CN104776182A - Continuously variable transmission - Google Patents
Continuously variable transmission Download PDFInfo
- Publication number
- CN104776182A CN104776182A CN201410720382.5A CN201410720382A CN104776182A CN 104776182 A CN104776182 A CN 104776182A CN 201410720382 A CN201410720382 A CN 201410720382A CN 104776182 A CN104776182 A CN 104776182A
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- China
- Prior art keywords
- connecting rod
- swing
- turning radius
- stepless speed
- speed variator
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H21/00—Gearings comprising primarily only links or levers, with or without slides
- F16H21/10—Gearings comprising primarily only links or levers, with or without slides all movement being in, or parallel to, a single plane
- F16H21/16—Gearings comprising primarily only links or levers, with or without slides all movement being in, or parallel to, a single plane for interconverting rotary motion and reciprocating motion
- F16H21/18—Crank gearings; Eccentric gearings
- F16H21/20—Crank gearings; Eccentric gearings with adjustment of throw
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Transmission Devices (AREA)
- Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)
- Rolling Contact Bearings (AREA)
Abstract
The invention provides a continuously variable transmission, a load input to rolling elements of a bearing of a connecting rod is dispersed to reduce the maximum load, and the durability of the bearing of the connecting rod can be improved. The connecting rod (15) is configured in a way that when a load input to a rotating disk (6) is a peak load, a maximum load vector is applied to the rotating disk (6) in the straight line connecting an input side pivot (P3) with an output side pivot (P4). The area, of the rotating disk (6), corresponding to the maximum load vector is provided with a hollow-out hole (6c) which passes through the rotating disk (6) in the rotating central axis direction.
Description
Technical field
The present invention relates to the stepless speed variator of the fourbar linkage type using connecting rod.
Background technique
In the past, be known to the stepless speed variator of following fourbar linkage type, this fourbar linkage type stepless speed variator has: input shaft, and the driving force from the main driving sources such as motor (traveling driving source) is passed to this input shaft; Output shaft, the rotating center axis being parallel ground of itself and input shaft configures; And multiple connecting rod (for example, referring to patent documentation 1).
In the stepless speed variator described in patent documentation 1, connecting rod has: turning radius controlling mechanism, and it is provided with the rotary part that can rotate centered by the rotating center axis of input shaft, and freely can regulate the turning radius of this rotary part; Be provided with and swing the swing connecting bar of end, its rotatably axle be bearing on output shaft; And connecting rod, one end is rotatably connected with the rotary part of turning radius controlling mechanism, and the swing end of its other end and swing connecting bar links.
Between swing connecting bar and output shaft, be provided with the overrunning clutch stoping mechanism as single direction rotation, swing connecting bar will be fixed relative to output shaft to during a sideway swivel centered by output shaft in swing connecting bar by this overrunning clutch, when swing connecting bar will rotate to opposite side, swing connecting bar is dallied relative to output shaft.
Turning radius controlling mechanism is made up of such as lower part: discoid rotary part, and it has the through hole worn prejudicially from center; Internal gear, it is arranged on the inner peripheral surface of the through hole of rotary part; 1st small gear, it is fixed on input shaft and engages with internal gear; Planet carrier, its driving force from secondary driving source (adjustment driving source) is passed to this planet carrier; And 2 the 2nd small gears, they engage with internal gear, respectively can rotation and the ground axle suspension that freely revolves round the sun freely by planet carrier.1st small gear and 2 the 2nd small gears are configured to their the central axis triangle that is summit for equilateral triangle.
In addition, turning radius controlling mechanism is except the structure shown in patent documentation 1, and what also have is made up of such as lower part: discoid cam part, and it is to rotate integratedly relative to the state of input shaft bias and input shaft; Rotary part, it can to rotate relative to the state of this cam part bias freely, and connecting rod is rotatably coated at this rotary part; Pinion shaft, it has multiple small gear in the axial direction; And secondary driving source, it makes pinion shaft rotate.
In this turning radius controlling mechanism, when the input shaft utilizing main driving source to rotate is identical with the rotational speed of the planet carrier utilizing secondary driving source to rotate, maintain the offset of center relative to the rotating center axis of input shaft of rotary part, the turning radius of turning radius controlling mechanism is also maintained constant.On the other hand, when input shaft is different from the rotational speed of planet carrier, the center of rotary part changes relative to the offset of the rotating center axis of input shaft, and the turning radius of turning radius controlling mechanism also changes.
Therefore, in this turning radius controlling mechanism, by making its turning radius change, and make the amplitude variations of the swing end of swing connecting bar, and then gear ratio is changed, the output shaft rotational speed of the rotational speed relative to input shaft is controlled.
Further, in this turning radius controlling mechanism, the distance between the center of the equilateral triangle that is summit with the center of 3 small gears and the rotating center axis of input shaft is set as equal with distance between the center of this equilateral triangle and the center of rotary part.
Therefore, this turning radius controlling mechanism can make the rotating center axis of input shaft and the center superposition of rotary part and make offset be " 0 ".When offset is " 0 ", even if when input shaft rotates, the amplitude of the swing end of swing connecting bar also becomes " 0 ", and output shaft becomes non-rotary state.
Further, in this turning radius controlling mechanism, cam part is formed by planet carrier and the 2nd small gear, to the driving force of cam part transmission from secondary driving source.This cam part is set as that phase place respective in each turning radius controlling mechanism, i.e. each connecting rod is different, utilizes multiple cam part around circumference one circle of input shaft.
Therefore, by being coated at the connecting rod of each turning radius controlling mechanism, each swing connecting bar can being made successively to output shaft transmitting torque, making output shaft Smooth Rotation.
Further, between the rotary part and the connecting rod being coated on this rotary part of turning radius controlling mechanism, the connecting rod bearing with rolling element is usually configured with.
Prior art document
Patent documentation
Patent documentation 1: Japanese Unexamined Patent Publication 2012-1048 publication
Summary of the invention
In the stepless speed variator formed like this, swing connecting bar to during a sideway swivel to output shaft transmitting torque (driving force), when rotating to opposite side not to output shaft transmitting torque.
Further, because connecting rod bearing is configured between rotary part and connecting rod, therefore, the durability of connecting rod bearing is driven by the size of the load being input to rotary part when rotary part rotates from connecting rod.
The present invention completes in view of above aspect, its object is to, there is provided a kind of stepless speed variator, this stepless speed variator by disperseing the load of the rolling element being input to connecting rod bearing and reducing maximum load, can improve the durability of connecting rod bearing.
