CN105202143A - Automotive power transmission device - Google Patents
Automotive power transmission device Download PDFInfo
- Publication number
- CN105202143A CN105202143A CN201510313468.0A CN201510313468A CN105202143A CN 105202143 A CN105202143 A CN 105202143A CN 201510313468 A CN201510313468 A CN 201510313468A CN 105202143 A CN105202143 A CN 105202143A
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- output shaft
- side fulcrum
- outlet side
- connecting rod
- shaft
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- 230000005540 biological transmission Effects 0.000 title claims abstract description 22
- 230000007246 mechanism Effects 0.000 claims abstract description 25
- 230000001276 controlling effect Effects 0.000 description 18
- 230000010355 oscillation Effects 0.000 description 8
- 230000002093 peripheral effect Effects 0.000 description 5
- 238000009826 distribution Methods 0.000 description 2
- 239000000314 lubricant Substances 0.000 description 2
- 238000011144 upstream manufacturing Methods 0.000 description 2
- 238000003466 welding Methods 0.000 description 2
- 240000001439 Opuntia Species 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000005461 lubrication Methods 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 230000001105 regulatory effect Effects 0.000 description 1
- 238000003860 storage Methods 0.000 description 1
Classifications
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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
- F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
- F16H37/12—Gearings comprising primarily toothed or friction gearing, links or levers, and cams, or members of at least two of these types
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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
- F16H57/00—General details of gearing
- F16H57/02—Gearboxes; Mounting gearing therein
- F16H57/023—Mounting or installation of gears or shafts in the gearboxes, e.g. methods or means for assembly
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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
- F16H2700/00—Transmission housings and mounting of transmission components therein; Cooling; Lubrication; Flexible suspensions, e.g. floating frames
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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
- F16H2702/00—Combinations of two or more transmissions
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Transmission Devices (AREA)
Abstract
The invention provides an automotive power transmission device which can reduce an output torque difference of each crank train. The automotive power transmission device is provided with the components of an input shaft, output shafts, input side fulcrums, output side fulcrums, connecting components, offset amount adjusting mechanisms and unidirectional clutches. The automotive power transmission device is provided with a plurality of crank trains in an axial direction, wherein each crank train is composed of the input side fulcrum, the output side fulcrum, the offset amount adjusting mechanism, the connecting component and the unidirectional clutch. The connecting components respectively convert the rotation of the input shaft to the swinging of the output side fulcrum according to the offset amount. The output shafts comprises a first output shaft which transmits a driving force by means of the unidirectional clutch from the output side fulcrum; and a second output shaft which is combined with the first output shaft and extends to the downstream side in a torque transmission direction, wherein the swinging radius between the rotation center of the output shaft and the output side fulcrum differs according to the distance between the rotation center and a combination part betwen the first output shaft and the second output shaft.
Description
Technical field
The present invention relates to the structure that minimizing four saves the difference of the output torque of link lever type stepless speed changer.
Background technique
Such as, four following joint link lever type stepless speed changers 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 four joint link lever type stepless speed changers described in above-mentioned Japanese Unexamined Patent Publication 2012-1048 publication, connecting rod and overrunning clutch are linked up in the mode rotated freely by connection pin etc., thus constitute the connecting rod from input shaft to output shaft transmission of drive force.And, four joint link lever type stepless speed changers are formed by configuring multiple connecting rod in the mode of the phase place that offsets one from another, and the distance between the rotating center (central axis of output shaft) of the center of the linking department of connecting rod side (path annulus) and overrunning clutch side is constant.
But, the difference of the torque transfer characteristics that these connecting rods cause due to the torsion of output shaft, the higher connecting rod of output torque and the lower connecting rod of output torque can be there is, therefore need the maximum permissible torque bearing the overrunning clutch of the outlet side of moment of torsion according to the connecting rod setting that the output torque in connecting rod is maximum.This maximum permissible torque can consist of the exterior part of fork rigidity the internal diameter or change changing the inner piece forming overrunning clutch according to each connecting rod sets, but need to change the shape of inner piece or exterior part or intensity etc. for each assembling position, manufacture cost uprises.
