CN104553741A - Vehicle power transmission device - Google Patents
Vehicle power transmission device Download PDFInfo
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- CN104553741A CN104553741A CN201410528403.3A CN201410528403A CN104553741A CN 104553741 A CN104553741 A CN 104553741A CN 201410528403 A CN201410528403 A CN 201410528403A CN 104553741 A CN104553741 A CN 104553741A
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- plane
- connecting part
- large end
- small end
- fork
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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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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Transmission Devices (AREA)
- Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)
Abstract
The invention provides a vehicle power transmission device. A connecting rod is provided with an annular big end part, a small end part and a connection part. The big end part is pressed in to a bearing arranged on the peripheral face of an eccentric disc. The small end part is connected with a swinging part. The connection part connects the big end part and the small end part and is provided with a shrink neck part and a rib part. The shrink part is arranged to fail to interface with a one-way clutch when the swinging rod swings. The rib part is arranged on the side face on the other side opposite to the side face, formed towards the one-way clutch, of one side of the shrink neck part.
Description
Technical field
The present invention relates to power transmission apparatus for vehicle.
Background technology
Disclose in DE 10 2,009 031 791 A1 specification sheets at German patent application, disclose the power transmission apparatus for vehicle of such structure: be connected with eccentric disk the large end of connecting rod, described eccentric disk rotates integratedly with the input shaft being connected to driving engine, and the small end of connecting rod is connected with output shaft through free-wheel clutch.In this power transmission apparatus for vehicle, the crank motion of the connecting rod produced by the eccentric rotary because of eccentric disk by free-wheel clutch is converted to the unidirectional rotary motion of output shaft.
Fig. 9 A, Fig. 9 B are the figure of the summary of the connecting rod of the power transmission apparatus for vehicle illustrated in the past.Connecting rod 900 possesses large end 903 and small end 905.About the region 910 near small end 905, in order to prevent the interference with free-wheel clutch 920, need to make this region 910 be formed as necking down shape., according to the relative placement of the center Ob of large end 903, the center Os of small end 905 and free-wheel clutch 920, the situation (Fig. 9 A) cannot guaranteeing the bending strength of necking down shape portion fully may be produced.
In addition, bending to avoid and the interference of free-wheel clutch 920 (Fig. 9 B) upward relative to the line of centers C linking center Ob and center Os by making the shape of connecting rod, necking down shape portion 915 can be remained wide cut thus, thus the bending strength of necking down shape portion 915 can be guaranteed., the connecting part 950 linking large end 903 and small end 905 becomes the upper and lower asymmetric structure of line of centers C about linking the center Ob of large the end 903 and center Os of small end 905.Be bent such flexural deformation when being compressed load along with connecting rod 901, the load diatibution suffered by ball (rolling body) supporting the ball-bearing casing of large end 903 becomes uneven.
Figure 10 A, Figure 10 B are the figure that the load diatibution suffered by rolling body of the ball-bearing casing of large end 903 to bearing connecting rod 901 is described.The figure of Figure 10 A to be the figure that the connecting rod 901 illustrated in figures 9 b and 9 is shown, Figure 10 B be relation illustrated between the position of rolling body and the load (sharing load) suffered by each rolling body.
Distance small end 905 position farthest of ball-bearing casing is set to θ=0 ° by the transverse axis of Figure 10 B, and with this position for starting point shows the position (degree) of rolling body counterclockwise.The longitudinal axis of Figure 10 B shows that go out in each position measurement of rolling body, suffered by rolling body load (sharing load: N).Time in the scope that the position of rolling body is in the scope of 0 °≤θ < 90 ° and 270 ° of < θ≤360 °, load is zero, time in the scope that the position of rolling body is in 90 °≤θ≤270 °, create load, but the position that peak load produces is not the position of θ=180 °, but the position of the vicinity of θ=170 °.
This is because: if the shape of connecting rod 901 is symmetrical about line of centers C line, then peak load should produce the position in θ=180 °, but, because the shape of connecting rod 901 is asymmetric about line of centers C, therefore, the rigidity of the antagonism clamp load of connecting rod 901 to uprise and at first half step-down at the lower part of line of centers C, therefore, delivers larger load at the higher lower part of the rigidity of antagonism clamp load (θ=170 ° vicinity).Therefore, the load diatibution suffered by rolling body supporting the ball-bearing casing of large end 903 becomes uneven.
