CN103968026B - Vehicle power transmission apparatus - Google Patents
Vehicle power transmission apparatus Download PDFInfo
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- CN103968026B CN103968026B CN201310693672.0A CN201310693672A CN103968026B CN 103968026 B CN103968026 B CN 103968026B CN 201310693672 A CN201310693672 A CN 201310693672A CN 103968026 B CN103968026 B CN 103968026B
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- Prior art keywords
- big end
- connecting rod
- chain link
- transmission apparatus
- power transmission
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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
- F16H29/00—Gearings for conveying rotary motion with intermittently-driving members, e.g. with freewheel action
- F16H29/02—Gearings for conveying rotary motion with intermittently-driving members, e.g. with freewheel action between one of the shafts and an oscillating or reciprocating intermediate member, not rotating with either of the shafts
- F16H29/04—Gearings for conveying rotary motion with intermittently-driving members, e.g. with freewheel action between one of the shafts and an oscillating or reciprocating intermediate member, not rotating with either of the shafts in which the transmission ratio is changed by adjustment of a crank, an eccentric, a wobble-plate, or a cam, on one of the shafts
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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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- 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
- F16H21/44—Gearings comprising primarily only links or levers, with or without slides all movement being in, or parallel to, a single plane for conveying or interconverting oscillating or reciprocating motions
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Transmission Devices (AREA)
Abstract
The invention provides a vehicle power transmission apparatus. The increase in weight of a connecting rod of the vehicle power transmission apparatus is minimized and meanwhile the roundness of a bearing pressed into a large end of the connecting rod is ensured. Two through holes which penetrate two axial surfaces are forme din a connecting part (19c) of the connecting rod (19). The center (Ob) of the outer circumferential surface (Pb) of the large end (19a) is eccentric to a small end (19b) relative to the center (Oa) of the inner circumferential surface (Pa). An inner rim part (Ea) of the large end, to which the through holes face, is an arc having a common center with the outer circumferential surface. Therefore, through preventing drastic change of the rigidity of the large end in the circumferential direction, the press-in counterforce can be made to change smoothly and slowly in the circumferential direction, and thus the roundness of the bearing (20) is improved. Furthermore, compared with a case that the roundness of the bearing is improved by forming thick wall integrally on the large end, the increase in weight and the increase in size of the connecting rod are minimized.
Description
Technical field
The present invention relates to the power transmission apparatus for vehicle possessing crank type buncher, described crank type infinitely variable speeds
Device transmits driving force through reciprocating connecting rod and one-way clutch from inputting axial output shaft.
Background technology
According to such power transmission apparatus for vehicle known in following patent documentation 1: by big end and the eccentric disc of connecting rod
Connecting, described eccentric disc and the power shaft being connected to electromotor rotate integratedly, and by the small end of connecting rod through one-way clutch
Device is connected with output shaft, utilizes the reciprocating motion of the connecting rod that the eccentric rotary because of eccentric disc produces by one-way clutch to be converted to
The rotary motion in one direction of output shaft.
Patent documentation 1: Japanese Unexamined Patent Application Publication 2005-502543 publication
, in above-mentioned existing power transmission apparatus for vehicle, the inner ring of ball bearing is pressed into and is located at power shaft
The outer peripheral face of eccentric disc, is pressed into the outer ring of this ball bearing by the inner peripheral surface of the big end of connecting rod.Owing to connecting rod has the big end of link
Portion and the linking part of small end, therefore, the rigidity of the big end of connecting rod is not fixed, the portion being connected with linking part
The rigidity divided uprises partly.Therefore, when the big end of connecting rod being pressed into the outer ring of ball bearing, higher with the rigidity of big end
The outer ring of part contact bear bigger press-in counteracting force, the outer ring of the part contact relatively low with the rigidity of big end is born
Less press-in counteracting force, owing to the official post of this press-in counteracting force obtains ball bearing deformation thus causes circularity to reduce, thus
The friction increase or the durability that there is ball bearing reduce such problem.
In order to avoid such problem, as long as making the wall thickness entirety of the big end of connecting rod increase to improve rigidity, but
It is, if it does, weight and the size such problem of increase of connecting rod can be there is.
Summary of the invention
The present invention completes in view of the foregoing, its object is to the weight of the connecting rod of power transmission apparatus for vehicle
Amount increases the suppression limit in minimum, guarantees to be pressed into the circularity of the bearing of the big end of this connecting rod simultaneously.