Summary of the invention
The present invention completes in view of above-mentioned problem, its object is to realize a kind ofly when not changing the shape of part and the intensity of connecting rod, to reduce the power transmission apparatus for vehicle of the difference of the output torque of each connecting rod.
In order to solve above-mentioned problem, reach object, the 1st form of the present invention provides a kind of power transmission apparatus for vehicle (1), and it has: input shaft (2), and it is by from driving source input queued switches power, output shaft (3), itself and described input shaft (2) configure abreast, input side fulcrum (P3), it is relative to described input shaft (2) eccentric rotary, outlet side fulcrum (P5), it swings relative to described output shaft (3), connecting member (15), it links described input side fulcrum (P3) and described outlet side fulcrum (P5), offset controlling mechanism (4), it can change the offset (R1) of described input side fulcrum (P3), and overrunning clutch (17), it makes the fixing or idle running relative to described output shaft (3) of described outlet side fulcrum (P5), be configured with multiple by described input side fulcrum (P3) in the axial direction, described outlet side fulcrum (P5), described offset controlling mechanism (4), the connecting rod that described connecting member (15) and described overrunning clutch (17) are formed, the rotary motion of described input shaft (2) is converted to the oscillating motion of described outlet side fulcrum (P5) by described connecting member (15) respectively according to described offset (R1), wherein, described output shaft (3) has: the 1st output shaft (3A), its via described overrunning clutch (17) by from described outlet side fulcrum (P5) transmission of drive force, and the 2nd output shaft (3B), itself and the 1st output shaft (3A) combine and extend to directions of torque transfer downstream side, from pendulum radius (R2) to described outlet side fulcrum (P5) of the rotating center (P4) of described output shaft (3) according to different from the distance described 1st output shaft (3A) and the connecting part (3A1) of described 2nd output shaft (3B) and different.
In addition, 2nd form of the present invention is in above-mentioned 1st form, increase being positioned at close to the pendulum radius (R2) of described 1st output shaft (3A) with the described outlet side fulcrum (P5) on the position of the connecting part (3A1) of described 2nd output shaft (3B) in described multiple connecting rod (20), and the pendulum radius (R2) that reduction is positioned at away from the described outlet side fulcrum (P5) on the position of described connecting part (3A1).
In addition, 3rd form of the present invention is in the above-mentioned 1st or the 2nd form, described 1st output shaft (3A) is arranged at the axial central part of described 1st output shaft (3A) with the connecting part (3A1) of described 2nd output shaft (3B), increase the pendulum radius (R2) of the described outlet side fulcrum (P5) on the central part being positioned at the axis of described 1st output shaft (3A) in described multiple connecting rod (20), and reduce the pendulum radius (R2) of the described outlet side fulcrum (P5) be positioned on the end of the axis of described 1st output shaft (3A).
In addition, 4th form of the present invention is in the above-mentioned 1st or the 2nd form, described 1st output shaft (3A) is arranged at the end of the side of the axis of described 1st output shaft (3A) with the connecting part (3A1) of described 2nd output shaft (3B), increase the pendulum radius (R2) of the described outlet side fulcrum (P5) on the end being positioned at the side of the axis of described 1st output shaft (3A) in described multiple connecting rod (20), and reduce the pendulum radius (R2) of the described outlet side fulcrum (P5) be positioned on the end of the opposite side of the axis of described 1st output shaft (3A).
The effect of invention
According to the present invention, when not changing the shape of part and the intensity of connecting rod, the difference of the output torque of each connecting rod can be reduced.
Specifically, according to the 1st form of the present invention, by making the pendulum radius of outlet side fulcrum change according to the torque transfer characteristics of connecting rod, thus the swing speed of outlet side fulcrum changes, and can reduce the difference of the output torque between connecting rod.
In addition, according to the 2nd to the 4th form of the present invention, the output torque of each connecting rod can be made to become even according to the position of the connecting part of output shaft.
