CN105090444A

CN105090444A - Continuously variable transmission

Info

Publication number: CN105090444A
Application number: CN201510229736.0A
Authority: CN
Inventors: 高杉将司
Original assignee: Honda Motor Co Ltd
Current assignee: Honda Motor Co Ltd
Priority date: 2014-05-07
Filing date: 2015-05-07
Publication date: 2015-11-25
Anticipated expiration: 2035-05-07
Also published as: CN105090444B; JP2015214991A; JP6180993B2

Abstract

The invention provides a continuously variable transmission which can suppress the expanding of the gap between a bearing ring of a bearing which supports an input shaft and an output shaft and a rolling element, and can improve a deteriorated structure of an NVH. The continuously variable transmission has an input shaft, an output shaft, a crank train, a one-way rotary stop mechanism and a transmission housing. The transmission housing has a side wall portion which supports the two end portions of the input shaft by means of an input bearing and supports the two end portions of the output shaft by means of an output bearing. The bearing ring is arranged on the side wall portion for supporting the input bearing and the output bearing, with respect to the input bearing and a center position upwardly the shaft of the rolling element of the output bearing, deviates towards the shaft end sides of near sides of the input shaft and the output shaft which are respectively supported by the input bearing and the output bearing

Description

Stepless speed variator

Technical field

The present invention relates to the vibration attenuation structure of the stepless speed variator of four joint linkage mechanism types.

Background technique

Such as, four following joint linkage mechanism type stepless speed variators are described in Japanese Unexamined Patent Publication 2012-1048 publication, the rotation of the input shaft be connected with motor is converted to the to-and-fro motion of connecting rod by it, by overrunning clutch, the to-and-fro motion of connecting rod is converted to the rotary motion of output shaft.

In above-mentioned Japanese Unexamined Patent Publication 2012-1048 publication, the two end part of input shaft and output shaft are supported in the sidewall portion of case of transmission with the mode axle that can rotate freely via pair of bearings.The loading direction that the lasso (outer ring and inner ring) of this pair of bearings and the gap of rolling element (spheroid) can input according to input shaft when transmitting from moment of torsion and output shaft and size and change, namely by the expansion of the bearing play of loading direction opposition side with reduce and make lasso and rolling element repeat to be separated and to contact, thus the impact sound of rolling element and lasso can be produced, become the deterioration reason of NVH (noise, vibration and sound vibration roughness).

Summary of the invention

The present invention completes in view of above-mentioned problem, its object is to realize a kind ofly can suppress the expansion in the gap between the lasso of the bearing supporting input shaft and output shaft and rolling element and improve the structure of the deterioration of NVH.

In order to solve above-mentioned problem, reach object, the 1st form of the present invention is a kind of stepless speed variator 1, and it has: input shaft 2, and it is by from traveling driving source input queued switches power, output shaft 3, itself and described input shaft 2 configure abreast, connecting rod 20, it has the fork 18 linked with described output shaft 3, the oscillating motion of described fork 18 will be converted to by the rotary motion of the driving force input part 4 ~ 7 of described input shaft 2 rotary actuation, when described driving force input part 4 rotates 1 circle, described fork 18 carries out 1 reciprocal oscillating motion, single direction rotation stops mechanism 17, and described fork 18 is fixed on described output shaft 3 when described fork 18 is for swinging aside by it, when described fork 18 is for swinging to opposite side, described fork 18 is dallied relative to described output shaft 3, and case of transmission 100, it supports described input shaft 2 and described output shaft 3 in the mode that can rotate freely, and accommodates described input shaft 2, described output shaft 3, described connecting rod 20 and described single direction rotation stop mechanism 17, and described case of transmission 100 has sidewall portion 101, 102, this sidewall portion 101, 102 by means of input shaft bearing 40A, 40B supports the two end part of described input shaft 2, and by means of output bearing 50A, 50B supports the two end part of described output shaft 3, described sidewall portion 101, the described input shaft bearing 40A of support on 102, 40B and described output bearing 50A, the lasso 40A1 of 50B, 40B1, 50A1, the position of 50B1 is relative to described input shaft bearing 40A, 40B and described output bearing 50A, the rolling element 40A2 of 50B, 40B2, 50A2, the central position 101A axially of 50B2, 102A, to by described input shaft bearing 40A, 40B and described output bearing 50A, the shaft end side skew of the nearside of the described input shaft 2 that 50B supports respectively and described output shaft 3.

