CN104816629B - Power transmission apparatus for vehicle - Google Patents
Power transmission apparatus for vehicle Download PDFInfo
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- CN104816629B CN104816629B CN201510052523.5A CN201510052523A CN104816629B CN 104816629 B CN104816629 B CN 104816629B CN 201510052523 A CN201510052523 A CN 201510052523A CN 104816629 B CN104816629 B CN 104816629B
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- power transmission
- input shaft
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- 230000002093 peripheral effect Effects 0.000 claims abstract description 30
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Abstract
The present invention provides a kind of power transmission apparatus for vehicle, and the weight of the connecting rod of power transmission apparatus for vehicle is increased and suppressed in Min. by it, while the circularity of the bearing for ensuring to be pressed into the big end of the connecting rod.Insertion axially two through holes on surface are formed with the linking part of connecting rod, the center of outer peripheral face of the center relative to big end of the circular arc of the inner edge portion of the big end that through hole is faced is constituted to the small end lateral deviation heart, therefore, it is connected with linking part at the circumferential two ends of through hole by making big end, and the vicinity of position makes the radial thickness of big end reduce and it is rigidly reduced at two for rigidly improving, rigidity thus, it is possible to prevent big end drastically changes in a circumferential direction, press-in reaction force is set gently to change in a circumferential direction, so as to improve the circularity of bearing.And, compared with big end is made on the whole for heavy wall come the situation of the circularity for improving bearing, the increase of the weight of connecting rod and size can be suppressed in Min..
Description
Technical field
The present invention relates to the power transmission apparatus for vehicle with crank-type buncher, the crank-type variable speed
Device transmits driving force by reciprocating connecting rod and one-way clutch from the axial output shaft of input.
Background technology
Such power transmission apparatus for vehicle according to known in following patent document 1：By the big end of connecting rod and eccentric disc
Connection, the eccentric disc integratedly rotates with the input shaft for being connected to engine, and by one-way clutch by the small end of connecting rod
Portion is connected with output shaft, and the reciprocating motion of the connecting rod that will be produced the eccentric rotary because of eccentric disc using one-way clutch is converted to
One rotary motion in direction of output shaft.
Patent document 1：German DE102009039993
However, in above-mentioned conventional power transmission apparatus for vehicle, the inner ring of ball bearing is pressed into located at input shaft
Eccentric disc outer peripheral face on, the inner peripheral surface of the big end of connecting rod is pressed on the outer ring of the ball bearing.Because connecting rod has
Link the linking part of big end and small end, therefore, the rigidity of the big end of connecting rod is not fixed in a circumferential direction, with linking part
The rigidity of the part of connection is partly uprised.Therefore, it is and big when the big end of connecting rod has been pressed on the outer ring of ball bearing
Bear larger press-in reaction force, the part relatively low with the rigidity of big end in the outer ring of the rigid part contact higher of end
Less press-in reaction force is born in the outer ring of contact, and circle is caused because the official post of the press-in reaction force obtains ball bearing deformation
Degree is reduced, and there are problems that the friction increase of ball bearing, durability reduction are such.
In order to avoid such problem, integrally increase to improve rigidity as long as making the wall thickness of the big end of connecting rod, but
It is, if it does, then there are problems that the weight of connecting rod and size increase such.Therefore, if in the linking part shape of connecting rod
Into through hole, and in the uniform wall thickness of the big end that connecting rod is caused at the part of linking part and other parts, then can
Avoiding weight increases, while improving the circularity of ball bearing.
But, even if veing configured as above, because the big end of connecting rod is in the circumferential two ends of through hole this position and company at two
Knot is connected, therefore the rigidity of this position at two is partly improved, and larger press-in reaction force, ball are born in the outer ring of ball bearing
The circularity of bearing is still possible to be damaged.
The content of the invention
The present invention is to complete in view of the foregoing, its object is to by the weight of the connecting rod of power transmission apparatus for vehicle
Amount increases and suppresses in minimum limit, while ensuring the circularity of bearing being pressed into the big end of the connecting rod.