Description according to a preferred embodiment of the present invention, other objects and advantages 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 External view of the structure of the stepless speed variator representing present embodiment.
Fig. 2 is the partial sectional view of the internal structure of the input shaft side of the stepless speed variator representing present embodiment.
Fig. 3 is the sectional view of the structure of the stepless speed variator representing present embodiment.
Fig. 4 is the sectional view of the stepless speed variator from end on observation present embodiment.
Fig. 5 A-5D is the figure of the gear shifting operation of the turning radius controlling mechanism of the stepless speed variator that present embodiment is described.
Fig. 6 A-6C 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. 7 A is the figure of angle of oscillation speed relative to the change of the angle of swing of input shaft of the outlet side fulcrum represented when changing length of connecting rod.
Fig. 7 B is the figure of angle of oscillation speed relative to the change of the angle of swing of input shaft of the outlet side fulcrum represented when changing pendulum radius.
Fig. 8 is the figure that the difference of the output torque represented for making the connecting rod of present embodiment becomes uniform 1st structure.
Fig. 9 A is the figure of the torque transfer characteristics of each connecting rod represented based on the 1st structure.
Fig. 9 B is the figure of the pendulum radius of the outlet side fulcrum of each connecting rod represented based on the 1st structure.
Figure 10 A is the figure of the output torque of the connecting rod represented when changing the pendulum radius of outlet side fulcrum by the 1st structure for each connecting rod.
Figure 10 B represents not by the figure of the 1st structure for the output torque of the connecting rod under the same case of the pendulum radius of each connecting rod change outlet side fulcrum.
Figure 11 is the figure that the difference of the output torque represented for making the connecting rod of present embodiment becomes uniform 2nd structure.
Figure 12 A is the figure of the torque transfer characteristics of each connecting rod represented based on the 2nd structure.
Figure 12 B is the figure of the pendulum radius of the outlet side fulcrum of each connecting rod represented based on the 2nd structure.
Figure 13 A is the figure of the output torque of the connecting rod represented when changing the pendulum radius of outlet side fulcrum by the 2nd structure for each connecting rod.
Figure 13 B represents not by the figure of the 2nd structure for the output torque of the connecting rod under the same case of the pendulum radius of each connecting rod change outlet side fulcrum.
Label declaration
1: stepless speed variator, 2: input shaft, 3: output shaft, 3A: the 1 output shaft, 3B: the 2 output shaft, 3A1: the 1 spline part, 3B1: the 2 spline part, 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, 100: case of transmission.
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, referring to figs. 1 through Fig. 4, illustrates the structure of the stepless speed variator of present embodiment.
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 contains input shaft 2, output shaft 3 and multiple (6) connecting rod 20 in the inside of case of transmission 100.Connecting rod 20 has offset controlling mechanism 4, connecting rod 15 and fork 18 respectively.
Input shaft 2 and multiple cam disk 5 link and form camshaft 51, and it accepts the driving force travelling driving source from motor or motor etc., is driven in rotation centered by rotating center axis P1.
Output shaft 3 and input shaft 2 are configured at the position be separated 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 set to eccentric rotary centered by the rotating center axis P1 of input shaft 2, has cam disk 5, eccentric disc 6 and pinion shaft 7.
Cam disk 5 is disc-shape, eccentric from the rotating center axis P1 of input shaft 2, and is set to 4 two by one group rotate integrally with input shaft 2 relative to 1 offset controlling mechanism.Each group of cam disk 5 is set to make phase shifting 60 ° around the rotating center axis P1 of input shaft 2 respectively, and is configured to pass the axis one week of 6 groups of cam disks 5 around input shaft 2.The cam disk 5 of 21 group relies on one-body molded or welding etc. to link the parts with same outer diameter, and each group cam disk 5 relies on bolt etc. axially fastening, thus becomes the camshaft 51 of strip.