In addition, 2nd form of the present invention is on the basis of above-mentioned 1st form, described sidewall portion 101,102 has: input area 101B, 102B, it is positioned at than the side of line L1 away from described output shaft 3, wherein this line L1 is by central position 101A, 102A axially of described input shaft bearing 40A, 40B, and loading direction when being maximum with the load F1, the F4 that act on described input shaft bearing 40A, 40B from described input shaft 2 is vertical, output area 101C, 102C, it is positioned at than the side of line L2 away from described input shaft 2, wherein this line L2 is by central position 101A, 102A axially of described output bearing 50A, 50B, and with the load F1 ', the F4 ' that act on from described output shaft 3 on described output bearing 50A, 50B for loading direction time maximum is vertical, and zone line 101D, 102D, it is clipped between described input area and described output area, described sidewall portion 101, 102 are configured to, when described single direction rotation stop mechanism 17 be when described fork 18 by from the thruster of described input shaft 2 to output shaft 3 side time described fork 18 is fixed mechanism, described input area 101B, 102B and described output area 101C, the rigidity of 102C is higher than described zone line 101D, the rigidity of 102D, when described single direction rotation stop mechanism 17 be when described fork 18 by from described output shaft 3 layback to mechanism during described input shaft 2 side, described fork 18 fixed, described input area 101B, 102B and described output area 101C, the rigidity of 102C is lower than described zone line 101D, the rigidity of 102D.

According to the present invention, can realize a kind ofly can suppressing the expansion in the gap between the lasso of the bearing supporting input shaft and output shaft and rolling element and improving the structure of the deterioration of NVH.

Particularly, according to the 1st form of the present invention, suppress the expansion in the gap of bearing by means of the moment of flexure resulted from axle head, and rely on toppling over of bearing and make to suppress the masterpiece of flexure for axle head, therefore can not damage the durability of axis body, reliability and moment of torsion transmission efficiency, can NVH be improved.

In addition, according to the 2nd form of the present invention, be easy to bend from the region of opposition side of the loading direction of input shaft and output shaft input and lasso reacting axial loads to bearing, therefore, it is possible to contribute to the effect of the expansion in the gap suppressed between rolling element and lasso, the improvement of NVH can be realized.

Description according to a preferred embodiment of the present invention, other feature and advantage of the present invention are all apparent to those skilled in the art.In the description, an example of the present invention is shown with reference to accompanying drawing.But such example, not for exhaustive various embodiment of the present invention, therefore, should determine scope of the present invention with reference to the claims after specification.

Accompanying drawing explanation

Fig. 1 is the sectional view of the structure of the stepless speed variator representing present embodiment.

Fig. 2 is the figure of the offset controlling mechanism of stepless speed variator from end on observation Fig. 1, connecting rod and fork.

Fig. 3 A-3D is the figure of the change of the offset that the offset controlling mechanism of the stepless speed variator representing Fig. 1 brings.

Fig. 4 A-4C is the figure of the relation of the pendulum angle scope of the change of offset and the oscillating motion of fork representing that the offset controlling mechanism of present embodiment brings.

Fig. 5 is the figure of the input shaft of the stepless speed variator that present embodiment is described and the bearing support structure of output shaft.

Fig. 6 A-6C represents that the connecting rod of present embodiment carries out the figure of power relation when moment of torsion transmits by pushing mode.

Fig. 7 A-7C represents that the connecting rod of present embodiment carries out the figure of power relation when moment of torsion transmits by tractive mode.

Fig. 8 A-8B is the External view in the sidewall portion of the case of transmission shown in Fig. 5.

Fig. 9 is that the sidewall portion of the case of transmission that present embodiment is described is to the expansion inhibitory action in the gap of bearing and the inhibiting figure of flexure to input shaft and output shaft.