To achieve these goals, according to the invention described in technical scheme 1, it is provided that a kind of power transmission apparatus for vehicle,
This power transmission apparatus for vehicle possesses: power shaft, and it is connected with the source of driving；Output shaft, it is joined abreast with described power shaft
Put；Swinging chain link, it is can be supported on described output shaft in the way of swinging；One-way clutch, it is arranged in described output shaft
With between described swing chain link, when this swing chain link swings to a direction, described one-way clutch engages, at this swing chain
Described one-way clutch debonding when joint swings in the other direction；Eccentric disc, itself and the eccentric rotation integratedly of described power shaft
Turn；Shifting actuator, it changes the offset of described eccentric disc；And connecting rod, its described eccentric disc of connection and described swing chain link,
Described power transmission apparatus for vehicle is characterised by, described connecting rod possesses: ring-type big end, its be pressed into described partially
The bearing arranged on the outer peripheral face of cartridge；Small end, it is connected with described swing chain link；And linking part, it links described big end
Portion and described small end, be formed through the through hole on axial two surfaces, the outer peripheral face of described big end at described linking part
Center relative to the center of inner peripheral surface to the described small end lateral deviation heart, described through hole in the face of the inner edge portion of described big end
It is, with described outer peripheral face, there is the circular arc at center jointly.
It addition, according to the invention described in technical scheme 2, it is provided that a kind of power transmission apparatus for vehicle, it is characterised in that
On the basis of the structure of technical scheme 1, described in the radius ratio of the inner edge portion of described through hole, the radius of the outer peripheral face of big end is little.
It addition, according to the invention described in technical scheme 3, it is provided that a kind of power transmission apparatus for vehicle, it is characterised in that
On the basis of the structure of technical scheme 1 or technical scheme 2, the outer peripheral face of the outer edge of described through hole and described big end is in cutting
Wire connects.
Further, the ball bearing 20 of embodiment corresponds to this corresponding to the bearing of the present invention, the electromotor E of embodiment
Bright driving source.
According to the structure of technical scheme 1, when the power shaft being connected with the source of driving rotates, big end is connected to and power shaft
The connecting rod of the eccentric disc of eccentric rotary moves back and forth integratedly, and the swing chain link being connected with the small end of connecting rod is carried out back and forth
Swing.When swinging chain link and swinging to a direction, one-way clutch engages, when swinging chain link and swinging in the other direction,
One-way clutch debonding, therefore, the reciprocating motion of connecting rod is converted into the rotary motion in a direction of output shaft.When logical
When crossing the offset of shifting actuator change eccentric disc, the reciprocating stroke of connecting rod changes and makes to swing chain link
Angle of oscillation changes, and therefore, is passed to output shaft after the rotation speed change of power shaft.
Connecting rod possesses: ring-type big end, and it is pressed on the outer peripheral face of eccentric disc the bearing arranged；Small end,
It is connected with swinging chain link；And linking part, it links big end and small end, therefore, the rigidity of the big end of connecting rod with even
At the part that knot connects, local uprises, and when the big end of connecting rod is pressed into bearing, there is a possibility that due to press-in
The unbalanced of counteracting force makes bearing bend, thus causes circularity to decline.
And, the linking part at connecting rod is formed through the through hole on axial two surfaces, in the outer peripheral face of big end
The heart is relative to the center of inner peripheral surface to the small end lateral deviation heart, and the inner edge portion in the face of big end of through hole is jointly to have with outer peripheral face
There is the circular arc at center, therefore, the most drastically changed by the rigidity preventing big end, it is possible to make press-in counteracting force
The most gently change thus improve the circularity of bearing.And, carry with making big end be integrally formed as heavy wall
The situation of the circularity of high bearing is compared, it is possible to suppress the weight of connecting rod and the increase of size in Min..
It addition, according to the structure of technical scheme 2, due to the half of the outer peripheral face of the big end of the radius ratio of the inner edge portion of through hole
Footpath is little, therefore, by reducing the radius of the inner edge portion of through hole, it is possible to reduces and becomes excessive at the part being connected with linking part
The rigidity of big end, it is possible to make the rigidity of big end the most uniformly thus improve the circularity of bearing further.