Summary of the invention
The present invention, in view of aforesaid situation, provides a kind of power transmission apparatus for vehicle, and it can guarantee the bending strength of the necking part of connecting rod, and can distribution and transmission is to the load of connecting part equably, and the load diatibution that rolling body is subject to is even.
The power transmission apparatus for vehicle of the 1st aspect of the present invention possesses: input shaft, and it is connected with drive source; Output shaft, itself and described input shaft configure abreast; Fork, it is supported in described output shaft in the mode that can swing; Free-wheel clutch, it is configured between described output shaft and described fork, and when described fork swings to a direction, this free-wheel clutch engages, and when this fork swings in the other direction, this free-wheel clutch is removed and engaged; Eccentric disk, itself and described input shaft eccentric rotary integratedly; Shifting actuator, it changes the offset of described eccentric disk; And connecting rod, it connects described eccentric disk and described fork, and the feature of described power transmission apparatus for vehicle is, described connecting rod possesses: the large end of ring-type, and it is pressed on the bearing that arranges at the outer peripheral face of described eccentric disk; Small end, it is connected with described fork; And connecting part, it links described large end and described small end, and described connecting part possesses: necking part, and it is provided in when described fork swings and does not interfere with described free-wheel clutch; And flank, it is arranged on the side of opposite side relative to the side towards the side that described free-wheel clutch is formed of described necking part.
In addition, 2nd aspect of vehicle according to the invention torque transfer, it is characterized in that, 2nd plane and the 1st plane orthogonal comprising the central axis of described large end and the central axis of described small end, and at described necking part place, described large end and described small end are separated, in the face of described 2nd plane, described necking part and described flank are configured to: the sectional area of the side of described 1st plane is equal with the sectional area of the opposite side of described 1st plane.
In addition, 3rd aspect of vehicle according to the invention torque transfer, it is characterized in that, 3rd plane and the 1st plane orthogonal comprising the central axis of described large end and the central axis of described small end, and with the 2nd plane orthogonal described large end and described small end separated perpendicular to described 1st plane and at described necking part place, and the 3rd plane comprises the center of the center of the outer peripheral face of described large end and the outer peripheral face of described small end, the cross sectional shape of described necking part and described flank is configured to: the shape of the shape of the side of the 3rd plane and the opposite side of the 3rd plane is about described 3rd plane symmetry.
In addition, the 4th aspect of vehicle according to the invention torque transfer, it is characterized in that, described connecting part possesses: through hole, and the line of centers consisted of about linking the center of described large end and the center of described small end is symmetrical; 1st connecting part, it links up between described large end and described necking part; And the 2nd connecting part, it is being formed with the position of described 1st connecting part about described line of centers symmetry, and link up between described large end and described necking part, described through hole is formed between described 1st connecting part and described 2nd connecting part, and the rigidity of described 1st connecting part is configured to the rigid phase of described 2nd connecting part same.
According to the structure of the 1st aspect, the bending strength of the necking part of connecting rod can be guaranteed, and can distribution and transmission is to the load of connecting part equably, the load diatibution that rolling body is subject to is even.
In addition, according to the structure of the 2nd aspect, can distribution and transmission to be to the load of connecting part equably, the load diatibution that rolling body is subject to is even.
In addition, according to the structure of the 3rd aspect, while the generation of thrust suppressing axis, the load transmitted to the 1st connecting part side and the 2nd connecting part side from necking part and flank can be distributed equably.
In addition, according to the structure of the 4th aspect, can distribution and transmission to be to the load of connecting part equably, the load diatibution that rolling body is subject to is even.
Further feature of the present invention becomes obvious by from the following description (with reference to accompanying drawing) carried out exemplary embodiment.
Accompanying drawing explanation
Fig. 1 is the skeleton diagram of power transmission apparatus for vehicle.