In order to reach above-mentioned purpose, the invention provides a kind of stepless speed variator, it is characterized in that, described stepless speed variator has: input shaft, and the driving force of traveling driving source is passed to this input shaft, output shaft, the rotating center axis being parallel ground of itself and input shaft configures, connecting rod, it has turning radius controlling mechanism, swing connecting bar and connecting rod, described turning radius controlling mechanism is provided with the rotary part that can rotate centered by the rotating center axis of input shaft, and freely can regulate the turning radius of this rotary part, described swing connecting bar rotatably axle is supported on output shaft and is provided with swing end, one end of described connecting rod is rotatably connected with the rotary part of turning radius controlling mechanism, the other end of described connecting rod and the swing end of swing connecting bar link, the rotary motion of input shaft is converted to the oscillating motion of swing connecting bar by described connecting rod, single direction rotation stops mechanism, and swing connecting bar will be fixed to during a sideway swivel relative to output shaft in swing connecting bar by it, when swing connecting bar will rotate to opposite side, swing connecting bar is dallied, and connecting rod bearing, it is configured between connecting rod and rotary part, there is multiple rolling element, connecting rod is formed as: when to become the load being input to this rotary part from this connecting rod be the rotatable phase of peak load to rotary part, on the straight line by the tie point between the swing end of tie point between turning radius controlling mechanism and this connecting rod and swing connecting bar and this connecting rod, maximum load vector is applied to this rotary part, rotary part is formed with hollow part, described hollow part is positioned at the region corresponding with maximum load vector, and it is through on the rotating center axis direction of this rotary part.
Here, peak load refers under the state of the value turning radius of rotary part being fixed as regulation, during rotary part rotates 1 week, is input to the maximum load of rotary part from connecting rod.
The connecting rod of stepless speed variator of the present invention is formed as: when to become the load inputted from this connecting rod to this rotary part be the rotatable phase of peak load to rotary part, on the straight line by the tie point between the swing end of tie point between turning radius controlling mechanism and this connecting rod and swing connecting bar and this connecting rod, apply maximum load vector to this rotary part.
Further, the rotary part of stepless speed variator of the present invention is formed with hollow part in through mode on the rotating center axis direction of this rotary part on the region corresponding with maximum load vector.
By this hollow part, the load that rotary part bears from connecting rod is disperseed.Therefore, also disperse to be delivered to the load of the connecting rod bearing be configured between connecting rod and rotary part, reduce the maximum load of each rolling element being input to bearing.
Therefore, according to stepless speed variator of the present invention, compared with stepless speed variator in the past, owing to reducing the maximum load of the rolling element being input to connecting rod bearing during left-hand tools portion input peak load, therefore, it is possible to improve the durability of connecting rod bearing.
Further, according to stepless speed variator of the present invention, by forming hollow part, compared with stepless speed variator in the past, the lightweight of rotary part can be realized.
Further, in stepless speed variator of the present invention, preferably it is mounted on a vehicle, and the rotatable phase that rotatable phase is the torque being delivered to output shaft when reaching maximum turning radius.
The rotatable phase that the load being input to rotary part from connecting rod becomes the rotary part of peak load changes along with the change of the turning radius of rotary part.That is, rotary part exist for each turning radius become peak load rotatable phase (hereinafter, referred to as " peak phase ".) and the peak load corresponding with this peak phase.
Further, the torque being delivered to output shaft is larger, and the peak load being input to rotary part is larger.
In addition, the maximum value being delivered to the torque of output shaft is determined by the characteristic etc. (such as, the slip limit characteristic of tire) of the vehicle carrying stepless speed variator.Further, by this characteristic etc., when the turning radius of rotary part is below certain value (that is, gear ratio is more than certain value), the torque being delivered to output shaft becomes steady state value, and, become maximum value.
Therefore, when the turning radius of rotary part is below certain value (that is, gear ratio is more than certain value), peak load keeps maximum peak load (hereinafter, referred to as " peak-peak load ") constant.
Therefore, if be configured to for the formation of the rotatable phase of hollow part be the torque being delivered to output shaft reach maximum turning radius time rotatable phase, then compared with stepless speed variator in the past, at least when the peak load being input to rotary part is peak-peak load, the load being delivered to connecting rod bearing is disperseed, and reduces the maximum load being input to rolling element.
Its result is, does not damage the ease etc. of the intensity of rotary part and the assembling of stepless speed variator, just can improve the durability of connecting rod bearing further than stepless speed variator in the past.
Further, in stepless speed variator of the present invention, preferably it is mounted on a vehicle, and has multiple connecting rod, rotatable phase when rotatable phase is the turning radius that torque reaches maximum, gear ratio becomes minimum value being delivered to output shaft.
Stepless speed variator possesses multiple connecting rod, when the torque being delivered to output shaft is steady state value, due to the turning radius of rotary part larger (gear ratio is less), the torque that each connecting rod is shared is larger, therefore, the peak load being input to each rotary part is also larger.
Therefore, rotatable phase when if the rotatable phase be configured to for the formation of hollow part is the turning radius that torque reaches maximum, gear ratio becomes minimum value being delivered to output shaft, even if then when possessing multiple connecting rod, compared with stepless speed variator in the past, also at least when the peak load being input to 1 rotary part becomes peak-peak load, the load being input to the rolling element of connecting rod bearing is disperseed, and reduces the maximum load being input to rolling element.
Its result is, even if when possessing multiple connecting rod, does not damage the ease etc. of the intensity of rotary part and the assembling of stepless speed variator, just can improve the durability of connecting rod bearing further than stepless speed variator in the past.
And, in stepless speed variator of the present invention, single direction rotation stop mechanism be configured to: swing end relative to output shaft will to rotate away from the mode of input shaft time swing connecting bar is fixed, swing end will to rotate close to the mode of input shaft time swing connecting bar is dallied, in this case, because the region corresponding with maximum load vector is present in than the tie point between turning radius controlling mechanism and connecting rod from the region close to the tie point between the swing end and connecting rod of swing connecting bar, therefore, preferably hollow part is formed with in this region.
And, in stepless speed variator of the present invention, single direction rotation stop mechanism be configured to: swing end relative to output shaft will to rotate close to the mode of input shaft time swing connecting bar is fixed, swing end will to rotate away from the mode of input shaft time swing connecting bar is dallied, in this case, because the region corresponding with maximum load vector is present in than the tie point between turning radius controlling mechanism and connecting rod from the region away from the tie point between the swing end and connecting rod of swing connecting bar, therefore, preferably free portion is engraved in formation in this region.
Accompanying drawing explanation
Fig. 1 is the partial sectional view of the 1st mode of execution that stepless speed variator of the present invention is shown.
Fig. 2 is the side view of the connecting rod of the stepless speed variator that Fig. 1 is shown.