Label declaration

1: stepless speed variator, 2: input shaft, 3: output shaft, 4: offset controlling mechanism, 5: cam disk, 6: eccentric disc, 6a: reception hole, 6b: internal tooth, 7: pinion shaft, 7a: external tooth, 7b: pinion bearing, 14: offset adjustment driving source, 14a: running shaft, 15: connecting rod, 15a: large footpath annulus, 15b: path annulus, 16: connecting rod bearing, 17: overrunning clutch, 18: fork, 20: connecting rod, 40A: the 1 input shaft bearing, 40B: the 2 input shaft bearing, 50A: the 1 exports bearing, 50B: the 2 exports bearing, 100: case of transmission, 101: the 1 sidewall portions, 102: the 2 sidewall portions.

Embodiment

Below, the mode of execution that present invention will be described in detail with reference to the accompanying.In addition, the mode of execution below illustrated is the example as realization rate of the present invention, and the present invention can be applied to the structure after modifying to following mode of execution in the scope not departing from its purport or being out of shape.In addition, stepless speed variator of the present invention can also be applied to other purposes beyond automobile, and this is self-explantory.

First the structure > of < stepless speed variator, sees figures.1.and.2, and the structure of the stepless speed variator of present embodiment is described.

The stepless speed variator 1 of present embodiment to make gear ratio i (rotational speed of the rotational speed/output shaft of i=input shaft) for infinitely great (∞) and make the rotational speed of output shaft be the one of speed changer, the i.e. so-called IVT (InfinityVariableTransmission: Limitless speed variator) of " 0 ".

The stepless speed variator 1 of present embodiment has input shaft 2, output shaft 3 and 6 offset controlling mechanisms 4.

Input shaft 2, output shaft 3, offset controlling mechanism 4 are contained in the inside of case of transmission 100.Case of transmission 100 has in the 1st sidewall portion 101 of the axially configured separate of input shaft 2 and output shaft 3 and the 2nd sidewall portion 102.When observing from input shaft 2, the 1st sidewall portion 101 is by the upstream side from motor input queued switches power, and the 2nd sidewall portion 102 is downstream side.Otherwise if observed from output shaft 3, then the 1st sidewall portion 101 is by the downstream side from motor output drive strength, and the 2nd sidewall portion 102 is upstream side.

One end of the upstream side of input shaft 2 is supported in the 1st sidewall portion 101 via the 1st input shaft bearing 40A in the mode that can rotate freely, and the other end in the downstream side of input shaft 2 is supported in the 2nd sidewall portion 102 in the mode that can rotate freely via the 2nd input shaft bearing 40B.Input shaft 2 is made up of the parts of hollow, and it accepts the driving force travelling driving source from motor or motor etc., is driven in rotation centered by rotating center axis P1.

In addition, one end in the downstream side of output shaft 3 exports bearing 50A via the 1st and is supported in the 1st sidewall portion 101 in the mode that can rotate freely, and the other end of the upstream side of output shaft 3 exports bearing 50B via the 2nd and is supported in the 2nd sidewall portion 102 in the mode that can rotate freely.Output shaft 3 and input shaft 2 are configured at the position be separated in the horizontal direction with input shaft 2 abreast, via the axletree transmission of drive force to automobile such as forward-reverse switching mechanism and differential gear.

Offset controlling mechanism 4 is driving force input part respectively, is set to rotate centered by the rotating center axis P1 of input shaft 2, has the cam disk 5 as cam part, the eccentric disc 6 as eccentric part and pinion shaft 7.

Cam disk 5 is disc-shape, with eccentric and be arranged at input shaft 22 by 1 group with the mode that input shaft 2 rotates integrally from the rotating center axis P1 of input shaft 2.Each group of cam disk 5 is set to phase shifting 60 ° respectively, is configured to pass 6 groups of cam disks 5 and rounds in the circumference of input shaft 2.

Eccentric disc 6 is disc-shape, is being provided with reception hole 6a from the position of its center P3 bias, to clip the mode of this reception hole 6a, 1 group of cam disk 5 is supported for and can be rotated.

The center of the reception hole 6a of eccentric disc 6 is formed, and makes the distance Ra of the center P2 (center of reception hole 6a) from the rotating center axis P1 of input shaft 2 to cam disk 5 identical with the distance Rb of the center P3 from the center P2 of cam disk 5 to eccentric disc 6.In addition, the inner peripheral surface clamped by 1 group of cam disk 5 of the reception hole 6a of eccentric disc 6 is formed with internal tooth 6b.