Fig. 2 is the details drawing of 2 in Fig. 1.
Fig. 3 is the cutaway view (high (TOP) state) along the 3-3 line in Fig. 2.
Fig. 4 is the cutaway view (low (LOW) state) along the 3-3 line in Fig. 2.
Fig. 5 A-5D is the Action Specification figure under high state.
Fig. 6 A-6D is the Action Specification figure under low state.
Fig. 7 A-7C is the figure of the shape that connecting rod is shown.
Fig. 8 A-8C is the figure be described the load acting on ball-bearing casing.
Fig. 9 A-9B is the figure of the connecting rod of the power transmission apparatus for vehicle illustrated in the past.
Figure 10 A-10B is the figure that the load diatibution be subject to the rolling body of ball-bearing casing is described.
Detailed description of the invention
Below, based on Fig. 1 ~ Fig. 8 A-8C, embodiments of the present invention are described.As shown in Figure 1, the power transmission apparatus for vehicle that the axletree 10,10 of the propulsive effort of the driving engine E as drive source through left and right is passed to drive wheel W, W possessed toric transmission T and the diff D of crank type.
Next, based on Fig. 2 ~ Fig. 6 A-6D, the structure of toric transmission T is described.As shown in Figures 2 and 3, the toric transmission T of present embodiment is by overlapping vertically for multiple (being illustrated the situation of 4 in embodiments) the power transfer unit U with same structure, these power transfer units U possesses the input shaft 11 shared configured abreast and the output shaft 12 shared, and is passed to output shaft 12 after being rotated in of input shaft 11 is decelerated or accelerates.
Below, representatively, the structure of a power transfer unit U is described.To connect with driving engine E and the input shaft 11 rotated runs through the inside of the S. A. 14a of the hollow of the such shifting actuator of electro-motor 14 in relative rotatable mode.The rotor 14b of shifting actuator 14 is fixed on S. A. 14a, and stator 14c is fixed on housing.The S. A. 14a of shifting actuator 14 can rotate with the speed identical with input shaft 11, and relatively can rotate with different speed relative to input shaft 11.
The input shaft 11 of S. A. 14a running through shifting actuator 14 is fixed with the 1st miniature gears 15, and the pinion carrier 16 of crank-like is connected to the S. A. 14a of shifting actuator 14 in the mode of crossing over the 1st miniature gears 15.Diameter 2 2nd miniature gearss 17,17 identical with the 1st miniature gears 15 are supported in cooperate with the 1st miniature gears 15 respectively by miniature gears pin 16a, 16a and are configured to the position of equilateral triangle, gear ring 18a engages with these the 1st miniature gearss 15 and the 2nd miniature gears 17,17, and described gear ring 18a is formed at the inside of the eccentric disk 18 of circular plate type in an eccentric manner.
Connecting rod 19 possesses large end 19a and small end 19b, large end 19a is embedded in the periphery of eccentric disk 18 in relatively rotatable mode through ball-bearing casing 20, small end 19b sells 26 and is supported on a pivot on fork 13, and described fork 13 is supported on the periphery of output shaft 12 in the mode that can swing.
The free-wheel clutch 21 be configured between output shaft 12 and fork 13 possesses: the exterior part 22 of ring-type, and it is pressed into the inner peripheral surface of fork 13; Inner component 23, it is configured at the inside of exterior part 22 and is fixed on output shaft 12; Roller 25, it is configured at the space of the wedge-like formed between exterior part 22 and inner component 23, and engaged spring 24 exerts a force.When fork 13 swings to a direction, free-wheel clutch 21 engages, and when fork 13 swings in the other direction, free-wheel clutch 21 is removed and engaged.
As shown in Figure 2,4 power transfer unit U have the pinion carrier 16 of crank-like jointly, and the phase place being supported on the eccentric disk 18 of pinion carrier 16 through the 2nd miniature gears 17,17 differs 90 ° respectively in each power transfer unit U.Such as, in fig. 2, the eccentric disk 18 of the power transfer unit U of left end is displaced to top in figure relative to input shaft 11, the eccentric disk 18 of the 3rd power transfer unit U from left is displaced to Figure below relative to input shaft 11, and the eccentric disk 18,18 of the 2nd and the 4th power transfer unit U, U from left is positioned at the centre of above-below direction.