In order to achieve the above object, the invention according to technical scheme 1, it is proposed that a kind of vehicle is transmitted with power and filled
Put, it possesses：Input shaft, it is connected with driving source；Output shaft, it is abreast configured with the input shaft；Swing rod, it is with can
The mode of swing is supported on the output shaft；One-way clutch, it is configured between the output shaft and the swing rod, when the pendulum
One-way clutch engagement when bar swings to a direction, when the swing rod swings in the other direction, the one-way clutch is released
Engagement；Eccentric disc, its integratedly eccentric rotary with the input shaft；Shifting actuator, the offset of its change eccentric disc；
And connecting rod, it connects the eccentric disc and described swing rod, and the power transmission apparatus for vehicle is characterised by, the connecting rod
Possess：The big end of ring-type, it is pressed on the bearing of the outer peripheral face of the eccentric disc；Small end, itself and the pendulum
Bar is connected；And linking part, it links the big end and the small end, wherein, it is formed with insertion axle in the linking part
To two through holes on surface, constitute the inner edge portion of the described big end that the through hole is faced circular arc center relative to
The center of the outer peripheral face of the big end is to the small end lateral deviation heart.
In addition, the invention according to technical scheme 2, it is proposed that a kind of power transmission apparatus for vehicle, it is characterised in that
On the basis of the structure of technical scheme 1, the outer edge of the linking part is in the outer peripheral face phase on secant-shaped ground and the big end
Even.
Also, the correspondence bearing of the invention of ball bearing 20 of implementation method, the engine E correspondences of implementation method are of the invention
Driving source.
According to the structure of technical scheme 1, when the input shaft being connected with driving source rotates, big end is connected to and input shaft
Integratedly the connecting rod on the eccentric disc of eccentric rotary is moved back and forth, and the swing rod being connected with the small end of connecting rod is carried out toward physical pendulum
It is dynamic.When swing rod swings to a direction, one-way clutch engagement, when swing rod swings in the other direction, one-way clutch
Debonding, therefore, the reciprocating motion of connecting rod be converted into output shaft to the rotary motion in direction.Caused when using speed change
When dynamic device changes the offset of eccentric disc, the reciprocating stroke of connecting rod changes so as to the angle of oscillation of swing rod becomes
Change, therefore, input shaft be rotated in speed change after be passed to output shaft.
Connecting rod possesses：The big end of ring-type, it is pressed on the bearing of the outer peripheral face of eccentric disc；Small end, its
It is connected with swing rod；And linking part, it links big end and small end, therefore, the rigidity of the big end of connecting rod with linking part
The part of connection is partly improved, when the big end of connecting rod is pressed on bearing, due to being pressed into the unbalanced of reaction force,
There is bearing flexure, circularity reduction.
But, insertion axially two through holes on surface are formed with the linking part of connecting rod, constitute what through hole was faced
The center of the outer peripheral face of the center relative to big end of the circular arc of the inner edge portion of big end to the small end lateral deviation heart, therefore, pass through
Big end is set to be connected with linking part at the circumferential two ends of through hole, and the vicinity of position makes big end at two for rigidly improving
Radial thickness is reduced and it is rigidly reduced, and the rigidity thus, it is possible to prevent big end drastically changes in a circumferential direction, makes pressure
Enter reaction force gently to change in a circumferential direction, so as to improve the circularity of bearing.And, it is on the whole thickness with big end is made
Wall is compared improving the situation of the circularity of bearing, can be suppressed in Min. the increase of the weight of connecting rod and size.
In addition, according to the structure of technical scheme 2, due to the outer peripheral face of the outer edge in secant-shaped with big end of linking part
It is connected, therefore, it is possible to the change of the radial thickness at the part that big end and linking part are connected of connecting rod is suppressed into minimum
Limit, the press-in reaction force that bearing can be made to be born from big end is more uniform in circumferencial direction, so as to further improve axle
The circularity held.