Fig. 3 A to Fig. 3 D is the explanatory drawing of the change of the turning radius of the input side fulcrum of the connecting rod of the stepless speed variator that Fig. 1 is shown, Fig. 3 A illustrates the situation that turning radius is maximum, Fig. 3 B illustrate turning radius be in situation, Fig. 3 C illustrates the situation that turning radius is little, and Fig. 3 D illustrates that turning radius is the situation of " 0 ".
Fig. 4 A to Fig. 4 D be the change of the turning radius relative to input side fulcrum of the connecting rod of the stepless speed variator that Fig. 1 is shown, the explanatory drawing of the change of the hunting range of outlet side fulcrum, Fig. 4 A illustrates the situation that hunting range is maximum, Fig. 4 B illustrate hunting range be in situation, Fig. 4 C illustrates the situation that hunting range is little, and Fig. 4 D illustrates that hunting range is " 0 " situation.
The chart of the change of the size of that Fig. 5 is the rotatable phase relative to rotating disc of the stepless speed variator that Fig. 1 is shown, be input to rotating disc from connecting rod load.
The chart of the change of torque that Fig. 6 illustrates the change of the turning radius relative to rotating disc of the stepless speed variator of Fig. 1, that be delivered to output shaft.
The chart of the change of torque that Fig. 7 A to Fig. 7 B is the rotatable phase relative to rotating disc of the stepless speed variator that Fig. 1 is shown, that be delivered to output shaft, Fig. 7 A illustrates that the turning radius of rotating disc is for state during R1a in the chart shown in Fig. 6, and Fig. 7 B illustrates that the turning radius of rotating disc is for state during R1b in the chart shown in Fig. 6.
Fig. 8 is the position of the openwork hole of the rotating disc of the stepless speed variator that Fig. 1 is shown and the side view of shape.
Fig. 9 illustrates the connecting rod of the 2nd mode of execution of stepless speed variator of the present invention and the position of openwork hole of the rotating disc of this connecting rod and the side view of shape.
Figure 10 is the position of openwork hole and the side view of shape of the rotating disc of the variation of the 1st mode of execution that stepless speed variator of the present invention is shown.
Label declaration
1A, 1B: stepless speed variator; 2: input part; 3: output shaft; 4: turning radius controlling mechanism; 5: cam disk (cam part); 5a: through hole; 5b: incision hole; 6: rotating disc (rotary part); 6a: accepting hole; 6b: internal tooth; 6c, 6d, 6e, 7: pinion shaft; 7a: small gear; 7b: pinion bearing; 8: differential attachment; 14a: running shaft; 9: sun gear; 10: the 1 gear rings; 11: the 2 gear rings; 12: ladder small gear; 12a: large-diameter portion; 12b: minor diameter part; 13: planet carrier; 14: actuator (adjustment driving source (secondary driving source)); 15: connecting rod; 15a: input side annulus; 15b: outlet side annulus; 16: connecting rod bearing; 17A, 17B: overrunning clutch (single direction rotation stops mechanism); 18: swing connecting bar; 18a: swing end; 18b: tab; 18c: patchhole; 19: connecting pin; 20: connecting rod; 21: transmission case; 21a: one end wall; 21b: the other end wall portion; 21c: surrounding wall portion; 22: bearing; 50: insert hole; ENG: motor (traveling driving source (main driving source)); H: gear ratio; P1: the rotating center axis of input shaft; P2: the center of cam disk 5; P3: the center (input side fulcrum) of rotating disc 6; P4: the center (outlet side fulcrum) of connecting pin 19; P5: the rotating center axis of output shaft 3; Distance between Rx:P1 and P2; Distance between Ry:P2 and P3; Distance (offset, the turning radius at the center (input side fulcrum P3) of rotating disc 6) between R1:P1 and P3; Distance (length of swing connecting bar 18) between R2:P4 and P5; V: the maximum load vector being input to rotating disc 6 from connecting rod 15; θ 1: the phase place of turning radius controlling mechanism 4; θ 2: the hunting range of swing connecting bar 18.
Embodiment
Below, with reference to accompanying drawing, the mode of execution of stepless speed variator of the present invention is described.The stepless speed variator of present embodiment is the stepless speed variator of fourbar linkage type, being can make gear ratio h (rotational speed of the rotational speed/output shaft of h=input shaft) infinitely great (∞) and make the rotational speed of output shaft be the speed changer of " 0 ", is the one of so-called IVT (Infinity Variable Transmission).
Further, present embodiment is mode of execution when being carried on vehicle by stepless speed variator, but, stepless speed variator of the present invention also can carry boats and ships etc. other the traffic tool or unmanned plane.
[the 1st mode of execution]
Be described with reference to the stepless speed variator 1A of Fig. 1 ~ Fig. 8 to the 1st mode of execution.
First, see figures.1.and.2, the structure of the stepless speed variator 1A of present embodiment is described.
As shown in Figure 1, the stepless speed variator 1A of present embodiment has: input part 2; Output shaft 3, the rotating center axis P1 of itself and input part 2 configures abreast; 6 turning radius controlling mechanisms 4, they are arranged on the rotating center axis P1 of input part 2.
By the driving force from the motor ENG (traveling driving source) as main driving source is passed to input part 2, this input part 2 rotates centered by rotating center axis P1.In addition, except internal-combustion engine, motor etc. also can be used as main driving source.
Output shaft 3 makes rotating power transmit to the driving wheel (omitting diagram) of vehicle via omitting illustrated differential gear.In addition, transmission shaft also can be set and replace differential gear.
Turning radius controlling mechanism 4 has: be arranged on the cam disk 5 (cam part) on the rotating center axis P1 of input part 2; And the rotating disc 6 (rotary part) be rotatably enclosed within outward on cam disk 5.
Cam disk 5 is discoid, and it is 1 group in the mode that can rotate integrally with input part 2 with 2 with the state of the rotating center axis P1 bias relative to input part 2 and arranges.The cam disk 5 of each 1 group is set to respective phase 60 °, is configured to circumference one circle of the rotating center axis P1 utilizing 6 groups of cam disks 5 around input part 2.
Cam disk 5 is formed with through hole 5a that is through on the rotating center axis P1 direction of input part 2 and that wear on the position of the center P2 bias relative to cam disk 5.Further, cam disk 5 is formed with incision hole 5b in the region across the rotating center axis P1 of input part 2 and the center P2 opposition side of cam disk 5, and this incision hole 5b makes the outer circumferential face of cam disk 5 be communicated with the inner peripheral surface of through hole 5a.