Further, in Fig. 1 ~ Fig. 6 A-6D, the shape of connecting rod 19 is schematically shown, but, about the shape of connecting rod 19, be described in detail based on Fig. 7 A-7C, Fig. 8 A-8C.
Fig. 7 A is the figure of the shape that the connecting rod 19 that embodiment relates to is shown.Connecting rod 19 possesses: the large end 19a of ring-type, and it is pressed on the ball-bearing casing 20 that arranges at the outer peripheral face of eccentric disk 18; Small end 19b, it is connected with fork 13; And connecting part, it links large end 19a and small end 19b.At this, connecting part possesses: necking part 19c, and it is provided in when fork 13 swings and does not interfere with free-wheel clutch 21; Flank 19d, it is strengthened the bending strength of necking part 19c; And the 1st connecting part 19e and the 2nd connecting part 19f, they link necking part 19c and large end 19a.Flank 19d is arranged on the side of the upper side of necking part 19c relative to free-wheel clutch.That is, flank 19d is arranged on the side of opposite side relative to the side towards the side that free-wheel clutch is formed of necking part 19c.
As shown in Figure 7 A, the 1st connecting part 19e and the 2nd connecting part 19f symmetrical (line is symmetrical) is formed up and down about line of centers C.In addition, the through hole 19h (peristome) of general triangular is formed in the inner side of the 1st connecting part 19e and the 2nd connecting part 19f.Through hole 19h is formed as: upper side and the lower side of crossing over line of centers C, and along the periphery of large end 19a.In addition, through hole 19h symmetrical (line is symmetrical) is formed up and down about line of centers C.1st connecting part 19e is formed in the upper side of through hole 19h, and the 2nd connecting part 19f is formed in the lower side of through hole 19e.
Rigidity and the rigidity of the 2nd connecting part 19f of the 1st connecting part 19e are configured to identical respectively.Rigidity such as can be obtained by the product of the elasticity modulus that forms the material of connecting rod 19 and the cross sectional moment of inertia determined according to the cross sectional shape of each connecting part.Because elasticity modulus can obtain as the characteristic value that material is intrinsic, therefore, in order to the rigid phase of the rigidity and the 2nd connecting part 19f that make the 1st connecting part 19e is same, as long as in the mode making cross sectional moment of inertia identical to determine both cross sectional shapes.Like this, by the rigidity of the 1st connecting part 19e is set identical with the rigidity of the 2nd connecting part 19f, 1st connecting part 19e and the 2nd connecting part 19f can share the load putting on connecting rod 19 equably, thereby, it is possible to make the load of sharing of the rolling body of the ball-bearing casing 20 of supporting large end 19a become even.
Fig. 7 B is the amplification stereogram of the structure that small end 19b, necking part 19c and flank 19d are shown.As shown in Figure 7 B, the upper side side of necking part 19c and lower side side are configured to arc-shaped.The flank 19d of tabular is provided with in the upper side side of necking part 19c.
Fig. 7 C be from the direction of arrow observe the AA cross section of Fig. 7 A, illustrative figure is carried out to the cross sectional shape of necking part 19c and flank 19d.In fig. 7 c, plane P is by the central axis of the center Ob of the outer peripheral face by large end 19a (central axis of large end 19a) and the plane that is included in by the central axis (central axis of small end 19b) of the center Os of the outer peripheral face of small end 19b in same plane.Flank 19d is located at the upper side side of necking part 19c relative to plane P.Like this, arrange flank 19d by the upper side side at necking part 19c, the load putting on connecting rod 19 is distributed by flank 19d and necking part 19c, therefore, it is possible to realize the raising of the bending strength of necking part 19c.