It addition, according to the structure of technical scheme 3, owing to the outer edge of through hole and the outer peripheral face of big end are that secant-shaped connects
Connect, therefore, it is possible to be Min., energy by the change suppression of the wall thickness at the part that big end and linking part connect of connecting rod
The press-in counteracting force enough making bearing bear from big end is the most uniform, thus improves the circle of bearing further
Degree.
Accompanying drawing explanation
Fig. 1 is the skeleton diagram of power transmission apparatus for vehicle.
Fig. 2 is the detailed figure of 2 of Fig. 1.
Fig. 3 is the sectional view (the highest (TOP) state) of the 3-3 line along Fig. 2.
Fig. 4 is the sectional view (minimum (LOW) state) of the 3-3 line along Fig. 2.
Fig. 5 is the Action Specification figure under high state.
Fig. 6 is the Action Specification figure under minimum state.
Fig. 7 is the figure of the shape illustrating connecting rod.
Fig. 8 is the figure of the circularity of the big end comparing embodiment and comparative example 1～3.
Fig. 9 is the figure of the circularity of the big end comparing embodiment and comparative example 4.
Figure 10 is to compare embodiment and the figure of comparative example 5.
Label declaration
11: power shaft；
12: output shaft；
13: swing chain link；
14: shifting actuator；
18: eccentric disc；
19: connecting rod；
19a: big end；
19b: small end；
19c: linking part；
19d: through hole；
20: ball bearing (bearing)；
21: one-way clutch；
E: electromotor (driving source)；
The inner edge portion of Ea: through hole；
The outer edge of Eb: linking part；
Oa: the center of the inner peripheral surface of big end；
Ob: the center of the outer peripheral face of big end；
Pa: the inner peripheral surface of big end；
Pb: the outer peripheral face of big end；
Rb: the radius of the outer peripheral face of big end；
The radius of the inner edge portion of Rc: through hole.
Detailed description of the invention
Below, based on Fig. 1～Figure 10, embodiments of the present invention are illustrated.
As it is shown in figure 1, the driving force of the electromotor E axletree 10,10 through left and right is transferred to the vehicle of driving wheel W, W with dynamic
Force transfering device possesses crank type buncher T and differential mechanism D.
It follows that the structure of buncher T is illustrated based on Fig. 2～Fig. 6.
As shown in Figures 2 and 3, the buncher T of present embodiment is mutually isostructural multiple (embodiment party by having
Formula is 4) power transfer unit U axially overlaps, and these power transfer units U possesses sharing of configuring abreast
Power shaft 11 and the output shaft 12 that shares, being rotated in of power shaft 11 is transferred to output shaft 12 after being decelerated or accelerating.
Hereinafter, as representative, the structure of a power transfer unit U is illustrated.It is connected with electromotor E and rotates
Power shaft 11 runs through rotary shaft 14a of the hollow of the such shifting actuator of electro-motor 14 in the way of rotating against freely
Internal.The rotor 14b of shifting actuator 14 is fixed on rotary shaft 14a, and stator 14c is fixed on housing.The rotation of shifting actuator 14
Rotating shaft 14a can rotate with the speed identical with power shaft 11, and can be the most relative relative to power shaft 11
Rotate.
The power shaft 11 of rotary shaft 14a running through shifting actuator 14 is fixed with the 1st little gear 15, the row of bent axle shape
Carrier 16 is connected to rotary shaft 14a of shifting actuator 14 in the way of crossing over the 1st little gear 15.Diameter and the 1st little gear
15 2 identical the 2nd little gears 17,17 are supported in cooperate with the 1st little gear 15 through pinion pin 16a, 16a respectively and are configured to
The position of equilateral triangle, gear ring 18a engages with these the 1st little little gears 17,17 of gear the 15 and the 2nd, and described gear ring 18a is prejudicially
It is formed at the inside of the eccentric disc 18 of circular plate type.
Connecting rod 19 possesses big end 19a, small end 19b and links the linking part 19c of big end 19a and small end 19b.
Big end 19a is embedded in the periphery of eccentric disc 18 in the way of rotating against freely through ball bearing 20, and small end 19b sells 26 pivots
Axle is supported on swing chain link 13, and described swing chain link 13 is can be supported on the periphery of output shaft 12 in the way of swinging.
It is arranged in output shaft 12 and the one-way clutch 21 swung between chain link 13 possesses: ring-type external part 22, its quilt
Press-in swings the inner peripheral surface of chain link 13；Inner part 23, it is configured at the inside of external part 22 and is fixed on output shaft 12；And roller
25, they are configured between external part 22 and inner part 23 space of the wedge-like formed, and engaged spring 24 exerts a force.