Utilize bolt (omitting diagram) between the cam disk 5 of 21 group and fix.Further, the opposing party of other cam disks 5 of 21 group that a side of the cam disk 5 of 21 group and adjacent turning radius controlling mechanism 4 have forms, and is integrally formed type cam part.Further, being positioned in cam disk 5 forms with input part 2 closest to the cam disk 5 on the position of motor ENG.Like this, input part 2 and multiple cam disk 5 is utilized to form input shaft (camshaft).
In addition, other means also can be utilized to fix without bolt between the cam disk 5 of 21 group.Further, one-piece type cam part by one-body molded and formed, also can be welded 2 cam disks 5 and make its integration.Further, as making to be positioned at the method formed with input part 2 closest to the cam disk 5 on the position of motor ENG, can be formed by one-body molded, also can weld cam part 5 and input part 2 and making it integrated.
As shown in Figure 2, rotating disc 6 is that the position of its center P3 bias is being provided with the discoid of accepting hole 6a, and rotating disc 6 is set to rotate relative to the rotating center axis P1 of input part 2.In its accepting hole 6a, be rotatably embedded with the cam disk 5 of each 1 group.Further, as shown in Figure 1, in the accepting hole 6a of rotating disc 6, the position between the cam disk 5 being in 1 group is provided with internal tooth 6b.
And, the accepting hole 6a of rotating disc 6 is eccentric relative to cam disk 5, and makes the distance Rx the center P2 (center of accepting hole 6a) from the rotating center axis P1 of input part 2 to cam disk 5 identical with the distance Ry the center P3 from the center P2 of cam disk 5 to rotating disc 6.
The input shaft be made up of with multiple cam disk 5 input part 2 possess form by making the through hole 5a of cam disk 5 be communicated with insert hole 50.Thus, input shaft becomes the hollow shaft shape closed with the one end open of motor ENG opposition side and the other end.
Be configured with pinion shaft 7 with one heart with rotating center axis P1 inserting in hole 50, this pinion shaft 7 is rotatable relative to input shaft.
Pinion shaft 7 has small gear 7a in the position that the internal tooth 6b with rotating disc 6 is corresponding.Further, pinion shaft 7 is provided with the pinion bearing 7b on the rotating center axis P1 direction of input part 2 between adjacent small gear 7a.Via this pinion bearing 7b, pinion shaft 7 supports input shaft.
The axle portion of small gear 7a and pinion shaft 7 forms as one.Small gear 7a engages with the internal tooth 6b of rotating disc 6 via the incision hole 5b of cam disk 5.In addition, small gear 7a also can be formed with pinion shaft 7 split, utilizes spline combine and link with pinion shaft 7.In the present embodiment, during referred to as small gear 7a, be defined as and comprise pinion shaft 7.
Further, the differential attachment 8 that pinion shaft 7 is formed with by planetary gears etc. is connected.
As shown in Figure 1, differential attachment 8 is such as configured to planetary gears, has: sun gear 9; The 1st gear ring 10 linked with the input shaft be made up of input part 2 and multiple cam disk 5; The 2nd gear ring 11 linked with pinion shaft 7; And by the supporting of ladder small gear 12 axle for can rotation and the planet carrier 13 that can revolve round the sun, wherein, described ladder small gear 12 be 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.
Driving force from the actuator 14 (adjustment driving source) of the secondary driving source as pinion shaft 7 is passed to sun gear 9.Therefore, via differential attachment 8, the driving force of actuator 14 is also transmitted to small gear 7a.
When making the rotational speed of pinion shaft 7 identical with the rotational speed of input part 2, sun gear 9 and the 1st gear ring 10 rotate with same speed.Its result is, these 4 key elements of sun gear 9, the 1st gear ring 10, the 2nd gear ring 11 and planet carrier 13 become the lock state that can not relatively rotate, and the pinion shaft 7 and the input part 2 that link with the 2nd gear ring 11 rotate with same speed.
When making the rotational speed of pinion shaft 7 slower than the rotational speed of input part 2, when the rotating speed setting the rotating speed of sun gear 9 as Ns, the 1st gear ring 10 be the gear ratio (number of teeth of the number of teeth/sun gear 9 of the 1st gear ring 10) of NR1, sun gear 9 and the 1st gear ring 10 for j time, the rotating speed of planet carrier 13 becomes (jNR1+Ns)/(j+1).And, when setting 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, the rotating speed of the 2nd gear ring 11 becomes { j (k+1) NR1+ (k-j) Ns}/{ k (j+1) }.
Namely, when existing poor between the rotational speed and the rotational speed of pinion shaft 7 of input part 2, transmit the driving force from actuator 14 come by means of the internal tooth 6b via the rotating disc 6 engaged with the small gear 7a of pinion shaft 7, rotating disc 6 rotates around the periphery of cam disk 5 centered by the center P2 of cam disk 5.
In addition, as shown in Figure 2, rotating disc 6 is eccentric relative to cam disk 5, and distance Rx center P2 from the rotating center axis P1 of input part 2 to cam disk 5 is identical with the distance Ry the center P3 from the center P2 of cam disk 5 to rotating disc 6.
Therefore, also the center P3 of rotating disc 6 can be made to be positioned on the line identical with the rotating center axis P1 of input part 2, make the distance (turning radius of turning radius controlling mechanism 4) between the rotating center axis P1 of the input part 2 and center P3 of rotating disc 6, that is, offset R1 is " 0 ".
The periphery of rotating disc 6 is rotatably connected with connecting rod 15, one (input part 2 side) end of this connecting rod 15 has the input side annulus 15a in large footpath, and another (output shaft 3 side) end has the diameter outlet side annulus 15b less than the diameter of input side annulus 15a.
The input side annulus 15a of connecting rod 15 is enclosed within rotating disc 6 via connecting rod bearing 16 is rotatably outer, and wherein, described connecting rod bearing 16 is made up of the ball bearing being 1 group with 2, and these 2 ball bearings are arranged side by side in the axial direction.
6 swing connecting bar 18 are bearing on output shaft 3 via overrunning clutch 17A (single direction rotation stops mechanism) rotatably axle corresponding to connecting rod 15 ground.
Overrunning clutch 17A is arranged between swing connecting bar 18 and output shaft 3, when swing connecting bar 18 relatively will rotate to side relative to output shaft 3 centered by the rotating center axis P5 of output shaft 3, swing connecting bar 18 is fixed (stationary state) relative to output shaft 3 by overrunning clutch 17A, when swing connecting bar 18 will rotate relatively to opposite side, overrunning clutch 17A makes swing connecting bar 18 dally (idling conditions) relative to output shaft 3.