Brief description of the drawings
Fig. 1 is the skeleton drawing of power transmission apparatus for vehicle.
Fig. 2 is the detailed figure of 2 of Fig. 1.
Fig. 3 is along the sectional view (OD states) of the 3-3 lines of Fig. 2.
Fig. 4 is along the sectional view (GN states) of the 3-3 lines of Fig. 2.
Fig. 5 is the Action Specification figure under OD states.
Fig. 6 is the Action Specification figure under GN states.
Fig. 7 is the figure of the shape of the connecting rod for representing implementation method.
Fig. 8 is the curve map of the load distribution of the ball bearing for representing implementation method.
Fig. 9 is the figure of the shape of the connecting rod for representing comparative example.
Figure 10 is the curve map of the load distribution of the ball bearing for representing comparative example.
Label declaration
11：Input shaft；
12：Output shaft；
13：Swing rod；
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：Engine (driving source)
Ea：The inner edge portion of the big end that through hole is faced；
Eb：The outer edge of linking part；
Ob：The center of the outer peripheral face of big end；
Oc：Constitute the center of the circular arc of the inner edge portion of the big end that through hole is faced；
Pb：The outer peripheral face of big end.
Specific embodiment
Below, embodiments of the present invention are illustrated based on Fig. 1~Figure 10.
As shown in figure 1, the driving force of engine E is used by the vehicle that the axletree 10,10 of left and right is transferred to driving wheel W, W
Power transmission possesses crank-type buncher T and differential mechanism D.
Next, being based on Fig. 2~Fig. 6, the structure to buncher T is illustrated.
As shown in Figures 2 and 3, the buncher T of present embodiment is that will have mutually isostructural multiple (in embodiment party
It is 4 in formula) power transfer unit U axially overlaps, and these power transfer units U possesses sharing of abreast configuring
Input shaft 11 and shared output shaft 12, being rotated in for input shaft 11 be decelerated or be transferred to after accelerating output shaft 12.
Hereinafter, as representative, the structure to a power transfer unit U is illustrated.It is connected and rotates with engine E
The hollow rotary shaft 14a of shifting actuator 14 as insertion electro-motor in the way of rotating against freely of input shaft 11
It is 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 same speed of input shaft 11, and can be relative at different rates relative to input shaft 11
Rotation.
The 1st little gear 15, the row of crank-like are fixed with the input shaft 11 of the rotary shaft 14a of insertion shifting actuator 14
Carrier 16 is connected to the rotary shaft 14a of shifting actuator 14 in the way of across the 1st little gear 15.Diameter and the 1st little gear
The little gear 17,17 of 15 identical two the 2nd is supported in the structure that cooperated with the 1st little gear 15 by pinion pin 16a, 16a respectively
Into the position of equilateral triangle, gear ring 18a is engaged with these the 1st little gears 15 and the 2nd little gear 17,17, and the gear ring 18a is with inclined
The mode of the heart 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.
Ball bearing 20 to be embedded in the periphery of eccentric disc 18 by way of rotating against freely, small end 19b passes through pin to big end 19a
26 are supported on a pivot on swing rod 13, and the swing rod 13 is supported on the periphery of output shaft 12 in the way of it can swing.
The one-way clutch 21 configured between output shaft 12 and swing rod 13 possesses：The exterior part 22 of ring-type, it is pressed into
To the inner peripheral surface of swing rod 13；Output shaft 12 is simultaneously fixed in inner part 23, its inside for being configured at exterior part 22；And roller 25,
It is configured in the space of the wedge-like formed between exterior part 22 and inner part 23, and engaged spring 24 exerts a force.