According to Fig. 2 it will already have become clear 4 power transfer unit U have the planet carrier 16 of bent axle shape jointly, through the 2nd
The phase place of the eccentric disc 18 that little gear 17,17 is supported on planet carrier 16 differs 90 ° respectively at each power transfer unit U.Such as,
In fig. 2, the eccentric disc 18 of the power transfer unit U of left end relative to power shaft 11 in figure displaced over, from left beginning
The eccentric disc 18 of the 3rd power transfer unit U is relative to power shaft 11 lower section displacement in figure, from the 2nd of left beginning the and the 4th
The eccentric disc 18,18 of individual power transfer unit U, U is positioned at the centre of above-below direction.
The shape of connecting rod 19 is schematically shown in Fig. 1～Fig. 6, but, based on the Fig. 7 true form to connecting rod 19
Illustrate.
The big end 19a of connecting rod 19 possesses inner peripheral surface Pa and the outer peripheral face Pb of the radius Rb bigger than Ra, the periphery of radius Ra
The center Ob of the face Pb center Oa relative to inner peripheral surface Pa leans on to small end 19b lateral deviation with the amount of distance a.Therefore, big end 19a
The wall thickness of radial direction the most uneven, wall thickness diminishes in the side away from small end 19b, and wall thickness is near small end
The side of 19b becomes big.
In the central authorities of the linking part 19c of triangle, it is formed with the through hole 19d of triangle, described through hole 19d and passes through
Wear axial two faces of connecting rod 19, through hole 19d towards inner edge portion Ea of big end 19a by the outer peripheral face Pb with big end 19a
The circular arc of the radius Rc jointly with center Ob is constituted.The radius Rc of inner edge portion Ea of through hole 19d is set to than big end 19a
The amount of radius Rb small distance b of outer peripheral face Pb.
Linking part 19c possesses 2 outer edges Eb, Eb, these 2 outer edges Eb, Eb from small end 19b side towards big end
19a side mutually spreads while extending on one side, and outer edge Eb, Eb are that secant-shaped is connected with the outer peripheral face Pb of big end 19a.
It follows that the effect to the embodiments of the present invention possessing said structure illustrates.
First, the effect to a power transfer unit U of buncher T illustrates.If making shifting actuator
Rotary shaft 14a of 14 rotates against relative to power shaft 11, then planet carrier 16 rotates around the axis L1 of power shaft 11.Now, OK
The center of the equilateral triangle that the center O of carrier 16, the i.e. the 1st little gear 15 and two the 2nd little gears 17,17 are constituted is around power shaft
The axis L1 of 11 rotates.
Fig. 3 and Fig. 5 shows that the center O of planet carrier 16 is positioned at and output relative to the 1st little gear 15 (i.e. power shaft 11)
The state of the side that axle 12 is contrary, now, the offset relative to power shaft 11 of eccentric disc 18 becomes maximum, buncher
The gear ratio of T becomes high state.Fig. 4 and Fig. 6 shows that the center O of planet carrier 16 is relative to the 1st little gear 15 (i.e. power shaft
11) being positioned at the state of the side identical with output shaft 12, now, the offset relative to power shaft 11 of eccentric disc 18 becomes
Little, the gear ratio of buncher T becomes minimum state.
Under the high state shown in Fig. 5, if making power shaft 11 rotate by electromotor E and with identical with power shaft 11
Speed make rotary shaft 14a of shifting actuator 14 rotate, then power shaft 11, rotary shaft 14a, the little gear of planet carrier the 16, the 1st
15, two the 2nd little gears 17,17 and eccentric disc 18 when being integrally forming centered by power shaft 11 around counterclockwise side
Eccentric rotary is carried out to (reference arrow A).From (A) of Fig. 5 through (B) to (C) of Fig. 5 of Fig. 5 state rotate period,
The connecting rod 19 that big end 19a rotates against, through ball bearing 20, the periphery being supported on eccentric disc 18 freely makes swing chain link 13 around inverse
Clockwise (reference arrow B) swings, and described swing chain link 13 sells 26 small end 19b being supported on a pivot on connecting rod 19.Fig. 5's
(A) show and swing, with (C) of Fig. 5, the two ends that chain link 13 swings to described arrow B direction.