The AA cross section of Fig. 7 C is vertical with the plane P (the 1st plane) the large central axis of end 19a and the central axis of small end 19b are included in same plane and plane that is that separated by large end 19a and small end 19b at necking part 19c place (the 2nd plane).In the face in AA cross section, the sectional area of necking part 19c and flank 19d is divided into lower side (opposite side) these two parts of the upper side of plane P (side) and plane P.Necking part 19c and flank 19d is configured to: the sectional area of the sectional area of the side of plane P and the opposite side of plane P is equal.The width W 1 of flank 19d and the width W 2 of height H 1 and necking part 19c and height H 2 is formed in the mode that the sectional area A2 of the lower side (opposite side) of the sectional area A1 of the upper side of plane P (side) and plane P is equal.Formed necking part 19c and flank 19d by the mode equal with the sectional area of the lower side (opposite side) of the upper side of plane P (side) and plane P, the load transmitted to the 1st connecting part 19e and the 2nd connecting part 19f side from necking part 19c and flank 19d can be distributed thus equably.By transmitting loading equably to the 1st connecting part 19e and the 2nd connecting part 19f side, thereby, it is possible to make the distribution of the load put on the rolling body of ball-bearing casing 20 become even.
The plane B of Fig. 7 C is such plane (the 3rd plane): it is vertical with comprising the plane P of the large central axis of end 19a with the central axis of small end 19b (the 1st plane), and with perpendicular to plane P (the 1st plane) and at necking part 19c place, large end 19a is vertical with the plane that small end 19b separates (AA cross section: the 2nd plane), and described plane B comprises the center Os of the center Ob of the outer peripheral face of large end 19a and the outer peripheral face of small end.The cross sectional shape of connecting rod 19 on AA cross section is symmetrical about plane B.That is, the cross sectional shape of necking part 19c and flank 19d is configured to: the symmetrical shape (symmetrical) of the shape of the side of plane B (centre plane) and the opposite side of plane B (centre plane).Like this, by making the cross sectional shape of necking part 19c and flank 19d symmetrical, the generation of the thrust of left and right directions (direction of principal axis) can be suppressed thus.While the generation suppressing thrust, the load transmitted to the 1st connecting part 19e and the 2nd connecting part 19f side from necking part 19c and flank 19d can be distributed equably.The distribution putting on the load on the rolling body of ball-bearing casing 20 also becomes even, thus can reduce the friction of the rolling body that the impact because of thrust causes.
Next, the effect of the embodiments of the present invention possessing said structure is described.First, the effect of a power transfer unit U of toric transmission T is described.If make the S. A. 14a of shifting actuator 14 relatively rotate relative to input shaft 11, then pinion carrier 16 rotates around the axis L1 of input shaft 11.Now, the center of center O, i.e. the 1st miniature gears 15 of pinion carrier 16 and the equilateral triangle of two the 2nd miniature gears 17,17 formations rotates around the axis L1 of input shaft 11.
The center O that Fig. 3 and Fig. 5 A-5D shows pinion carrier 16 is positioned at the state of the side contrary with output shaft 12 relative to the 1st miniature gears 15 (i.e. input shaft 11), now, eccentric disk 18 becomes maximum relative to the offset of input shaft 11, and the converter speed ratio of toric transmission T becomes high state.The center O that Fig. 4 with Fig. 6 A-6D shows pinion carrier 16 is positioned at the state of the side identical with output shaft 12 relative to the 1st miniature gears 15 (i.e. input shaft 11), now, eccentric disk 18 becomes minimum relative to the offset of input shaft 11, and the converter speed ratio of toric transmission T becomes low state.
Under the high state shown in Fig. 5 A-5D, if make input shaft 11 rotate by driving engine E and make with the speed identical with input shaft 11 the S. A. 14a of shifting actuator 14 rotate, then input shaft 11, S. A. 14a, pinion carrier 16, the 1st miniature gears 15, two the 2nd miniature gearss 17,17 and eccentric disk 18 carry out eccentric rotary becoming under the state that is integrated centered by input shaft 11 (reference arrow A) counterclockwise.From Fig. 5 A through state from Fig. 5 B to Fig. 5 C rotate during, large end 19a is made fork 13 (reference arrow B) swing counterclockwise through ball-bearing casing 20 by the connecting rod 19 being relatively rotatably freely supported on the periphery of eccentric disk 18, and described fork 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 shows the two ends of the swing along arrow B direction of fork 13.