Pinion shaft 7 and input shaft 2 are configured in the hollow portion of input shaft 2 with one heart, and are supported in the inner peripheral surface of input shaft 2 in the mode that can relatively rotate via pinion bearing 7b.In addition, the outer circumferential face of pinion shaft 7 is provided with external tooth 7a.And then, pinion shaft 7 is connected with differential attachment 8.

Incision hole 2a is formed between 1 group of cam disk 5 on input shaft 2, inner peripheral surface is communicated with outer circumferential face at the position opposed with the eccentric direction of cam disk 5 by this incision hole 2a, via this incision hole 2a, the external tooth 7a of pinion shaft 7 engages with the internal tooth 6b of the reception hole 6a of eccentric disc 6.

Differential attachment 8 is planetary gears, the 1st gear ring 10 that it has sun gear 9, links with input shaft 2, and the 2nd gear ring 11 that links of pinion shaft 7 and by ladder small gear 12 with can the planet carrier 13 that supports of the mode axle of rotation and revolution, described ladder small gear 12 is made up of the large-diameter portion 12a engaged with sun gear 9 and the 1st gear ring 10 and the minor diameter part 12b that engages with the 2nd gear ring 11.In addition, the running shaft 14a of offset adjustment driving source 14 that the sun gear 9 of differential attachment 8 is formed with the motor driven by pinion shaft 7 links.

And, when making the rotational speed of this offset adjustment driving source 14 identical with the rotational speed of input shaft 2, sun gear 9 rotates with identical speed with the 1st gear ring 10, become sun gear 9, lock state that the 1st gear ring 10, these 4 key elements of the 2nd gear ring 11 and planet carrier 13 cannot carry out relative rotation, the pinion shaft 7 linked with the 2nd gear ring 11 rotates with the speed identical with input shaft 2.

In addition, when making the rotational speed of offset adjustment driving source 14 slower than the rotational speed of input shaft 2, if set the rotating speed of sun gear 9 as the rotating speed of Ns, the 1st gear ring 10 be NR1, the gear ratio (number of teeth of the number of teeth/sun gear 9 of the 1st gear ring 10) of sun gear 9 and the 1st gear ring 10 is j, then the rotating speed of planet carrier 13 is (jNR1+Ns)/(j+1).In addition, if set the gear ratio ((number of teeth of the number of teeth/sun gear 9 of the 2nd gear ring 11) × (number of teeth of the number of teeth/minor diameter part 12b of the large-diameter portion 12a of ladder small gear 12)) of sun gear 9 and the 2nd gear ring 11 as k, then the rotating speed of the 2nd gear ring 11 is { j (k+1) NR1+ (k-j) Ns}/{ k (j+1) }.

Therefore, when make the rotational speed of offset adjustment driving source 14 slower than the rotational speed of input shaft 2 and be fixed with the rotational speed of the input shaft 2 of cam disk 5 identical with the rotational speed of pinion shaft 7, eccentric disc 6 and cam disk 5 rotate integrally.On the other hand, when the rotational speed of input shaft 2 and the rotational speed of pinion shaft 7 there are differences, eccentric disc 6 rotates at the periphery of cam disk 5 centered by the center P2 of cam disk 5.

As shown in Figure 2, eccentric disc 6 is relative to cam disk 5, eccentric in the mode that the distance Ra from P1 to P2 is identical with the distance Rb from P2 to P3.Therefore, it is possible to make the center P3 of eccentric disc 6 be positioned on the line identical with the rotating center axis P1 of input shaft 2, make the distance between the rotating center axis P1 of the input shaft 2 and center P3 of eccentric disc 6, i.e. offset R1 for " 0 ".

The outer edge of eccentric disc 6 is supported with connecting rod 15 in the mode that can rotate.Connecting rod 15 has the large footpath annulus 15a in large footpath an end, have the path annulus 15b of path in another end.The large footpath annulus 15a of connecting rod 15 is supported in the outer edge of eccentric disc 6 via connecting rod bearing 16.

On output shaft 3, the overrunning clutch 17 of mechanism is stoped to be linked with fork 18 via as single direction rotation.Overrunning clutch 17, when for fork 18 being fixed on output shaft 3 to when a sideway swivel centered by the rotating center axis P4 of output shaft 3, makes fork 18 dally relative to output shaft 3 when for rotating to opposite side.