Swing connecting bar 18 is formed as ring-type, is thereunder provided with the swing end 18a linked with the outlet side annulus 15b of connecting rod 15.Swing end 18a is provided with a pair outstanding tab 18b, and tab 18b is from axially clamping outlet side annulus 15b.A pair tab 18b is equipped with the patchhole 18c corresponding with the internal diameter of outlet side annulus 15b.
By inserting the connecting pin 19 as swing axis to patchhole 18c and outlet side annulus 15b, connecting rod 15 and swing connecting bar 18 can be linked with the relative rotation.
In the stepless speed variator 1A of present embodiment, form connecting rod 20 by having the turning radius controlling mechanism 4 of said structure, swing connecting bar 18 and connecting rod 15.
Connecting rod 20 and overrunning clutch 17 are incorporated in transmission case 21.In the below of this transmission case 21, it is hollow that lubricant oil defines oil.
Further, swing connecting bar 18 is configured to make it to swing end 18a to be immersed in the oil low-lying area of the lubricant oil accumulated in the below of transmission case 21.
Therefore, when the driving of connecting rod 20, the hollow lubrication of oil can be utilized to swing end 18a, and the lubricant oil kicked up in oily low-lying area by the oscillating motion of swing connecting bar 18, can lubricate the miscellaneous part of stepless speed variator 1A.
Further, transmission case 21 is made up of such as lower part: an end wall 21a, and it is fixed on motor ENG; The other end wall portion 21b, itself and an end wall 21a are arranged opposite; Surrounding wall portion 21c, it covers connecting rod 20 and overrunning clutch 17A across interval, and links the outer rim of an end wall 21a and the outer rim of the other end wall portion 21b.
At one end wall portion 21a and the other end wall portion 21b is formed and supports the opening portion of input shaft for axle and support the opening portion of output shaft 3 for axle, and chimeric on these opening portions have bearing 22.
In addition, in the present embodiment, the situation possessing 6 connecting rods 20 is illustrated.But the quantity of the connecting rod in stepless speed variator of the present invention is not limited to this quantity, such as, also can have the connecting rod of less than 5, also can have the connecting rod of more than 7.
Further, in the present embodiment, following situation is illustrated: form input shaft by input part 2 and multiple cam disk 5, input shaft possess form by making the through hole 5a of cam disk 5 be connected insert hole 50.But the input shaft in stepless speed variator of the present invention is not limited only to the structure formed like this.
Such as, input part can be made to be configured to have the hollow shaft-like inserting hole of one end open, form the through hole larger than the through hole of present embodiment input part can be run through insertion at discoid cam disk, cam disk is combined with the outer circumferential face spline of the input part being configured to hollow shaft-like.
In this situation, the input part be made up of quill shaft and the incision hole of cam disk are provided with incision hole accordingly.Further, be inserted into the small gear in input part to engage with the internal tooth of rotating disc via the incision hole of input part and the incision hole of cam disk.
Further, in the present embodiment, to using overrunning clutch 17 to stop the situation of mechanism to be illustrated as single direction rotation.But, single direction rotation in stepless speed variator of the present invention stops mechanism to be not limited only to overrunning clutch, such as, also can use twin-direction clutch, this twin-direction clutch is configured to freely to switch can from swing connecting bar to the sense of rotation relative to output shaft of the swing connecting bar of output shaft transmitting torque.
Then, with reference to Fig. 1 ~ Fig. 4 D, the connecting rod 20 of the stepless speed variator of present embodiment is described.
As shown in Figure 1, the stepless speed variator 1A total of present embodiment has 6 connecting rods 20 (fourbar linkage).As shown in Figure 2, connecting rod 20 is by connecting rod 15, swing connecting bar 18 and have rotating disc 6 can freely regulate the turning radius controlling mechanism 4 of its turning radius to form.By this connecting rod 20, the rotary motion of input shaft is converted to the oscillating motion of swing connecting bar 18.
In this connecting rod 20, when the turning radius (offset R1) of the center P3 (input side fulcrum) of the rotating disc 6 of turning radius controlling mechanism 4 is not " 0 ", when making input part 2 rotate with same speed with pinion shaft 7, each connecting rod 15 is while change phase place, push to output shaft 3 side and pull to the action of input part 2 side and repeat this alternating movement, swing connecting bar 18 be swung while hocket between input part 2 and output shaft 3 by swinging end 18a.
And, owing to being provided with overrunning clutch 17A between swing connecting bar 18 and output shaft 3, therefore, made by connecting rod 15 swing connecting bar 18 relative to output shaft 3 to push direction sideway swivel, namely swing end 18a relative to output shaft 3 to rotate away from the mode of input part 2 and to rotate with the speed of the rotational speed exceeding output shaft 3 time, swing connecting bar 18 is fixed relative to output shaft 3, transmits torque to output shaft 3.
On the other hand, swing connecting bar 18 relative to output shaft 3 to draw direction sideway swivel, namely swing end 18a relative to output shaft 3 to rotate close to the mode of input part 2 time, swing connecting bar 18 dallies relative to output shaft 3, not to output shaft 3 transmitting torque.
In the stepless speed variator 1A of present embodiment, the turning radius controlling mechanism 4 of 6 connecting rods 20 is owing to being configured in the mode of each difference 60 degree of phase places respectively, and therefore, output shaft 3 utilizes 6 connecting rods 20 to rotate successively.
Fig. 3 A to Fig. 3 D be illustrate the turning radius of the center P3 of the rotating disc 6 of turning radius controlling mechanism 4 (input side fulcrum) (offset R1) is changed state under pinion shaft 7 and rotating disc 6 between the figure of position relationship.
Fig. 3 A illustrates and makes offset R1 be the state of " maximum ", and pinion shaft 7 and rotating disc 6 are positioned at the position making the center P3 of the rotating center axis P1 of input part 2, the center P2 of cam disk 5 and rotating disc 6 arranged side by side in a straight line.Gear ratio h in this situation becomes minimum.
Fig. 3 B illustrate make offset R1 be less than Fig. 3 A " in " state, Fig. 3 C illustrates and makes offset R1 be the state of " little " also less than Fig. 3 B.Gear ratio h become in figure 3b larger than the gear ratio h of Fig. 3 A " in ", become " greatly " larger than the gear ratio h of Fig. 3 B in fig. 3 c.
Fig. 3 D illustrates and makes offset R1 be the state of " 0 ", and the rotating center axis P1 of input part 2 is positioned at concentric position with the center P3 of rotating disc 6.The gear ratio h of this situation becomes infinitely great (∞).
Fig. 4 A to Fig. 4 D is the figure of the relation between the hunting range θ 2 of the turning radius (offset R1) of the center P3 (input side fulcrum) of the rotating disc 6 that turning radius controlling mechanism 4 is shown and the oscillating motion of swing connecting bar 18.