So, when swinging chain link 13 and swinging to arrow B direction, the external part 22 of the engaging-in one-way clutch of roller 25 21 is with interior
The space of the wedge-like between parts 23, thus the rotation of external part 22 is transferred to output shaft 12 via inner part 23, therefore, defeated
Shaft 12 (reference arrow C) counterclockwise rotates.
If the little gear 15 of power shaft the 11 and the 1st further rotates, then gear ring 18a and the 1st little gear of little gear the 15 and the 2nd
17, the eccentric disc 18 (reference arrow A) counterclockwise of 17 engagements carries out eccentric rotary.From (C) of Fig. 5 through Fig. 5's
(D) period rotated to the state of (A) of Fig. 5, big end 19a rotates against through ball bearing 20 and is supported on eccentric disc 18 freely
The connecting rod 19 of periphery make swing chain link 13 (reference arrow B') clockwise swing, described swing chain link 13 sells 26 pivots
Axle is supported on small end 19b of connecting rod 19.(C) of Fig. 5 and (A) of Fig. 5 show that swing chain link 13 is to described arrow B' direction
The two ends swung.
So, when swinging chain link 13 and swinging to arrow B' direction, roller 25 compressive engagement spring 24 is while by from outward
The space of the wedge-like between parts 22 and inner part 23 is released, so that external part 22 skids relative to inner part 23, thus
Output shaft 12 does not rotates.
As described above, when swing chain link 13 reciprocally swinging time, only when swing chain link 13 swaying direction be counterclockwise
During direction (reference arrow B), output shaft 12 (reference arrow C) the most counterclockwise rotates, therefore, and output shaft 12 intermittent rotary.
The figure of effect when Fig. 6 is to be shown under minimum state operating buncher T.Now, due to power shaft 11
Position is consistent with the center of eccentric disc 18, and therefore eccentric disc 18 is zero relative to the offset of power shaft 11.If in this state
Under make power shaft 11 rotate by electromotor E and make rotary shaft 14a of shifting actuator 14 with the speed identical with power shaft 11
Rotate, then power shaft 11, rotary shaft 14a, planet carrier the 16, the 1st little gear 15, two the 2nd little gears 17,17 and eccentric discs 18
When being integrally forming, centered by power shaft 11, (reference arrow A) carries out eccentric rotary counterclockwise., by
Offset in eccentric disc 18 is zero, and therefore the reciprocating stroke of connecting rod 19 is also zero, and output shaft 12 does not rotates.
Therefore, if driving shifting actuator 14 position of planet carrier 16 to be set in the high state of Fig. 3 and Fig. 4
Between low state, then it is capable of the operating under any gear ratio between zero gear ratio and predetermined gear ratio.
In buncher T, the phase place of the eccentric disc 18 of 4 the power transfer unit U being set up in parallel is staggered mutually
90 °, therefore, 4 power transfer unit U alternately transmit driving force, and any one in i.e. 4 one-way clutch 21 is necessarily located
In engagement state, thus enable that output shaft 12 rotates continuously.
, when the outer peripheral face of ball bearing 20 being pressed into the inner peripheral surface Pa of big end 19a of connecting rod 19, ball bearing 20 from
The inner peripheral surface Pa of big end 19a is deformed by being radially oriented the press-in counteracting force of inner side.Now, if being radially oriented inner side
Press-in counteracting force uniform in a circumferential direction, then may insure that the circularity of the ball bearing 20 after press-in, but the biggest end
The rigidity of portion 19a is the most uneven, near the part that big end 19a and linking part 19c connects, and rigidity local
Raise, accordingly, there exist ball bearing 20 and deform because of loading of pressing in thus cause circularity to reduce such problem.
The comparative example 1 of Fig. 8 is that the center Ob of the center Oa and outer peripheral face Pb that make inner peripheral surface Pa is consistent and make outer peripheral face Pb
Comparative example identical with the radius Rc of inner edge portion Ea for radius Rb, the wall thickness of big end 19a is in order to realize miniaturization and lightweight
And it being set to less, its weight is 422g.
In comparative example 1, the wall thickness of big end 19a is relatively thin, and the part of big end 19a and linking part 19c connection
Rigidity local raises, and therefore, the press-in counteracting force local of this part increases and causes ball bearing 20 to deform to radially inner side, by
This causes circularity to deteriorate to 52.5 μm.Circularity refers to the maximum radius of the rolling track of the ball of ball bearing 20 and least radius
Difference, in the case of positive round, circularity is 0 μm, and numerical value is the biggest, represents that circularity is the poorest.