Fork 18 is provided with and swings end 18a, swing end 18a is provided with a pair tab 18b that can be formed in the mode of axially clamping path annulus 15b.A pair tab 18b runs through and is provided with the through hole 18c corresponding with the internal diameter of path annulus 15b.In through hole 18c and path annulus 15b, insert connection pin 19, thus connecting rod 15 and fork 18 are linked up.In addition, fork 18 is provided with annulus 18d.

< connecting rod > then, with reference to Fig. 2 ~ Fig. 4 A-4C, illustrates the connecting rod of the stepless speed variator of present embodiment.

As shown in Figure 2, in the stepless speed variator 1 of present embodiment, offset controlling mechanism 4, connecting rod 15 and fork 18 form connecting rod 20 (four joint linkage mechanisms).

By connecting rod 20, the rotary motion of input shaft 2 is converted to the oscillating motion centered by the rotating center axis P4 of output shaft 3 of fork 18.The stepless speed variator 1 of present embodiment as shown in Figure 1, has total 6 connecting rods 20.

In connecting rod 20, when the offset R1 of offset controlling mechanism 4 is not " 0 ", if make input shaft 2 rotate with identical speed with pinion shaft 7, then each connecting rod 15 staggers the phase place of 60 degree respectively, and alternately repeat to be pushed to output shaft 3 side or to be pulled to input shaft 2 side between input shaft 2 and output shaft 3, fork 18 is swung.

And, overrunning clutch 17 is provided with between fork 18 and output shaft 3, therefore when pushing fork 18, fork 18 is fixed and transmits the moment of torsion produced by the oscillating motion of fork 18 to output shaft 3, output shaft 3 is rotated, when tractive fork 18, fork 18 dallies and can not transmit to output shaft 3 moment of torsion produced by the oscillating motion of fork 18.Stagger the respectively phase place of 60 degree of 6 offset controlling mechanisms 4 configures, and therefore output shaft 3 is by 6 offset controlling mechanism 4 rotary actuations in order.

In addition, in the stepless speed variator 1 of present embodiment, as shown in figs. 3 a-3d, offset controlling mechanism 4 eccentric adjustment amount R1 can be passed through.

Fig. 3 A represents makes offset R1 be the state of " maximum ", and the mode that pinion shaft 7 and eccentric disc 6 are arranged on straight line with the center P2 of rotating center axis P1 and cam disk 5 making the input shaft 2 and center P3 of eccentric disc 6 is located.Gear ratio i is now minimum.Fig. 3 B represent make offset R1 be less than Fig. 3 A " in " state, Fig. 3 C represents makes offset R1 be the state of " little " being less than Fig. 3 B further.About gear ratio i, represent in figure 3b be greater than the gear ratio i of Fig. 3 A " in " state, represent in fig. 3 c and be greater than the state of " greatly " of the gear ratio i of Fig. 3 B.Fig. 3 D represents makes offset R1 be the state of " 0 ", and the rotating center axis P1 of the input shaft 2 and center P3 of eccentric disc 6 is located with one heart.Gear ratio i is now infinitely great (∞).

Fig. 4 A-4C represents the relation of the pendulum angle scope of the change of the offset R1 that the offset controlling mechanism 4 of present embodiment brings and the oscillating motion of fork 18.

When Fig. 4 A represents that offset R1 is " maximum " of Fig. 3 A, the fork 18 of (when gear ratio i is minimum) is relative to the hunting range θ 2 of the rotary motion (angle of swing θ 1) of offset controlling mechanism 4, Fig. 4 B represent offset R1 be Fig. 3 B " in " time (when gear ratio i is middle) fork 18 when representing that offset R1 is " little " of Fig. 3 C relative to hunting range θ 2, Fig. 4 C of the rotary motion (angle of swing θ 1) of offset controlling mechanism 4 fork 18 of (when gear ratio i is large) relative to the hunting range θ 2 of the rotary motion (angle of swing θ 1) of offset controlling mechanism 4.Here, from the rotating center axis P4 of output shaft 3 to connecting rod 15 with swing end 18a tie point, be namely the length R2 of fork 18 to the distance of the center P5 of connection pin 19.