Fig. 4 A illustrates that offset R1 is the situation (gear ratio h is the situation of " minimum ") of " maximum " of Fig. 3 A, Fig. 4 B illustrate offset R1 be Fig. 3 B " in " situation (gear ratio h be " in " situation), Fig. 4 C illustrates that offset R1 is the situation (gear ratio h is the situation of " greatly ") of " little " of Fig. 3 C, and Fig. 4 D illustrates that offset R1 is the situation (gear ratio h is the situation of infinitely great " ∞ ") of " 0 " of Fig. 3 D.
Here, R2 is the length of swing connecting bar 18.More specifically, R2 is the distance from the rotating center axis P5 of output shaft 3 to the center (outlet side fulcrum P4) of tie point, the i.e. connecting pin 19 connecting rod 15 and swing end 18a.Further, θ 1 is the phase place of the rotating disc 6 of turning radius controlling mechanism 4.
Can know from this Fig. 4, along with offset R1 diminishes, the hunting range θ 2 of swing connecting bar 18 narrows, and when offset R1 becomes " 0 ", swing connecting bar 18 does not swing.
Fig. 5 be under the state illustrating that the turning radius (offset R1) of rotating disc 6 is fixed to the value of regulation, relative to the rotating disc 6 of turning radius controlling mechanism 4 rotatable phase θ 1, the chart of the change of the size of the load that is input to rotating disc 6 from connecting rod 15.
Also can know from this Fig. 5, under the turning radius (offset R1) of rotating disc 6 is maintained constant state, during rotating disc 6 rotates 1 circle, the rotatable phase (peak phase θ p) that the load being input to rotating disc 6 from connecting rod 15 specifies at certain becomes maximum load (peak load Np).
The peak phase θ p corresponding with this peak load Np changes along with the change of the turning radius (offset R1) of rotating disc 6.That is, there is peak phase θ p and the peak load Np corresponding with this peak phase θ p for each turning radius (offset R1) in rotating disc 6.
Further, the torque being delivered to output shaft 3 is larger, and the peak load Np being input to rotating disc 6 is larger.
Fig. 6 be illustrate when the stepless speed variator 1A of present embodiment being used for general vehicle etc., relative to the turning radius (offset R1) of rotating disc 6 change, the chart of the change of the torque that is delivered to output shaft 3.
When only considering the structure of connecting rod 20 that stepless speed variator 1A possesses, turning radius (offset R1) less (gear ratio h is larger) of rotating disc 6, the torque being delivered to output shaft 3 is larger.
But, in fact, according to the characteristic etc. of the vehicle of lift-launch stepless speed variator 1A, become chart as shown in Figure 6.
Specifically, when offset R1 be regulation value (in figure 6 for R1b) below (gear ratio h is more than certain value), the torque being delivered to output shaft 3 becomes the slip limit value determined by the friction factor etc. of the driving wheel of this vehicle, when offset R1 is more than R1b, with the increase of offset R1, the torque being delivered to output shaft 3 reduces.
That is, in the turning radius (offset R1) of rotating disc 6 for below certain value (gear ratio h is more than certain value), the torque being delivered to output shaft 3 becomes steady state value and becomes maximum value.
Therefore, in the turning radius (offset R1) of rotating disc 6 for below certain value (gear ratio h is more than certain value), along with being delivered to the torque of output shaft 3 and the peak load Np changed keeps maximum peak load (hereinafter, referred to as " peak-peak load ") constant.
On the other hand, even if in the turning radius (offset R1) of rotating disc 6 for below certain value (gear ratio h is more than certain value), corresponding to the turning radius (offset R1) of rotating disc 6, the peak phase θ p reaching its peak load Np also can change.
And, stepless speed variator 1A due to present embodiment possesses multiple connecting rod 20, therefore, in figure 6, even if when the torque being delivered to output shaft 3 is slip limit value (maximum value), the quantity sharing the connecting rod 20 of the torque being delivered to this output shaft 3 neither be identical all the time.
Specifically, when offset R1 is the R1a close to 0, as shown in Figure 7 A, at certain time point, the quantity sharing the connecting rod 20 of the torque being delivered to output shaft 3 is 4.
But, larger than R1a (with reference to Fig. 6) at offset R1, for the torque being delivered to output shaft 3 be about to start to reduce before R1b, as shown in Figure 7 B, sharing with the quantity of the connecting rod 20 of the torque of the same size of Fig. 7 A is 3.
Namely, stepless speed variator 1A due to present embodiment possesses multiple connecting rod 20, therefore, when the size of the torque being delivered to output shaft 3 is steady state value (being here maximum value), turning radius (offset R1) larger (gear ratio h is less) of rotating disc 6, the torque that each connecting rod 20 is shared becomes larger, and the peak load Np being input to each rotating disc 6 also becomes larger.
Therefore, in the stepless speed variator 1A of present embodiment, when offset R1 becomes the R1b before the torque being delivered to output shaft 3 is about to start to reduce, the peak load Np being imported into each rotating disc 6 becomes maximum.
Then, with reference to Fig. 8, the openwork hole 6c (hollow part) of the rotating disc 6 of the stepless speed variator 1A of present embodiment is described in detail.
As shown in Figure 8, on the rotating disc 6 of the turning radius controlling mechanism 4 had at the connecting rod 20 of present embodiment, be formed with the upper through openwork hole 6c in the rotating center axis direction (that is, the rotating center axis P1 direction of input shaft) of rotating disc 6.
And, this openwork hole 6c is formed as: when becoming the load inputted from connecting rod 15 and reaching rotatable phase (the peak phase θ p) of peak load Np, this openwork hole 6c is arranged in the region corresponding with the maximum load vector (the vector v of Fig. 8) of the load vector being input to rotating disc 6 from connecting rod 15 of rotating disc 6.
By this openwork hole 6c, the load that rotating disc 6 bears from connecting rod 15 is disperseed.Therefore, the load being delivered to the connecting rod bearing 16 be configured between connecting rod 15 and rotating disc 6 is also disperseed, and reduces the maximum load of each rolling element being input to connecting rod bearing 16.
Therefore, stepless speed variator 1A according to the present embodiment, compared with stepless speed variator in the past, due to left-hand tools dish 6 input peak load Np time, the maximum load being input to the rolling element of connecting rod bearing 16 reduces, and therefore, the durability of connecting rod bearing 16 improves.
Further, stepless speed variator 1A according to the present embodiment, defines openwork hole 6c, thus, compared with stepless speed variator in the past, makes rotating disc 6 be able to lightweight.