Eccentric disc 6 is disc-shape, being provided with reception hole 6a from the position of the center P3 bias as input side fulcrum, 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 is configured in the through hole 5a of the inside of through camshaft 51 with one heart with the rotating center axis P1 of input shaft 2, and is supported on the inner peripheral surface of the through hole 5a of camshaft 51 in the mode that can relatively rotate via pinion bearing 7b.In addition, the outer circumferential face of the pinion shaft 7 between pinion bearing 7b is provided with external tooth 7a.And then pinion shaft 7 is connected to differential attachment 8.
Camshaft 51 is formed with incision hole 2a in the mode making the external tooth 7a of pinion shaft 7 expose, and 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 camshaft 51, 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.
This offset adjustment driving source 14 is controlled by not shown controller, for setting the offset R1 of offset controlling mechanism 4.
And, when making the rotational speed of this offset adjustment driving source 14 and input shaft 2 identical with the rotational speed of camshaft 51, 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 camshaft 51 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 and camshaft 51, 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) }.
Eccentric disc 6 is relative to cam disk 5, eccentric in the mode that distance Ra is identical with distance Rb, 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, be linked with the fork 18 as outlet side fulcrum via overrunning clutch 17.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 the path annulus 15b of connecting rod 15.A pair tab 18b runs through and is provided with the through hole 18c corresponding with the internal diameter of the path annulus 15b of connecting rod 15.In through hole 18c and path annulus 15b, insert connection pin 19, thus connecting rod 15 and fork 18 are linked up.
In the present embodiment, the swing end 18a of fork 18 is configured at the below of output shaft 3 in the mode of submerging in the lubricant oil of the below of housing 100 storage.The each several part of lubricant oil, lubrication stepless speed variator 1 thereby, it is possible to kicked up by the oscillating motion of fork 18.
Then, the connecting rod 20 of the stepless speed variator 1 of present embodiment is described.
Connecting rod 20 has offset controlling mechanism 4, connecting rod 15 and fork 18.
The rotary motion of input shaft 2, by connecting rod 20, is converted to the oscillating motion centered by the rotating center axis P4 of output shaft 3 of fork 18 by the stepless speed variator 1 of present embodiment.
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 with camshaft 51, 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. 5 a-5d, offset controlling mechanism 4 eccentric adjustment amount R1 can be passed through.
Fig. 5 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. 5 B represent make offset R1 be less than Fig. 5 A " in " state, Fig. 5 C represents makes offset R1 be the state of " little " being less than Fig. 5 B further.About gear ratio i, represent in figure 5b be greater than the gear ratio i of Fig. 5 A " in " state, represent in figure 5 c and be greater than the state of " greatly " of the gear ratio i of Fig. 5 B.Fig. 5 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. 6 A-6C 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. 6 A represents that offset R1 is " maximum " of Fig. 5 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. 6 B represent offset R1 be Fig. 5 B " in " time (when gear ratio i is middle) fork 18 when representing that offset R1 is " little " of Fig. 5 C relative to hunting range θ 2, Fig. 6 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 pendulum radius R2 of the outlet side fulcrum P5 of fork 18 to the distance of the center P5 of connection pin 19.
According to Fig. 6 A-6C, 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.
< reduces the structure > of the deviation of the output torque of each connecting rod then, with reference to Fig. 7 A-7B to Figure 13 A-13B, the structure of the deviation of the output torque reducing present embodiment is described.
As shown in Figure 8 and Figure 11, output shaft 3 has the 1st output shaft 3A and the 2nd output shaft 3B to the stepless speed variator 1 of present embodiment.1st output shaft 3A is inner piece as overrunning clutch 17 and plays the parts of the hollow shape of function, and is played the fork 18 of function via overrunning clutch 17 transmission of drive force by from as exterior part.2nd output shaft 3B is the axis body chimeric with the hollow hole 3A2 spline of the 1st output shaft 3A, to directions of torque transfer downstream side transmission of drive force.Namely, the 1st spline part 3A1 of the 2nd spline part 3B1 on the inner peripheral surface being formed at the 1st output shaft 3A be vertically formed at vertically on the outer circumferential face of the 2nd output shaft 3B is combined and rotates integrally, thus via the axletree transmission of drive force to automobile such as forward-reverse switching mechanism and differential gear.