Like this, when fork 13 swings along arrow B direction, the space of the wedge-like between the exterior part 22 of the engaging-in free-wheel clutch 21 of roller 25 and inner component 23, thus the inner component 23 that is rotated through of exterior part 22 is passed to output shaft 12, therefore, output shaft 12 (reference arrow C) rotation counterclockwise.
If input shaft 11 and the 1st miniature gears 15 further rotate, then make eccentric disk 18 (reference arrow A) eccentric rotary counterclockwise that gear ring 18a engages with the 1st miniature gears 15 and the 2nd miniature gears 17,17.From Fig. 5 C through state from Fig. 5 D to Fig. 5 A rotate during, large end 19a is made fork 13 (reference arrow B') swing clockwise through ball-bearing casing 20 by the connecting rod 19 being relatively rotatably freely supported on the periphery of eccentric disk 18, and described fork 13 is supported on a pivot on the small end 19b of connecting rod 19 by pin 26.Fig. 5 C and Fig. 5 A shows the two ends of the swing along arrow B ' direction of fork 13.
Like this, when fork 13 swings along arrow B ' direction, roller 25 compressive engagement spring 24, while released by the space from the wedge-like between exterior part 22 and inner component 23, makes exterior part 22 skid relative to inner component 23 thus, and output shaft 12 non rotating.
As described above, when fork 13 reciprocally swinging, output shaft 12 (reference arrow C) rotation just counterclockwise when only having the swaying direction when fork 13 to be anticlockwise direction (reference arrow B), therefore, output shaft 12 intermittent rotary.
Fig. 6 A-6D is the figure of the effect illustrated when operating toric transmission T in the low regime.Now, because the position of input shaft 11 is consistent with the center of eccentric disk 18, therefore eccentric disk 18 is zero relative to the offset of input shaft 11.If make input shaft 11 rotate by driving engine E in this condition and make with the speed identical with input shaft 11 the S. A. 14a of shifting actuator 14 rotate, then input shaft 11, S. A. 14a, pinion carrier 16, the 1st miniature gears 15, two the 2nd miniature gearss 17,17 and eccentric disk 18 carry out eccentric rotary becoming under the state that is integrated centered by input shaft 11 (reference arrow A) counterclockwise., the offset due to eccentric disk 18 is zero, and therefore the reciprocating stroke of connecting rod 19 is also zero, output shaft 12 non rotating.
Therefore, if drive shifting actuator 14 to be set between the high state of Fig. 3 and the low state of Fig. 4 by the position of pinion carrier 16, then the running under any converter speed ratio between zero converter speed ratio and predetermined converter speed ratio can be realized.
In toric transmission T, the phase place of the eccentric disk 18 of 4 the power transfer unit U be set up in parallel staggers mutually 90 °, therefore, 4 power transfer unit U alternately transmission of drive force, namely any one in 4 free-wheel clutchs 21 must be in engagement state, can make output shaft 12 continuous rotation thus.
Fig. 8 A-8C is to when connecting rod transfers a driving force to output shaft 12 along with the rotation of input shaft 11 as above, the figure that the load diatibution suffered by rolling body of the ball-bearing casing 20 of the large end 19a of bearing connecting rod 19 is described.
Fig. 8 A is the figure that the connecting rod 19 involved by embodiment illustrated in Fig. 7 A-7C is shown, Fig. 8 B is the figure of the relation illustrated between the position of the rolling body that embodiment relates to and the load (sharing load) suffered by each rolling body.Be configured to, make the sectional area A2 of the lower side (opposite side) of the sectional area A1 of the upper side of plane P (side) and plane P equal.
The distance small end 19b position farthest of ball-bearing casing is set to θ=0 ° by the transverse axis of Fig. 8 B, and with this position for starting point shows the position (degree) of rolling body clockwise.The longitudinal axis of Fig. 8 B shows that go out in each position measurement of rolling body, suffered by rolling body load (sharing load: N).When being in the scope of the scope of 0 °≤θ < 90 ° and 270 ° of < θ≤360 ° in the position of rolling body, load is zero.When being in the scope of 90 °≤θ≤270 ° in the position of rolling body, produce load, but, centered by θ=180 ° roughly from θ=140, ° peak load produced to the scope of 220 ° demonstrates the load diatibution of approximate equality.