And, in the stepless speed variator 1A of present embodiment, as mentioned above, when rotating disc 6 turning radius (offset R1) for below certain value (gear ratio h is more than certain value) (in figure 6, when offset R1 is below R1b), along with the torque being delivered to output shaft 3, the peak load Np that changes keeps peak-peak load constant.
Therefore, in the stepless speed variator 1A of present embodiment, the rotatable phase being configured to be used in the rotating disc 6 determining the region forming openwork hole 6c is at least included as rotatable phase when vehicle can export turning radius (the offset R1) of peak torque.
Namely, in the stepless speed variator 1A of present embodiment, at least to comprise the mode in the region of certain limit corresponding to rotatable phase that all peak load Np with being input to rotating disc 6 become the certain limit of peak-peak load, rotating disc 6 forms openwork hole 6c.
Due to such formation, therefore, in the stepless speed variator 1A of present embodiment, compared with stepless speed variator in the past, at least when the peak load Np being input to rotating disc 6 becomes peak-peak load (when offset R1 is below R1b in figure 6), the load being input to the rolling element of connecting rod bearing 16 is disperseed, and reduces the maximum load being input to rolling element.
Further, in the stepless speed variator 1A of present embodiment, owing to possessing multiple connecting rod, therefore, as mentioned above, when offset R1 is the R1b before the torque being delivered to output shaft 3 is about to start to reduce, the peak load Np being input to each rotating disc 6 becomes maximum.
Therefore, in the stepless speed variator 1A of present embodiment, the region corresponding with the maximum load vector of peak load Np during R1b before the torque that to be the offset R1 of rotating disc 6 be the region corresponding with the maximum load vector of peak-peak load in rotating disc 6 is delivered to output shaft 3 is about to start to reduce.
Therefore, in the stepless speed variator 1A of present embodiment, the rotatable phase being configured to be used in the rotating disc 6 determining the region forming openwork hole 6c be at least included as vehicle can export peak torque and gear ratio h reaches turning radius (the offset R1) of minimum value time rotatable phase.
Namely, in the stepless speed variator 1A of present embodiment, with at least comprise the load that is input to each rotating disc 6 add up to maximum turning radius (offset R1) time become the mode in region corresponding to maximum rotatable phase with the peak load of the rotating disc 6 being input to each connecting rod 20, rotating disc 6 is formed openwork hole 6c.
Due to such formation, therefore, in the stepless speed variator 1A of present embodiment, compared with stepless speed variator in the past, at least when the peak load being input to 1 rotating disc 6 becomes peak-peak load (when offset R1 becomes R1b in figure 6), the load being input to the rolling element of connecting rod bearing 16 is disperseed, and reduces the maximum load being input to rolling element.
And, openwork hole 6c is formed in such region: under the turning radius (offset R1) of rotating disc 6 is adjusted to the state making the torque maximum being delivered to output shaft 3, and this region is on the straight line of the outlet side fulcrum P4 by the tie point between the input side fulcrum P3 as the tie point between turning radius controlling mechanism 4 and the connecting rod 15 and swing end 18a as swing connecting bar 18 and connecting rod 15.
This is because the connecting rod 15 that the stepless speed variator 1A of present embodiment has is configured to, on the straight line by input side fulcrum P3 and outlet side fulcrum P4, input maximum load vector to rotating disc 6.That is, on this line, there is the region corresponding with the maximum load vector inputted from connecting rod 15 of rotating disc 6.
And, openwork hole 6c is formed in such region of rotating disc 6, this region than the input side fulcrum P3 as the tie point between turning radius controlling mechanism 4 and connecting rod 15 close to the outlet side fulcrum P4 as the tie point between the swing end 18a of swing connecting bar 18 and connecting rod 15.
This is because, as mentioned above, the stepless speed variator 1A of present embodiment possesses overrunning clutch 17A, this overrunning clutch 17A be configured to swing end 18a relative to output shaft 3 will to rotate away from the mode of input part 2 time swing connecting bar 18 is fixed, swing end 18a will to rotate close to the mode of input part 2 time swing connecting bar 18 is dallied.
Namely, owing to possessing such overrunning clutch 17A, therefore, in the stepless speed variator 1A of present embodiment, the region corresponding with the maximum load vector inputted from connecting rod 15 of rotating disc 6 is present in than the region of input side fulcrum P3 closer to outlet side fulcrum P4.
[the 2nd mode of execution]
With reference to Fig. 9, the stepless speed variator 1B of present embodiment is described.But, identical label is marked for the structure same with the stepless speed variator 1A of the 1st mode of execution in the structure of the stepless speed variator 1B of present embodiment, and their description is omitted.
As shown in Figure 9, the stepless speed variator 1B of present embodiment is provided with overrunning clutch 17B between swing connecting bar 18 and output shaft 3.
Therefore, made by connecting rod 15 swing connecting bar 18 relative to output shaft 3 to draw direction sideway swivel, namely swing end 18a relative to output shaft 3 to rotate close to the mode of input part 2 time, swing connecting bar 18 is fixed relative to output shaft 3, transmits torque to output shaft 3.
On the other hand, swing connecting bar 18 relative to output shaft 3 to push direction sideway swivel, namely swing end 18a relative to output shaft 3 to rotate away from the mode of input part 2 time, swing connecting bar 18 dallies relative to output shaft 3, not to output shaft 3 transmitting torque.
Owing to possessing such overrunning clutch 17B, therefore, in the stepless speed variator 1B of present embodiment, the region corresponding with the maximum load vector inputted from connecting rod 15 of rotating disc 6 is present in than the input side fulcrum P3 as the tie point between turning radius controlling mechanism 4 and connecting rod 15 from the region away from the outlet side fulcrum P4 as the tie point between the swing end 18a of swing connecting bar 18 and connecting rod 15.
Therefore, in the stepless speed variator 1B of present embodiment, openwork hole 6d is formed in than input side fulcrum P3 from the region away from outlet side fulcrum P4.
Further, even be formed with the stepless speed variator 1B of the present embodiment of openwork hole 6d on such position, the action effect same with the stepless speed variator 1A of the 1st mode of execution can also be obtained.
Above, illustrated mode of execution is illustrated, but the present invention is not limited only to such mode.
Such as, in the above-described embodiment, openwork hole 6c, 6d is defined to comprise by the mode in the region on the straight line of input side fulcrum P3 and outlet side fulcrum P4.But hollow out of the present invention does not necessarily carry out hollow out in the mode comprising such region.
In the above-described embodiment, it is consistent with above-mentioned straight line because of the maximum load vector being input to the load of rotating disc 6 from connecting rod 15 for carrying out hollow out in the mode comprising such region.Therefore, in the variform situation of connecting rod, the region should carrying out hollow out also changes.