And, in the present embodiment, for each connecting rod, different according to the distance the 1st spline part 3A1 of the 1st output shaft 3A from the pendulum radius R2 of the outlet side fulcrum P5 of distance, the i.e. fork 18 the rotating center axis P4 to the center P5 of the connection pin 19 of the fork 18 as outlet side fulcrum of output shaft 3, thus decrease the difference of the output torque of 6 connecting rods 20.That is, be configured in the fork 18 of 6 connecting rods 20, outlet side fulcrum P5 is located the position away from the 1st spline part 3A1, then pendulum radius R2 is less.In other words, the pendulum radius R2 be constructed to be positioned at away from the outlet side fulcrum P5 of the fork 18 on the position of the 1st spline part 3A1 is less than the pendulum radius R2 of the outlet side fulcrum P5 be positioned at close to the fork 18 on the position of the 1st spline part 3A1.
The situation A that Fig. 7 A-7B represents the length L changing connecting rod 15 and change pendulum radius R2 the angle of oscillation speed of outlet side fulcrum P5 of situation B relative to the change of the angle of swing of input shaft 2.
About connecting rod 20, as known in Fig. 7 A, though for each connecting rod 20 change connecting rod 15 length, namely from the length L input side fulcrum P3 to outlet side fulcrum P5, the angle of oscillation speed of fork 18 also not easily changes.On the other hand, as shown in Figure 7 B, if change the pendulum radius R2 of the outlet side fulcrum P5 of fork 18 for each connecting rod 20, then the angle of oscillation speed of the outlet side fulcrum P5 of fork 18 easily changes according to pendulum radius R2.In addition, in Fig. 7 A-7B, the value of X is greater than the value of Y (X > Y).
In addition, based on following formula, if increase the pendulum radius R2 of outlet side fulcrum P5, then angle of oscillation speed can reduce, and due to the impact of axis body torsion, torque transfer characteristics is reduced, thus output torque reduces.On the other hand, if reduce the pendulum radius R2 of outlet side fulcrum P5, then angle of oscillation speed can increase, and the impact that axis body reverses diminishes and torque transfer characteristics increases, and therefore output torque increases.
V＝R2·ω
Wherein, V, ω are respectively swing speed and the angle of oscillation speed of outlet side fulcrum P5.
And, as in the embodiment described in, changed the pendulum radius R2 of the outlet side fulcrum P5 of fork 18 for each connecting rod 20 by the distance between basis and the 1st spline part 3A1, the difference of the output torque that the difference that can balance out torque transfer characteristics causes, can reduce the difference of the output torque of each connecting rod 20.
(the 1st structure example)
In Fig. 8 of expression the 1st structure example, the 1st spline part 3A1 of the 1st output shaft 3A is arranged at axial central part, make to be in the position corresponding with the 1st spline part 3A1 and the pendulum radius R2 be positioned at close to the outlet side fulcrum P5 of in the part in downstream side No. 3 fork 18_3th is maximum (minimizing output torque), and be set as the position of the distance be more between the 1st spline part 3A1, then the pendulum radius R2 of outlet side fulcrum P5 less (output torque more increases).In this case, the pendulum radius R2 of the outlet side fulcrum P5 of No. 6 fork 18_6th is minimum, and residue fork is fork 18_1th, 5th, 4th, 2th by order from small to large.
When adopting this structure, as shown in Figure 9 A, the torque transfer characteristics of end is less than the torque transfer characteristics of axial central part to the torque transfer characteristics of each connecting rod 20, namely more away from the 1st spline part 3A1, then the impact of axis body torsion is larger, and torque transfer characteristics is lower.And, in the present embodiment, for the distribution of the torque transfer characteristics of each connecting rod 20 illustrated, be set as the position of the distance be more between the 1st spline part 3A1, then the pendulum radius R2 of the outlet side fulcrum P5 of fork 18 is less, thus increases output torque.By as above forming, compare the pendulum radius R2 of the outlet side fulcrum P5 of all connecting rod 20_1th ~ 6th shown in Figure 10 B identical when output torque T12, as shown in Figure 10 A, the difference of the output torque T11 of each connecting rod 20_1th ~ 6th diminishes, and the output torque of each connecting rod 20 can be made to become even.