According to Fig. 4 A-4C, along with offset R1 diminishes, the pendulum angle range Theta 2 of fork 18 also diminishes, and when offset R1 becomes " 0 ", fork 18 no longer swings.

The bearing support structure > of < input shaft and output shaft then, with reference to Fig. 5 to Fig. 9, illustrates the input shaft 2 of present embodiment and the bearing support structure of output shaft 3.

In the present embodiment, as shown in Figure 5, the position making the 1st sidewall portion 101 of case of transmission 100 support lasso (outer ring) 40A1 of the 1st input shaft bearing 40A offsets to the shaft end side of an end of input shaft 2 relative to the central position 101A axially of the rolling element 40A2 of the 1st input shaft bearing 40A.Similarly, the position making the 2nd sidewall portion 102 of case of transmission 100 support lasso (outer ring) 40B1 of the 2nd input shaft bearing 40B offsets to the shaft end side of the other end of input shaft 2 relative to the central position 102A axially of the rolling element 40B2 of the 2nd input shaft bearing 40B.

In addition, make the 1st sidewall portion 101 of case of transmission 100 support the 1st position exporting the lasso 50A1 of bearing 50A exports the rolling element 50A2 of bearing 50A central position 101A axially relative to the 1st offsets to the shaft end side of an end of output shaft 3.Similarly, make the 2nd sidewall portion 102 of case of transmission 100 support the 2nd position exporting the lasso 50B1 of bearing 50B exports the rolling element 50B2 of bearing 50B central position 102A axially relative to the 2nd offsets to the shaft end side of the other end of output shaft 3.

That is, the supporting structure of the input shaft 2 in the 1st sidewall portion 101 and the 2nd sidewall portion 102 and the bearing of output shaft 3 is the relation of the central position symmetry about axis.

Here, about present embodiment to input shaft bearing and the expansion inhibitory action in gap and the flexure inhibitory action to input shaft and output shaft that export bearing, be described using an end of the input shaft 2 as the structural element in the Z of region in Fig. 6 A and Fig. 7 A, the 1st sidewall portion 101 and the 1st input shaft bearing 40A as an example.

Fig. 6 A-6C show when single direction rotation stop mechanism 17 with by fork 18 from input shaft 2 thruster to output shaft 3 side time fix fork 18 pushing mode carry out when moment of torsion transmits power relation.

When carrying out moment of torsion transmission by pushing mode, as shown in Figure 6B, the line of action being input to the load F1 of the 1st input shaft bearing 40A from input shaft 2 occurs to offset with the line of action of the reaction force F2 applied from the 1st sidewall portion 101 for load F1 and produces moment M 1.And, as shown in Figure 6 C, this moment M 1 can make lasso (outer ring) 40A1 of the 1st input shaft bearing 40A generation topple over, thus the raceway of lasso (outer ring) 40A1 is shifted to the direction of touch scrolling body 40A2, therefore, when moment of torsion transmits, the expansion in the gap between the lasso 40A1 of the opposite direction (Figure below) of the load F1 on the 1st input shaft bearing 40A and rolling element 40A2 can be suppressed.In addition, even if lasso (outer ring) 40A1 of the 1st input shaft bearing 40A creates topple over, because radial load is top dog acting in the load on rolling element 40A2, therefore the distributed load of rolling element 40A2 has almost no change, and can think and can not bring impact to bearing performance (durability and wearability) originally.

And then, when moment of torsion transmits, the reaction force inputted from output shaft 3 side direction input shaft 2 side and the moment M 1 produced at the two end part of input shaft 2 act on input shaft 2 in the mode producing the flexure B1 shown in Fig. 6 A, but pass through toppling over of lasso (outer ring) 40A1 of the 1st input shaft bearing 40A, loading direction for the reaction force F3 of load F1 changes, act in the opposite direction of moment M 1 to suppress the mode bending B1, therefore the expansion of the flexure of axis body can be suppressed, the durability of input shaft 2 can not be damaged, reliability and moment of torsion transmission efficiency, NVH can be improved.

Fig. 7 A-7C shows the power relation that the tractive mode of fixing fork 18 when single direction rotation stops mechanism 17 so that fork 18 is pulled to input shaft 2 side from output shaft 3 side is carried out when moment of torsion transmits.