Further, in the above-described embodiment, openwork hole 6c, 6d is formed by making rotating disc 6 hollow out.But hollow part of the present invention, not being necessarily openwork hole, namely leaving the shape of the edge of rotary part, also can be the otch that hollow out arrives the edge of rotary part.
Further, in the above-described embodiment, as shown in Figure 8 and Figure 9, the shape of openwork hole 6c, 6d becomes oval.But the shape of hollow part of the present invention is not limited only to this shape.Such as, shown in the variation of the stepless speed variator 1A of the 1st mode of execution as shown in Figure 10, also can form the openwork hole 6e that hollow part becomes the shape of the shape considering rotating disc 6.
Claims (5)
1. a stepless speed variator, is characterized in that, described stepless speed variator has:
Input shaft, the driving force of traveling driving source is passed to this input shaft;
Output shaft, the rotating center axis being parallel ground of itself and described input shaft configures;
Connecting rod, it has turning radius controlling mechanism, swing connecting bar and connecting rod, described turning radius controlling mechanism is provided with the rotary part that can rotate centered by the rotating center axis of described input shaft, and freely can regulate the turning radius of this rotary part, described swing connecting bar rotatably axle is supported on described output shaft and is provided with swing end, one end of described connecting rod is rotatably connected with the described rotary part of described turning radius controlling mechanism, the other end of described connecting rod and the swing end of swing connecting bar link, the rotary motion of described input shaft is converted to the oscillating motion of described swing connecting bar by described connecting rod,
Single direction rotation stops mechanism, and described swing connecting bar will be fixed to during a sideway swivel relative to described output shaft in described swing connecting bar by it, when described swing connecting bar will rotate to opposite side, described swing connecting bar is dallied; And
Connecting rod bearing, it is configured between described connecting rod and described rotary part, has multiple rolling element,
Described connecting rod is formed as: when to become the load being input to this rotary part from this connecting rod be the rotatable phase of peak load to described rotary part, on the straight line by the tie point between the described swing end of the tie point between described turning radius controlling mechanism and this connecting rod and described swing connecting bar and this connecting rod, maximum load vector is applied to this rotary part
Described rotary part is formed with hollow part, and described hollow part is positioned at the region corresponding with described maximum load vector, and through on the rotating center axis direction of this rotary part.
2. stepless speed variator according to claim 1, is characterized in that,
Described stepless speed variator is mounted on a vehicle,
Described rotatable phase is the rotatable phase of the torque being delivered to described output shaft when reaching maximum described turning radius.
3. stepless speed variator according to claim 2, is characterized in that,
Described stepless speed variator is mounted on a vehicle, and has multiple described connecting rod,
Rotatable phase when described rotatable phase is the described turning radius that torque reaches maximum, gear ratio becomes minimum value being delivered to described output shaft.
4. the stepless speed variator according to any one in claims 1 to 3, is characterized in that,
Described single direction rotation stop mechanism in described swing end relative to described output shaft will to rotate away from the mode of described input shaft time described swing connecting bar is fixed, in described swing end will to rotate close to the mode of described input shaft time described swing connecting bar is dallied
Described region is from the region close to the tie point between the described swing end and described connecting rod of described swing connecting bar than the tie point between described turning radius controlling mechanism and described connecting rod.
5. the stepless speed variator according to any one in claims 1 to 3, is characterized in that,
Described single direction rotation stop mechanism in described swing end relative to described output shaft will to rotate close to the mode of described input shaft time described swing connecting bar is fixed, in described swing end will to rotate away from the mode of described input shaft time described swing connecting bar is dallied
Described region is from the region away from the tie point between the described swing end and described connecting rod of described swing connecting bar than the tie point between described turning radius controlling mechanism and described connecting rod.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2014002623A JP6111207B2 (en) | 2014-01-09 | 2014-01-09 | Continuously variable transmission |
| JP2014-002623 | 2014-01-09 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN104776182A true CN104776182A (en) | 2015-07-15 |
| CN104776182B CN104776182B (en) | 2017-05-17 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201410720382.5A Active CN104776182B (en) | 2014-01-09 | 2014-12-02 | Continuously variable transmission |
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| Country | Link |
|---|---|
| JP (1) | JP6111207B2 (en) |
| CN (1) | CN104776182B (en) |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102009013993A1 (en) * | 2008-04-15 | 2009-10-22 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Output arrangement for use in crank-continuously variable transmission of e.g. diesel engine, has connection unit connected with free-wheel unit over eccentric unit and needle bearing that is provided around eccentric unit |
| DE102009031801A1 (en) * | 2008-07-21 | 2010-02-04 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Adjusting device for stepless transmission, particularly for crank continuously variable transmission, has drive shaft mounted in transmission housing and multiple eccentric units arranged next to each other on drive shaft |
| JP2012251609A (en) * | 2011-06-03 | 2012-12-20 | Honda Motor Co Ltd | Continuously variable transmission |
| WO2013001859A1 (en) * | 2011-06-30 | 2013-01-03 | 本田技研工業株式会社 | Four-joint link type continuously variable transmission |
| JP2013024359A (en) * | 2011-07-25 | 2013-02-04 | Honda Motor Co Ltd | Transmission device |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP5695541B2 (en) * | 2011-10-21 | 2015-04-08 | 本田技研工業株式会社 | Continuously variable transmission |
-
2014
- 2014-01-09 JP JP2014002623A patent/JP6111207B2/en not_active Expired - Fee Related
- 2014-12-02 CN CN201410720382.5A patent/CN104776182B/en active Active
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102009013993A1 (en) * | 2008-04-15 | 2009-10-22 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Output arrangement for use in crank-continuously variable transmission of e.g. diesel engine, has connection unit connected with free-wheel unit over eccentric unit and needle bearing that is provided around eccentric unit |
| DE102009031801A1 (en) * | 2008-07-21 | 2010-02-04 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Adjusting device for stepless transmission, particularly for crank continuously variable transmission, has drive shaft mounted in transmission housing and multiple eccentric units arranged next to each other on drive shaft |
| JP2012251609A (en) * | 2011-06-03 | 2012-12-20 | Honda Motor Co Ltd | Continuously variable transmission |
| WO2013001859A1 (en) * | 2011-06-30 | 2013-01-03 | 本田技研工業株式会社 | Four-joint link type continuously variable transmission |
| JP2013024359A (en) * | 2011-07-25 | 2013-02-04 | Honda Motor Co Ltd | Transmission device |
Also Published As
| Publication number | Publication date |
|---|---|
| JP6111207B2 (en) | 2017-04-05 |
| CN104776182B (en) | 2017-05-17 |
| JP2015132278A (en) | 2015-07-23 |
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