Comparative example 2 is the comparative example of the wall thickness increase of the big end 19a making comparative example 1, and other are identical with comparative example 1.?
In comparative example 2, by making the wall thickness of big end 19a increase, weight increases to 918g, and, the outer peripheral face Pb's of big end 19a
Radius R2 also increases., owing to the increase of wall thickness makes the rigidity of big end 19a improve on the whole, alleviate rigidity and exist
Drastically changing this situation at the part that big end 19a and linking part 19c connects, therefore circularity significantly reduces and becomes 12.5 μ
m。
Comparative example 3 is the center Ob that the center Oa of the inner peripheral surface Pa of the big end 19a relative to comparative example 2 makes outer peripheral face Pb
To the comparative example of small end 19b side skew, weight becomes the 640g of the centre of comparative example 1 and comparative example 2.Due to big end 19a
Increasing with the wall thickness at the part of linking part 19c connection and the drastically change of rigidity is relaxed further, therefore circularity enters one
Step reduces and becomes 9.5 μm., in comparative example 3, at the part that big end 19a and linking part 19c connects, rigidity
Unbalanced still remaining, therefore circularity is impaired.
In embodiments, the radius Rc of inner edge portion Ea of the through hole 19d of comparative example 3 is set to than outer peripheral face Pb's
Radius Rb is little so that big end 19a reduces in the face of the rigidity local of the part of inner edge portion Ea.Thus, the connecting rod 19 of embodiment
Weight be suppressed in 625g, and, circularity improves to better than any one in comparative example 1～comparative example 3 3.8.
Fig. 9 is the figure of the effect for through hole 19d is described, in the comparative example 4 shown in (B) of Fig. 9, with embodiment
Part suitable for through hole 19d do not extend through, but blocked by the web 19e of thin-walled.Understand, owing to this web 19e makes
In the face of the rigidity of the big end 19a of inner edge portion Ea of through hole 19d significantly improves, circularity significantly deteriorates.On the other hand, at Fig. 9
The embodiment shown in (A) in understand, by forming through hole 19d, in the face of the big end of inner edge portion Ea of through hole 19d
The rigidity of 19a reduces, and circularity greatly improves.
Figure 10 is the figure of the effect of outer edge Eb, the Eb for linking part 19c is described, in the comparison shown in (B) of Figure 10
In example 5, outer edge Eb, Eb of linking part 19c be not the outer peripheral face Pb with big end 19a be that secant-shaped is connected, but across
Connect.As a result of which it is, there is a problem in that the wall thickness of big end 19a drastically changes near cross part, owing to thus causing
The drastically change of rigidity so that circularity deteriorates.On the other hand, in the embodiment shown in (A) of Figure 10, linking part 19c
The outer peripheral face Pb of outer edge Eb, Eb and big end 19a be that secant-shaped is connected, it is therefore prevented that the wall thickness of big end 19a is being handed over
Drastically change near fork, thus improve circularity.
As described above, according to present embodiment, it is possible to the weight of connecting rod 19 is being increased suppression minimal same
Time make the rigidity of big end 19a the most uniform, it can be ensured that be pressed into circularity the reality of the ball bearing 20 of big end 19a
The reduction now rubbed and the raising of durability.
Above, embodiments of the present invention are illustrated, but the present invention can be in the range of without departing from its main points
Carry out various design alteration.
Such as, the bearing of the present invention is not limited to the ball bearing 20 of embodiment, can be needle bearing, roller axle
Hold, the arbitrary bearing such as sliding bearing.
It addition, the driving source of the present invention is not limited to the electromotor E of embodiment, it is also possible to be that motor generator etc. is appointed
The driving source of meaning.