Based on same principle, when carrying out moment of torsion transmission by tractive mode, as shown in Figure 7 B, the line of action of the load F4 inputted to the 1st input shaft bearing 40A from input shaft 2 occurs to offset with the line of action of the reaction force F5 applied from the 1st sidewall portion 101 for load F4 and produces moment M 2.And, as seen in figure 7 c, this moment M 2 makes lasso (outer ring) 40A1 of the 1st input shaft bearing 40A generation topple over, thus the raceway of lasso (outer ring) 40A1 is shifted to the direction of touch scrolling body 40A2, therefore, when moment of torsion transmits, the expansion in the gap between the lasso 40A1 of the opposite direction (in figure top) of the load F4 on the 1st input shaft bearing 40A and rolling element 40A2 can be suppressed.

And then, the reaction force inputted from output shaft 3 side direction input shaft 2 side when moment of torsion transmits and the moment M 2 produced at the two end part of input shaft 2 act on input shaft 2 in the mode producing the flexure B2 shown in Fig. 7 A, but pass through toppling over of lasso (outer ring) 40A1 of the 1st input shaft bearing 40A, loading direction for the reaction force F6 of load F4 changes, act in the opposite direction of moment M 2 to suppress the mode bending B2, therefore the expansion of the flexure of axis body can be suppressed, the durability of input shaft 2 can not be damaged, reliability and moment of torsion transmission efficiency, NVH can be improved.

In addition, the expansion inhibitory action in above-mentioned gap acts on the 1st and the 2nd output bearing 50A, the 50B at the 2nd input shaft bearing 40B of the other end of axle support input shaft 2 and the two end part of axle support output shaft 3 too.In addition, the flexure inhibitory action on an end of input shaft 2 and the flexure inhibitory action on the other end symmetric relation and produce synergy each other each other.And then, for be input to load F1 ', the F4 ' of the 1st and the 2nd output bearing 50A, 50B from output shaft 3 for, based on same principle, also suppress the expansion in gap to export bearing 50A, 50B to the 1st and the 2nd and suppress the mode of the flexure of output shaft 3 to play a role.

In the present embodiment, also for the rigidity in the 1st sidewall portion 101 and the 2nd sidewall portion 102, strong and weak rank is set according to the direction of the load F1 accepted from input shaft 2 and output shaft 3 and F4, thus improves the improvement effect of NVH.

As shown in figures 8 a-8b, 1st sidewall portion 101 and the 2nd sidewall portion 102 are divided into lower area: input area 101B, 102B, it than line L1 in the outer part, wherein this line L1 is by central position 101A, 102A axially of the 1st and the 2nd input shaft bearing 40A, 40B, and be input to input shaft bearing 40A with from input shaft 2, the loading direction of the load F1 of 40B when being maximum be vertical; Output area 101C, 102C, it than line L2 in the outer part, wherein this line L2 exports central position 101A, 102A axially of bearing 50A, 50B by the 1st and the 2nd, and be input to from output shaft 3 the load F1 ' that exports bearing 50A, 50B for loading direction time maximum vertical; And zone line 101D, 102D, it is clipped in input area 101B, 102B and between output area 101C, 102C, in this case, arranges strong and weak rank as follows according to each region for rigidity.

Namely, as shown in Figure 8 A, when single direction rotation stop mechanism 17 with when by fork 18 from input shaft 2 thruster to output shaft 3 side time fix fork 18 pushing mode carry out moment of torsion transmission, make the rigidity of input area 101B, 102B and output area 101C, 102C higher than the rigidity of zone line 101D, 102D.

On the other hand, as shown in Figure 8 B, when single direction rotation stop mechanism 17 with when by fork 18 from output shaft 3 layback to input shaft 2 side time fix fork 18 tractive mode carry out moment of torsion transmission, make the rigidity of input area 101B, 102B and output area 101C, 102C lower than the rigidity of zone line 101D, 102D.

By as above forming, thus the rigidity being positioned at the region in the sidewall portion the opposite direction of the loading direction inputted from input shaft 2 and output shaft 3 dies down, therefore the lasso (outer ring or inner ring) in the region of the opposition side of loading direction is easy to follow the toppling over of lasso of loading direction side and is shifted, namely in the example of Fig. 6 A-6C, as shown in Figure 9, 1st sidewall portion 101 is easy to bend with the region 101D of the direction opposite side of load F1, and be easy to produce thrust load on the lasso 40A1 of 101D side, this region, therefore the expansion inhibitory action in gap is contributed to, the improvement of NVH can be realized.In addition, the expansion inhibitory action in above-mentioned gap acts on the other end of input shaft 2 and the two end part of output shaft 3 too.

