeshing position of the internal gear correspond to the radius of turn Increase and increase, make the radius of turn big in the radius of turn relative to the rate of change of the anglec of rotation of the rotating part High-speed side increase, reduce in the little low speed side of the radius of turn.

2. buncher according to claim 1, it is characterised in that

The increase of the pitch radius corresponding with the increase of the radius of turn is gradual.