If will be dispensed to the load of the 1st connecting part 19e as f1, will be dispensed to the load of the 2nd connecting part 19f as f2, then the pass between the load of distributing is f1=f2.According to the present embodiment, the load F putting on connecting rod 19 can be distributed equably relative to the 1st connecting part 19e and the 2nd connecting part 19f, thereby, it is possible to make the load of sharing of the rolling body of the ball-bearing casing 20 of supporting large end 19a become even.
Fig. 8 C be as comparative example show the sectional area A2 of the sectional area A1 of the upper side of plane P and lower side inconsistent when rolling body position and share the figure of the relation between load.When being in the scope of the scope of 0 °≤θ < 90 ° and 270 ° of < θ≤360 ° in the position of rolling body, load is zero, but produce peak load near θ=140 °, load diatibution does not become equalization as Fig. 8 B.This is because, the pass of sectional area is the sectional area A2 of the sectional area A1 > lower side of the upper side of plane P, from comprise flank 19d, that load that sectional area A1 side direction the 1st connecting part 19e side of the upper side of plane P is distributed becomes the load of distributing than sectional area A2 side direction the 2nd connecting part 19f of side is from below many.
According to the present embodiment, the bending strength of the necking part of connecting rod can be guaranteed, and can distribution and transmission is to the load of connecting part equably, the load diatibution that rolling body is subject to is even.
Above, embodiments of the present invention are illustrated, but the present invention can carry out various design modification in the scope not departing from its main points.
Such as, bearing of the present invention is not limited to the ball-bearing casing 20 of embodiment, can be the arbitrary bearing such as needle bearing, cylindrical bearing, plain bearing.In addition, the connecting rod 19 of embodiment carrys out transmission of drive force by clamp load, but also can carry out transmission of drive force by tensile load.
Although invention has been described for the embodiment of reference example, should be understood that the present invention is not limited to disclosed exemplary embodiment.The scope of following claim will be given the widest explanation thus comprise all amendments, equivalent structure and function.
Claims (4)
1. a power transmission apparatus for vehicle, this power transmission apparatus for vehicle possesses:
Input shaft, it is connected with drive source;
Output shaft, itself and described input shaft configure abreast;
Fork, it is supported in described output shaft in the mode that can swing;
Free-wheel clutch, it is configured between described output shaft and described fork, and when described fork swings to a direction, this free-wheel clutch engages, and when this fork swings in the other direction, this free-wheel clutch is removed and engaged;
Eccentric disk, itself and described input shaft eccentric rotary integratedly;
Shifting actuator, it changes the offset of described eccentric disk; With
Connecting rod, it connects described eccentric disk and described fork,
The feature of described power transmission apparatus for vehicle is,
Described connecting rod possesses:
The large end of ring-type, it is pressed on the bearing that arranges at the outer peripheral face of described eccentric disk;
Small end, it is connected with described fork; With
Connecting part, it links described large end and described small end,
Described connecting part possesses:
Necking part, it is provided in when described fork swings and does not interfere with described free-wheel clutch; With
Flank, it is arranged on the side of opposite side relative to the side towards the side that described free-wheel clutch is formed of described necking part.
2. power transmission apparatus for vehicle according to claim 1, is characterized in that,
2nd plane and the 1st plane orthogonal comprising the central axis of described large end and the central axis of described small end, and at described necking part place, described large end and described small end are separated, in the face of described 2nd plane, described necking part and described flank are configured to: the sectional area of the side of described 1st plane is equal with the sectional area of the opposite side of described 1st plane.
3. power transmission apparatus for vehicle according to claim 1 and 2, is characterized in that,
3rd plane and the 1st plane orthogonal comprising the central axis of described large end and the central axis of described small end, and with the 2nd plane orthogonal described large end and described small end separated perpendicular to described 1st plane and at described necking part place, and the 3rd plane comprises the center of the center of the outer peripheral face of described large end and the outer peripheral face of described small end, and the cross sectional shape of described necking part and described flank is configured to: the shape of the shape of the side of the 3rd plane and the opposite side of the 3rd plane is about described 3rd plane symmetry.