In addition, as shown in Figure 9 B, in each connecting rod 20_1th ~ 6th, the difference of the maxima and minima of the pendulum radius R2 of the outlet side fulcrum P5 between axial central part and end is ± a few about mm.
(the 2nd structure example)
In Figure 11 of expression the 2nd structure example, the 1st spline part 3A1 of the 1st output shaft 3A is arranged at an end in the directions of torque transfer downstream side of the axis of the 1st output shaft 3A, the pendulum radius R2 be positioned at close to the outlet side fulcrum P5 of the fork 18_1th in the part of the 1st spline part 3A1 is made to be maximum, and be set as the position of the distance be more between the 1st spline part 3A1, then the pendulum radius R2 of outlet side fulcrum P5 less (output torque more increases).That is, according to the order from No. 1 fork 18_1th to No. 6 fork 18_6th, more close to the end of directions of torque transfer upstream side, then the pendulum radius R2 of the outlet side fulcrum P5 of fork 18 is less.
When adopting this structure, the torque transfer characteristics of each connecting rod 20 as illustrated in fig. 12, the torque transfer characteristics of the end of the upstream side of directions of torque transfer is less than the torque transfer characteristics in the downstream side of directions of torque transfer, namely, more away from the 1st spline part 3A1, then the impact of axis body torsion is larger, and torque transfer characteristics is lower.And, in the present embodiment, for the distribution of the torque transfer characteristics of each connecting rod 20 illustrated, be set as the position of the distance be more between the 1st spline part 3A1, then the pendulum radius R2 of the outlet side fulcrum P5 of fork 18 is less, thus increases output torque.By as above forming, compare the pendulum radius R2 of the outlet side fulcrum P5 of all connecting rod 20_1th ~ 6th shown in Figure 13 B identical when output torque T22, as shown in FIG. 13A, the difference of the output torque T21 of each connecting rod 20_1th ~ 6th diminishes, and the output torque of each connecting rod 20 can be made to become even.
In addition, as shown in Figure 12 B, in each connecting rod 20_1th ~ 6th, the difference of the maxima and minima of the pendulum radius R2 of the outlet side fulcrum P5 between axial two end part is ± a few about mm.
In addition, in above-mentioned 2nd structure example, the 1st spline part 3A1 is defined at the inner peripheral surface of the 1st output shaft 3A, and define the 2nd spline part 3B1 at the outer circumferential face of the 2nd output shaft 3B, also can form the 1st spline part 3A1 at the outer circumferential face of the 1st output shaft 3A, and form the 2nd spline part 3B1 at the inner peripheral surface of the 2nd output shaft 3B.
In addition, in above-mentioned 2nd structure example, also can be configured to form the 1st spline part 3A1 at the two end part of the 1st output shaft 3A, and link the 2nd output shaft 3B respectively at the two end part of the 1st output shaft 3A.
In addition, in the above-mentioned 1st and the 2nd structure example, spline part is formed at central part and directions of torque transfer end of downstream side, but the position of spline part is not limited thereto, the arbitrary position on the 1st output shaft 3A can be formed at.In this case, change the pendulum radius R2 of outlet side fulcrum P5 according to the torque transfer characteristics of each connecting rod 20 of the distance corresponded between spline part, thus output torque can be made to become even.
In addition, spline can not also be used to combine, but by the joint such as flange or welding the 1st output shaft 3A and the 2nd output shaft 3B.
In addition, in order to make the pendulum radius R2 of the outlet side fulcrum P5 of the fork 18 of each connecting rod 20 different, the different parts peculiar (exterior part of fork 18) of the pendulum radius R2 of outlet side fulcrum P5 can be made for each connecting rod 20, or the different ring-shaped member of internal diameter etc. is installed in the through hole 18c of fork 18 realizes regulating.In addition, between connecting rod 20, (such as adjacent crank linkage mechanism) torque transfer characteristics changes hardly, can also general purpose accessory.