Can be clear and definite according to Fig. 2,4 power transfer unit U have the planet carrier 16 of crank-like jointly, by the 2nd small tooth
The phase of the eccentric disc 18 that wheel 17,17 is supported on planet carrier 16 differs 90 ° respectively in each power transfer unit U.For example,
In fig. 2, the eccentric disc 18 of the power transfer unit U of left end is displaced to top in figure relative to input shaft 11, since left
3rd eccentric disc 18 of power transfer unit U is displaced to lower section, the 2nd and the 4th since left in figure relative to input shaft 11
The eccentric disc 18,18 of individual power transfer unit U, U is located at the centre of above-below direction.
The shape of connecting rod 19 is schematically shown in Fig. 1~Fig. 6, but, based on Fig. 7 to the true form of connecting rod 19
It is described in detail.
The inner peripheral surface Pa and radius that there is the big end 19a of the connecting rod 19 of implementation method radius to be Ra are the Rb bigger than Ra
The center Ob of outer peripheral face Pb, the center Oa relative to inner peripheral surface Pa, outer peripheral face Pb is to small end 19b sides offset distances a.Therefore,
The radial thickness of big end 19a is uneven in a circumferential direction, and wall thickness is small in the side away from small end 19b, and wall thickness is being close to
The side of small end 19b is big.
In the center of the linking part 19c of triangle, the through hole 19d of triangle is formed with, the through hole 19d is passed through
Lead to axially two surfaces of bar 19, the inner edge portion Ea of the big end 19a that through hole 19d is faced is by with from outer peripheral face Pb
Heart Ob is to Oc, the circular arc composition that radius is Rc centered on the point of the further offset distance b in small end 19b sides.Through hole 19d institutes
The radius Rc of the inner edge portion Ea for facing is set to smaller than the radius Rb of the outer peripheral face Pb of big end 19a.As a result, through hole
The radial thickness t of the inner edge portion Ea that 19d is faced is big in the circumferential center of inner edge portion Ea, circumferential small in ends.
Linking part 19c possesses two outer edges Eb, Eb, and the two outer edges Eb, Eb is from small end 19b sides towards big end
19a sides are expanded while extending, outer edge Eb, Eb are connected in secant-shaped ground with the outer peripheral face Pb of big end 19a.
And Fig. 9 represents the connecting rod 19 of comparative example.In the connecting rod 19 of comparative example, the big end that through hole 19d is faced
The inner edge portion Ea of 19a is had center Ob, radius by the outer peripheral face Pb with big end 19a for the circular arc of Rc' is constituted jointly, insertion
The radius Rc' of the inner edge portion Ea of hole 19d is set to the radius Rb small distances c than the outer peripheral face Pb of big end 19a.Its result
It is that the radial thickness t of the inner edge portion Ea that through hole 19d is faced keeps fixed throughout the circumferential.
Next, the effect to the embodiments of the present invention for possessing said structure is illustrated.
First, the effect to a power transfer unit U of buncher T is illustrated.If making shifting actuator
14 rotary shaft 14a is rotated against relative to input shaft 11, then planet carrier 16 rotates around the axis L1 of input shaft 11.Now, OK
The center O of carrier 16, the center of the equilateral triangle being made up of the 1st little gear 15 and two the 2nd little gears 17,17 are around input shaft
11 axis L1 rotations.
Fig. 3 and Fig. 5 represent the center O of planet carrier 16 relative to the 1st little gear 15 (i.e. input shaft 11) positioned at output
The state of the opposite side of axle 12, now, eccentric disc 18 becomes maximum relative to the offset of input shaft 11, buncher T
Gear ratio be changed into minimum OD states.The center O that Fig. 4 and Fig. 6 represent planet carrier 16 is (i.e. defeated relative to the 1st little gear 15
Enter axle 11) positioned at the state with the identical side of output shaft 12, now, eccentric disc 18 is changed into relative to the offset of input shaft 11
Minimum, the gear ratio of buncher T is changed into infinitely great GN (geared neutral) state.