Claims (3)
1. a power transmission apparatus for vehicle, it possesses:
Power shaft (11), it is connected with the source of driving (E)；
Output shaft (12), it configures abreast with described power shaft (11)；
Swinging chain link (13), it is can be supported on described output shaft (12) in the way of swinging；
One-way clutch (21), it is arranged between described output shaft (12) and described swing chain link (13), at this swing chain link
(13) when swinging to a direction, described one-way clutch (21) engages, when this swing chain link (13) swings in the other direction
Described one-way clutch (21) debonding；
Eccentric disc (18), itself and described power shaft (11) eccentric rotary integratedly；
Shifting actuator (14), it changes the offset of described eccentric disc (18)；With
Connecting rod (19), its described eccentric disc of connection (18) and described swing chain link (13),
Described power transmission apparatus for vehicle is characterised by,
Described connecting rod (19) possesses: ring-type big end (19a), and it is pressed into and sets on the outer peripheral face of described eccentric disc (18)
The bearing (20) put；Small end (19b), it is connected with described swing chain link (13)；With linking part (19c), its link is described greatly
End (19a) and described small end (19b),
The through hole (19d) on axial two surfaces it is formed through, outside described big end (19a) at described linking part (19c)
The center (Oa) relative to inner peripheral surface (Pa), the center (Ob) of side face (Pb) to described small end (19b) the lateral deviation heart, described in run through
The inner edge portion (Ea) in the face of described big end (19a) in hole (19d) is that the outer peripheral face (Pb) with described big end (19a) has jointly
There is the circular arc of center (Ob),
The wall thickness of the radial direction of described big end (19a) is the most uneven, and described wall thickness is away from described small end
(19b) side diminishes, and described wall thickness is becoming big near the side of described small end (19b).
Power transmission apparatus for vehicle the most according to claim 1, it is characterised in that
The radius (Rc) of the inner edge portion (Ea) of described through hole (19d) is than the radius of the outer peripheral face (Pb) of described big end (19a)
(Rb) little.
3. according to the power transmission apparatus for vehicle described in claim 1 or claim 2, it is characterised in that
The outer edge (Eb) of described through hole (19d) is connected in secant-shaped with the outer peripheral face (Pb) of described big end (19a).
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2013-020814 | 2013-02-05 | ||
| JP2013020814A JP6011971B2 (en) | 2013-02-05 | 2013-02-05 | Power transmission device for vehicle |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN103968026A CN103968026A (en) | 2014-08-06 |
| CN103968026B true CN103968026B (en) | 2017-01-11 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201310693672.0A Active CN103968026B (en) | 2013-02-05 | 2013-12-17 | Vehicle power transmission apparatus |
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| Country | Link |
|---|---|
| JP (1) | JP6011971B2 (en) |
| CN (1) | CN103968026B (en) |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP6168523B2 (en) * | 2014-02-05 | 2017-07-26 | 本田技研工業株式会社 | Power transmission device for vehicle |
| JP6602623B2 (en) * | 2015-09-25 | 2019-11-06 | Ｎｔｎ株式会社 | Connecting rod module and manufacturing method thereof |
| CN109236975A (en) * | 2018-10-31 | 2019-01-18 | 江苏牛牌纺织机械有限公司 | A kind of eccentric wheel and connecting rod engaging member |
Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN202500976U (en) * | 2012-03-12 | 2012-10-24 | 周有强 | Connecting-rod tooth-engaging type speed reducing and changing device |
Family Cites Families (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2005502543A (en) * | 2001-09-26 | 2005-01-27 | ルーク ラメレン ウント クツプルングスバウ ベタイリグングス コマンディートゲゼルシャフト | Drive device |
| JP2003322138A (en) * | 2002-04-30 | 2003-11-14 | Ntn Corp | Connecting rod and connecting rod with bearing |
| JP5363426B2 (en) * | 2010-06-15 | 2013-12-11 | 本田技研工業株式会社 | Power transmission device for vehicle |
| US9347416B2 (en) * | 2010-08-27 | 2016-05-24 | Honda Motor Co., Ltd. | Engine starting device for vehicle |
| US9121483B2 (en) * | 2011-06-30 | 2015-09-01 | Honda Motor Co., Ltd. | Four-joint link type continuously variable transmission |
| CN103649594B (en) * | 2011-07-13 | 2016-03-09 | 本田技研工业株式会社 | Stepless speed variator |
-
2013
- 2013-02-05 JP JP2013020814A patent/JP6011971B2/en not_active Expired - Fee Related
- 2013-12-17 CN CN201310693672.0A patent/CN103968026B/en active Active
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN202500976U (en) * | 2012-03-12 | 2012-10-24 | 周有强 | Connecting-rod tooth-engaging type speed reducing and changing device |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2014152808A (en) | 2014-08-25 |
| CN103968026A (en) | 2014-08-06 |
| JP6011971B2 (en) | 2016-10-25 |
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