As mentioned above, according to the present embodiment, when not changing part shape and the intensity of connecting rod 20, the difference of the output torque of each connecting rod 20 can be reduced.
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 (4)
1. a power transmission apparatus for vehicle (1), it has:
Input shaft (2), it is by from driving source input queued switches power;
Output shaft (3), itself and described input shaft (2) configure abreast;
Input side fulcrum (P3), it is relative to described input shaft (2) eccentric rotary;
Outlet side fulcrum (P5), it swings relative to described output shaft (3);
Connecting member (15), it links described input side fulcrum (P3) and described outlet side fulcrum (P5);
Offset controlling mechanism (4), it can change the offset (R1) of described input side fulcrum (P3); And
Overrunning clutch (17), it makes the fixing or idle running relative to described output shaft (3) of described outlet side fulcrum (P5),
Be configured with multiple connecting rod be made up of described input side fulcrum (P3), described outlet side fulcrum (P5), described offset controlling mechanism (4), described connecting member (15) and described overrunning clutch (17) in the axial direction
The rotary motion of described input shaft (2) is converted to the oscillating motion of described outlet side fulcrum (P5) by described connecting member (15) respectively according to described offset (R1),
The feature of this power transmission apparatus for vehicle is,
Described output shaft (3) has: the 1st output shaft (3A), its via described overrunning clutch (17) by from described outlet side fulcrum (P5) transmission of drive force; And the 2nd output shaft (3B), itself and the 1st output shaft (3A) combine and extend to directions of torque transfer downstream side,
From pendulum radius (R2) to described outlet side fulcrum (P5) of the rotating center (P4) of described output shaft (3) according to different from the distance described 1st output shaft (3A) and the connecting part (3A1) of described 2nd output shaft (3B) and different.
2. power transmission apparatus for vehicle according to claim 1, is characterized in that,
Increase being positioned at close to the pendulum radius (R2) of described 1st output shaft (3A) with the described outlet side fulcrum (P5) on the position of the connecting part (3A1) of described 2nd output shaft (3B) in described multiple connecting rod (20), and the pendulum radius (R2) that reduction is positioned at away from the described outlet side fulcrum (P5) on the position of described connecting part (3A1).
3. power transmission apparatus for vehicle according to claim 1 and 2, is characterized in that,
Described 1st output shaft (3A) is arranged at the axial central part of described 1st output shaft (3A) with the connecting part (3A1) of described 2nd output shaft (3B),
Increase the pendulum radius (R2) of the described outlet side fulcrum (P5) on the central part being positioned at the axis of described 1st output shaft (3A) in described multiple connecting rod (20), and reduce the pendulum radius (R2) of the described outlet side fulcrum (P5) be positioned on the end of the axis of described 1st output shaft (3A).
4. power transmission apparatus for vehicle according to claim 1 and 2, is characterized in that,
Described 1st output shaft (3A) is arranged at the end of the side of the axis of described 1st output shaft (3A) with the connecting part (3A1) of described 2nd output shaft (3B),
Increase the pendulum radius (R2) of the described outlet side fulcrum (P5) on the end being positioned at the side of the axis of described 1st output shaft (3A) in described multiple connecting rod (20), and reduce the pendulum radius (R2) of the described outlet side fulcrum (P5) be positioned on the end of the opposite side of the axis of described 1st output shaft (3A).