Under the OD states shown in Fig. 5, if using engine E make input shaft 11 rotate and with the identical of input shaft 11
Speed rotates the rotary shaft 14a of shifting actuator 14, then input shaft 11, rotary shaft 14a, planet carrier 16, the 1st little gear 15,
Two the 2nd little gears 17,17 and eccentric disc 18 in the state of being integrally formed centered on input shaft 11 in the counterclockwise direction
(reference arrow A) carries out eccentric rotary.During being rotated to the state of Fig. 5 (C) by Fig. 5 (B) from Fig. 5 (A), big end
19a makes swing rod 13 along the inverse time ball bearing 20 to be supported on the connecting rod 19 of the periphery of eccentric disc 18 by way of rotating against freely
Pin direction (reference arrow B) swings, and the swing rod 13 is supported on a pivot on the small end 19b of connecting rod 19 by pin 26.Fig. 5 (A) and
Fig. 5 (C) represents the two ends that swing rod 13 swings along the arrow B directions.
So, when swing rod 13 swings along arrow B directions, exterior part 22 and the inside of the engaging-in one-way clutch 21 of roller 25
In the space of the wedge-like between part 23, so as to the rotation of exterior part 22 is transferred into output shaft 12 by inner part 23, therefore, it is defeated
(reference arrow C) rotation in the counterclockwise direction of shaft 12.
If the little gear 15 of input shaft 11 and the 1st is further rotated, gear ring 18a and the 1st little gear 15 and the 2nd little gear
17th, (reference arrow A) carries out eccentric rotary to the eccentric disc 18 of 17 engagements in the counterclockwise direction.From Fig. 5 (C) by Fig. 5 (D) to
During the state of Fig. 5 (A) rotates, big end 19a is ball bearing 20 being supported on eccentric disc by way of rotating against freely
The connecting rod 19 of 18 periphery makes swing rod 13, and (reference arrow B') swings along clockwise direction, and the swing rod 13 passes through the pivot branch of pin 26
Hold the small end 19b in connecting rod 19.Fig. 5 (C) and Fig. 5 (A) represent the two ends that swing rod 13 swings along the arrow B' directions.
So, when swing rod 13 swings along arrow B' directions, the one side of 25 one side compressive engagement spring of roller 24 is from exterior part
It is pushed out in the space of the wedge-like between 22 and inner part 23, thus, exterior part 22 skids relative to inner part 23, output shaft 12
Do not rotate.
As described above, when 13 reciprocally swinging of swing rod, only when the swaying direction of swing rod 13 is for counterclockwise (with reference to arrow
Head B) when, (reference arrow C) rotates output shaft 12 in the counterclockwise direction, therefore output shaft 12 is rotated intermittently.
Fig. 6 is the figure of effect when showing to operate buncher T under GN states.Now, due to the position of input shaft 11
Put consistent with the center of eccentric disc 18, therefore eccentric disc 18 is zero relative to the offset of input shaft 11.If in this condition
Input shaft 11 is rotated using engine E, and revolve the rotary shaft 14a of shifting actuator 14 with the same speed of input shaft 11
Turn, then input shaft 11, rotary shaft 14a, planet carrier 16,15, two the 2nd little gears 17,17 of the 1st little gear and eccentric disc 18 exist
In the state of being integrally formed, (reference arrow A) carries out eccentric rotary in the counterclockwise direction centered on input shaft 11.But, by
It is zero in the offset of eccentric disc 18, therefore the reciprocating stroke of connecting rod 19 is also zero, output shaft 12 does not rotate.
Therefore, if driving shifting actuator 14 and the position of planet carrier 16 being set in the OD states of Fig. 3 and the GN of Fig. 4
Between state, then the operating under any gear ratio between infinitely great gear ratio and predetermined gear ratio can be realized.
In buncher T, the phase of 4 eccentric discs of power transfer unit U 18 being set up in parallel offsets one from another
90 °, therefore, 4 power transfer unit U alternately transmit in the one-way clutch of driving force, i.e., 4 21 any one necessarily locate
In engagement state, thus enable that output shaft 12 continuously rotates.