4. power transmission apparatus for vehicle according to claim 1 and 2, is characterized in that,
Described connecting part possesses:
Through hole, the line of centers consisted of about linking the center of described large end and the center of described small end is symmetrical;
1st connecting part, it links up between described large end and described necking part; And
2nd connecting part, it is being formed with the position of described 1st connecting part about described line of centers symmetry, and links up between described large end and described necking part,
Described through hole is formed between described 1st connecting part and described 2nd connecting part,
The rigidity of described 1st connecting part is configured to the rigid phase of described 2nd connecting part same.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2013212341A JP6117672B2 (en) | 2013-10-09 | 2013-10-09 | Power transmission device for vehicle |
| JP2013-212341 | 2013-10-09 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN104553741A true CN104553741A (en) | 2015-04-29 |
| CN104553741B CN104553741B (en) | 2017-04-12 |
Family
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201410528403.3A Active CN104553741B (en) | 2013-10-09 | 2014-10-09 | Vehicle power transmission device |
Country Status (2)
| Country | Link |
|---|---|
| JP (1) | JP6117672B2 (en) |
| CN (1) | CN104553741B (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112533780A (en) * | 2018-08-08 | 2021-03-19 | 采埃孚股份公司 | Multi-point connecting rod for chassis of motor vehicle |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102009031791A1 (en) * | 2008-07-21 | 2010-01-28 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Connecting rod eye for drive-side connection of stepless, adjustable crank gear, has upper connecting rod eye provided for connection with free-wheel unit, where eye is asymmetrically formed with respect to connecting line |
| WO2013001859A1 (en) * | 2011-06-30 | 2013-01-03 | 本田技研工業株式会社 | Four-joint link type continuously variable transmission |
| WO2013008624A1 (en) * | 2011-07-13 | 2013-01-17 | 本田技研工業株式会社 | Continuously variable transmission |
| CN103189626A (en) * | 2010-11-02 | 2013-07-03 | 本田技研工业株式会社 | Drive system |
Family Cites Families (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP4618231B2 (en) * | 2006-11-07 | 2011-01-26 | トヨタ自動車株式会社 | Internal combustion engine and its connecting rod |
| JP4946583B2 (en) * | 2007-04-12 | 2012-06-06 | マツダ株式会社 | Connecting rod |
| JP2011140999A (en) * | 2010-01-08 | 2011-07-21 | Honda Motor Co Ltd | Continuously variable transmission |
| JP2011163531A (en) * | 2010-02-15 | 2011-08-25 | Honda Motor Co Ltd | One-way clutch |
-
2013
- 2013-10-09 JP JP2013212341A patent/JP6117672B2/en not_active Expired - Fee Related
-
2014
- 2014-10-09 CN CN201410528403.3A patent/CN104553741B/en active Active
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102009031791A1 (en) * | 2008-07-21 | 2010-01-28 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Connecting rod eye for drive-side connection of stepless, adjustable crank gear, has upper connecting rod eye provided for connection with free-wheel unit, where eye is asymmetrically formed with respect to connecting line |
| CN103189626A (en) * | 2010-11-02 | 2013-07-03 | 本田技研工业株式会社 | Drive system |
| WO2013001859A1 (en) * | 2011-06-30 | 2013-01-03 | 本田技研工業株式会社 | Four-joint link type continuously variable transmission |
| WO2013008624A1 (en) * | 2011-07-13 | 2013-01-17 | 本田技研工業株式会社 | Continuously variable transmission |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112533780A (en) * | 2018-08-08 | 2021-03-19 | 采埃孚股份公司 | Multi-point connecting rod for chassis of motor vehicle |
Also Published As
| Publication number | Publication date |
|---|---|
| JP6117672B2 (en) | 2017-04-19 |
| JP2015075184A (en) | 2015-04-20 |
| CN104553741B (en) | 2017-04-12 |
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