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2014-119878 | 2014-06-10 | ||
| JP2014119878A JP6072730B2 (en) | 2014-06-10 | 2014-06-10 | Power transmission device for vehicle |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN105202143A true CN105202143A (en) | 2015-12-30 |
| CN105202143B CN105202143B (en) | 2018-03-09 |
Family
ID=54933940
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201510313468.0A Expired - Fee Related CN105202143B (en) | 2014-06-10 | 2015-06-09 | Power transmission apparatus for vehicle |
Country Status (2)
| Country | Link |
|---|---|
| JP (1) | JP6072730B2 (en) |
| CN (1) | CN105202143B (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108999947A (en) * | 2018-09-13 | 2018-12-14 | 湖南山水节能科技股份有限公司 | The radial gear of variable-ratio |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107606094B (en) * | 2017-09-01 | 2019-05-21 | 重庆釜钰汽车科技有限公司 | Double swing-bar friction ratchet gear speed change gear |
| CN111173910B (en) * | 2019-11-05 | 2023-07-25 | 杨成强 | Torsion amplifying mechanism and driving mechanism |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1061472A (en) * | 1990-11-10 | 1992-05-27 | 何楚平 | Internal link pulsation stepless gear box |
| JPH0526323A (en) * | 1991-07-15 | 1993-02-02 | Nishi Seisakusho:Kk | Power transmission device |
| CN102080707A (en) * | 2011-02-22 | 2011-06-01 | 德州高科力液压有限公司 | Two-end output speed reducing transmission device |
| CN202349143U (en) * | 2011-11-02 | 2012-07-25 | 周承岗 | Stepless speed change device |
| JP2013036535A (en) * | 2011-08-08 | 2013-02-21 | Honda Motor Co Ltd | Four-bar linkage mechanism type continuously variable transmission |
| CN103534516A (en) * | 2011-06-30 | 2014-01-22 | 本田技研工业株式会社 | Four-joint link type continuously variable transmission |
Family Cites Families (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP5372842B2 (en) * | 2010-06-15 | 2013-12-18 | 本田技研工業株式会社 | Vehicle engine starting device |
| JP5896998B2 (en) * | 2010-06-29 | 2016-03-30 | シェフラー テクノロジーズ アー・ゲー ウント コー． カー・ゲーＳｃｈａｅｆｆｌｅｒ Ｔｅｃｈｎｏｌｏｇｉｅｓ ＡＧ ＆ Ｃｏ． ＫＧ | Crank-free wheel transmission with freewheel outer ring and freewheel outer ring |
| JP5885032B2 (en) * | 2012-07-02 | 2016-03-15 | 本田技研工業株式会社 | Power transmission device for vehicle |
| JP5885031B2 (en) * | 2012-07-02 | 2016-03-15 | 本田技研工業株式会社 | Power transmission device for vehicle |
| JP5885034B2 (en) * | 2012-09-26 | 2016-03-15 | 本田技研工業株式会社 | Power transmission device for vehicle |
-
2014
- 2014-06-10 JP JP2014119878A patent/JP6072730B2/en not_active Expired - Fee Related
-
2015
- 2015-06-09 CN CN201510313468.0A patent/CN105202143B/en not_active Expired - Fee Related
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1061472A (en) * | 1990-11-10 | 1992-05-27 | 何楚平 | Internal link pulsation stepless gear box |
| JPH0526323A (en) * | 1991-07-15 | 1993-02-02 | Nishi Seisakusho:Kk | Power transmission device |
| CN102080707A (en) * | 2011-02-22 | 2011-06-01 | 德州高科力液压有限公司 | Two-end output speed reducing transmission device |
| CN103534516A (en) * | 2011-06-30 | 2014-01-22 | 本田技研工业株式会社 | Four-joint link type continuously variable transmission |
| JP2013036535A (en) * | 2011-08-08 | 2013-02-21 | Honda Motor Co Ltd | Four-bar linkage mechanism type continuously variable transmission |
| CN202349143U (en) * | 2011-11-02 | 2012-07-25 | 周承岗 | Stepless speed change device |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108999947A (en) * | 2018-09-13 | 2018-12-14 | 湖南山水节能科技股份有限公司 | The radial gear of variable-ratio |
Also Published As
| Publication number | Publication date |
|---|---|
| JP6072730B2 (en) | 2017-02-01 |
| JP2015232379A (en) | 2015-12-24 |
| CN105202143B (en) | 2018-03-09 |
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