But, when the outer peripheral face of ball bearing 20 to be 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 bears to be radially oriented the press-in reaction force of inner side and deform.Now, if being radially oriented inner side
Press-in reaction force it is uniform in a circumferential direction, then may insure the circularity of the ball bearing 20 after press-in, but actually big end
The rigidity of portion 19a is uneven in circumferencial direction, the vicinity of the part connected in big end 19a and linking part 19c, and rigidity is partly
Improve, deform because of loading of pressing in accordingly, there exist ball bearing 20, so that the such problem of circularity reduction.
Figure 10 is the curve map of load distribution that bears of ball of the ball bearing 20 for representing the comparative example shown in Fig. 9, and it is horizontal
Axle represents and for the side farthest from small end 19b of ball bearing 20 to be set to θ=0 °, the circle measured in the counterclockwise direction from this
Circumferential direction position.In the range of the scope of 90 ° of 0 °≤θ ＜ and 270 ° of ＜ θ≤360 °, load is zero, 90 °≤θ≤270 °
In the range of produce load, but near θ=135 ° and θ=225 ° nearby this at two on position, generation peak load.
Its reason be put on the compressive load of connecting rod 19 from big end 19a via linking part 19c two outer edges
Eb, Eb are transferred to small end 19b, but in the root (i.e. the vicinity of the vicinity of θ=135 ° and θ=225 °) of outer edge Eb, Eb, greatly
The rigidity of end 19a is partly improved, and the peak load of double-peak type is generated in the part.Thus, if double-peak type can be reduced
Peak load, then the circularity of ball bearing 20 can be improved, so as to further improve durability.
Fig. 8 is the curve map of the load distribution of the ball bearing 20 for representing the implementation method shown in Fig. 7, it is known that shown in Figure 10
The peak load of the double-peak type of comparative example almost disappears, as the flat load distribution smaller than the peak load.
Its reason is, the inner edge portion Ea of the big end 19a that through hole 19d is faced from from the center Ob of outer peripheral face Pb to
Oc, the circular arc composition that radius is Rc centered on the point of the further offset distance b in small end 19b sides, therefore, through hole 19d institutes
The radial thickness t of the inner edge portion Ea for facing is small in ends in the circumference of inner edge portion Ea, outer edge Eb, Eb of connecting rod 19 with big end
The rigidity of the continuous roots of 19a is partly reduced, and thus the peak load of double-peak type disappears.
As described above, according to present embodiment, making while the weight of connecting rod 19 is increased and suppressed in Min. big
The rigidity of end 19a is uniform in a circumferential direction, and makes the load of the ball bearing 20 of the big end 19a of supporting equal in a circumferential direction
It is even such that it is able to reduce frictional force and improve durability.
In addition, linking part 19c possesses two outer edges Eb, Eb, the two outer edges Eb, Eb is from small end 19b sides direction
Big end 19a sides expand mutually while extending, outer edge Eb, Eb connect in secant-shaped ground with the outer peripheral face Pb of big end 19a on one side
Connect, the radial thickness t therefore, it is possible to prevent big end 19a drastically changes in the root of outer edge Eb, Eb such that it is able to enter one
Step improves the circularity of ball bearing 20.
Embodiments of the present invention are illustrated above, but the present invention can enter not departing from the range of its main points
The various design alterations of row.
For example, in embodiments, the outer peripheral faces of the center Oa relative to big end 19a of the inner peripheral surface Pa of big end 19a
The center Ob of Pb is eccentric, and Dan Liangge centers Oa, Ob can also be consistent.
In addition, bearing of the invention is not limited to the ball bearing 20 of implementation method, can be needle bearing, roller axle
Hold, the arbitrary bearing such as sliding bearing.
In addition, driving source of the invention is not limited to engine E, or motor generator of implementation method etc. appointing
The driving source of meaning.