In addition, according to direction and the size of the load inputted from input shaft 2 and output shaft 3, the rigidity in the sidewall portion of case of transmission is adjusted to optimum, thus case of transmission can be formed with required MIN weight, therefore can either realize lightweight, efficiency can improve NVH well again.

As mentioned above, according to the present embodiment, can realize a kind ofly can suppressing the expansion in the gap between the lasso of the bearing supporting input shaft 2 and output shaft 3 and rolling element and improving the structure of the deterioration of NVH.

The present invention is not limited to above-described embodiment, can make a variety of changes within the spirit and scope of the present invention and revise.Therefore, in order to make public awareness scope of the present invention, at this, following claims are proposed.

Claims

1. a stepless speed variator (1), it has:

Input shaft (2), it is by from traveling driving source input queued switches power;

Output shaft (3), itself and described input shaft (2) configure abreast;

Connecting rod (20), it has the fork (18) linked with described output shaft (3), the oscillating motion of described fork (18) will be converted to by the rotary motion of the driving force input part (4 ~ 7) of described input shaft (2) rotary actuation, when described driving force input part (4) rotates 1 circle, described fork (18) carries out 1 reciprocal oscillating motion;

Single direction rotation stops mechanism (17), described fork (18) is fixed on described output shaft (3) when described fork (18) is for swinging aside by it, makes described fork (18) dally relative to described output shaft (3) when described fork (18) is for swinging to opposite side; And

Case of transmission (100), it supports described input shaft (2) and described output shaft (3) in the mode that can rotate freely, and accommodate described input shaft (2), described output shaft (3), described connecting rod (20) and described single direction rotation and stop mechanism (17)

The feature of this stepless speed variator (1) is,

Described case of transmission (100) has sidewall portion (101,102), this sidewall portion (101,102) supports the two end part of described input shaft (2) by means of input shaft bearing (40A, 40B), and the two end part of described output shaft (3) are supported by means of output bearing (50A, 50B)

Described sidewall portion (101, 102) the described input shaft bearing (40A of the support on, 40B) with described output bearing (50A, lasso (40A1 50B), 40B1, 50A1, position 50B1) is relative to described input shaft bearing (40A, 40B) with described output bearing (50A, rolling element (40A2 50B), 40B2, 50A2, central position (101A axially 50B2), 102A), to by described input shaft bearing (40A, 40B) with described output bearing (50A, the shaft end side skew of the described input shaft (2) 50B) supported respectively and the nearside of described output shaft (3).

2. stepless speed variator according to claim 1 (1), is characterized in that,

Described sidewall portion (101,102) has:

Input area (101B, 102B), it is positioned at than the side of line (L1) away from described output shaft (3), wherein this line (L1) is by the central position (101A, 102A) axially of described input shaft bearing (40A, 40B), and with the load (F1, F4) acted on from described input shaft (2) in described input shaft bearing (40A, 40B) for loading direction time maximum is vertical;

Output area (101C, 102C), it is positioned at than the side of line (L2) away from described input shaft (2), wherein this line (L2) is by the central position (101A, 102A) axially of described output bearing (50A, 50B), and with the load acted on from described output shaft (3) on described output bearing (50A, 50B) (F1 ', F4 ') for loading direction time maximum is vertical; And

Zone line (101D, 102D), it is clipped between described input area and described output area,

Described sidewall portion (101,102) is configured to,

When described single direction rotation stop mechanism (17) be when described fork (18) by from described input shaft (2) thruster to output shaft (3) side time described fork (18) is fixed mechanism, the rigidity of described input area (101B, 102B) and described output area (101C, 102C) is higher than the rigidity of described zone line (101D, 102D)

When described single direction rotation stop mechanism (17) be when described fork (18) by from described output shaft (3) layback to described input shaft (2) side time described fork (18) is fixed mechanism, the rigidity of described input area (101B, 102B) and described output area (101C, 102C) is lower than the rigidity of described zone line (101D, 102D).