Claims (2)
1. a kind of power transmission apparatus for vehicle, it possesses：
Input shaft (11), it is connected with driving source (E)；
Output shaft (12), it is abreast configured with the input shaft (11)；
Swing rod (13), it is supported on the output shaft (12) in the way of it can swing；
One-way clutch (21), it is configured between the output shaft (12) and the swing rod (13), when the swing rod (13) is to one
The one-way clutch (21) engagement, the one-way clutch when the swing rod (13) swings in the other direction when individual direction swings
(21) debonding；
Eccentric disc (18), its integratedly eccentric rotary with the input shaft (11)；
Shifting actuator (14), the offset of its change eccentric disc (18)；And
Connecting rod (19), its connection eccentric disc (18) and described swing rod (13),
The power transmission apparatus for vehicle is characterised by,
The connecting rod (19) possesses：The big end (19a) of ring-type, it is pressed into the outer peripheral face located at the eccentric disc (18)
On bearing (20)；Small end (19b), it is connected with the swing rod (13)；And linking part (19c), it links the big end
(19a) and the small end (19b),
Insertion axially two through holes on surface (19d) are formed with the linking part (19c), the through hole (19d) is constituted
The center (Oc) of the circular arc of the inner edge portion (Ea) of the described big end (19a) for being faced is outer relative to the big end (19a)
The inner edge portion that the center (Ob) of side face (Pb) is faced to the small end (19b) the lateral deviation heart, the through hole (19d)
(Ea) radial thickness (t) is big in the circumferential center of the inner edge portion (Ea), circumferential small in ends.
2. power transmission apparatus for vehicle according to claim 1, it is characterised in that
The outer edge (Eb) of the linking part (19c) is connected in secant-shaped ground with the outer peripheral face (Pb) of the big end (19a).
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2014-020081 | 2014-02-05 | ||
| JP2014020081A JP6168523B2 (en) | 2014-02-05 | 2014-02-05 | Power transmission device for vehicle |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN104816629A CN104816629A (en) | 2015-08-05 |
| CN104816629B true CN104816629B (en) | 2017-07-04 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201510052523.5A Expired - Fee Related CN104816629B (en) | 2014-02-05 | 2015-02-02 | Power transmission apparatus for vehicle |
Country Status (2)
| Country | Link |
|---|---|
| JP (1) | JP6168523B2 (en) |
| CN (1) | CN104816629B (en) |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP6208790B2 (en) * | 2016-02-29 | 2017-10-04 | 本田技研工業株式会社 | Power transmission device for vehicle |
| CN110104156A (en) * | 2019-05-17 | 2019-08-09 | 王朋 | Shake big shield ship |
| CN110966367B (en) * | 2019-12-06 | 2021-01-15 | 中国科学院深圳先进技术研究院 | Amplitude-adjustable sine mechanism |
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| JP2003322138A (en) * | 2002-04-30 | 2003-11-14 | Ntn Corp | Connecting rod and connecting rod with bearing |
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| US9121483B2 (en) * | 2011-06-30 | 2015-09-01 | Honda Motor Co., Ltd. | Four-joint link type continuously variable transmission |
| CN202500976U (en) * | 2012-03-12 | 2012-10-24 | 周有强 | Connecting-rod tooth-engaging type speed reducing and changing device |
| JP6011971B2 (en) * | 2013-02-05 | 2016-10-25 | 本田技研工業株式会社 | Power transmission device for vehicle |
-
2014
- 2014-02-05 JP JP2014020081A patent/JP6168523B2/en not_active Expired - Fee Related
-
2015
- 2015-02-02 CN CN201510052523.5A patent/CN104816629B/en not_active Expired - Fee Related
Also Published As
| Publication number | Publication date |
|---|---|
| JP6168523B2 (en) | 2017-07-26 |
| JP2015148242A (en) | 2015-08-20 |
| CN104816629A (en) | 2015-08-05 |
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Granted publication date: 20170704 |