CN103968026A - Vehicle power transmission apparatus - Google Patents
Vehicle power transmission apparatus Download PDFInfo
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- CN103968026A CN103968026A CN201310693672.0A CN201310693672A CN103968026A CN 103968026 A CN103968026 A CN 103968026A CN 201310693672 A CN201310693672 A CN 201310693672A CN 103968026 A CN103968026 A CN 103968026A
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- China
- Prior art keywords
- large end
- connecting rod
- outer circumferential
- chain link
- 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 possess the power transmission apparatus for vehicle of curved shaft type stepless speed variator, described curved shaft type stepless speed variator through reciprocating connecting rod and overrunning clutch from input shaft to output shaft transmission of drive force.
Background technique
According to the known such power transmission apparatus for vehicle of following patent documentation 1: the large end of connecting rod is connected with eccentric disc, described eccentric disc rotates integratedly with the input shaft that is connected in motor, and the small end of connecting rod is connected with output shaft through overrunning clutch, utilizes overrunning clutch the to-and-fro motion of the connecting rod producing because of the eccentric rotary of eccentric disc to be converted to the rotatablely moving an of direction of output shaft.
Patent documentation 1: Japanese Unexamined Patent Application Publication 2005-502543 communique
, in above-mentioned existing power transmission apparatus for vehicle, the inner ring of ball bearing is pressed into the outer circumferential face of the eccentric disc of being located at input shaft, the inner peripheral surface of the large end of connecting rod is pressed into the outer ring of this ball bearing.Because connecting rod has the linking department that links large end and small end, therefore, the rigidity of the large end of connecting rod is unfixing in a circumferential direction, and the rigidity of the part being connected with linking department uprises partly.Therefore, in the time that the large end of connecting rod is pressed into the outer ring of ball bearing, the larger reaction force that is pressed into is born in the outer ring that the part higher with the rigidity of large end contacts, the less reaction force that is pressed into is born in the outer ring that the part lower with the rigidity of large end contacts, thereby cause circularity to reduce because this official post that is pressed into reaction force obtains ball bearing distortion, thereby exist the friction increase of ball bearing or durability to reduce such problem.
For fear of such problem, as long as the wall thickness entirety of the large end of connecting rod is increased to improve rigidity, still, if done like this, can exist the weight of connecting rod and size to increase such problem.
Summary of the invention
The present invention In view of the foregoing completes, and its object is the weight increase of the connecting rod of power transmission apparatus for vehicle to be suppressed at minimum limit, guarantees the circularity of the bearing of the large end that is pressed into this connecting rod simultaneously.
To achieve these goals, according to the invention described in technological scheme 1, provide a kind of power transmission apparatus for vehicle, this power transmission apparatus for vehicle possesses: input shaft, and it is connected with driving source; Output shaft, itself and described input shaft configure abreast; Swing chain link, it is supported on described output shaft in the mode that can swing; Overrunning clutch, it is configured between described output shaft and described swing chain link, in the time that this swing chain link swings to direction described in overrunning clutch engage, in the time that this swing chain link swings in the other direction described in overrunning clutch remove and engage; Eccentric disc, itself and described input shaft eccentric rotary integratedly; Shifting actuator, it changes the offset of described eccentric disc; And connecting rod, it connects described eccentric disc and described swing chain link, and described power transmission apparatus for vehicle is characterised in that, and described connecting rod possesses: the large end of ring-type, it is pressed into the bearing arranging on the outer circumferential face of described eccentric disc; Small end, it is connected with described swing chain link; And linking department, it links described large end and described small end, be formed with through-shaft to two surperficial penetration holes at described linking department, the center of the outer circumferential face of described large end is with respect to the small end lateral deviation heart described in the middle mind-set of inner peripheral surface, and the inner edge portion in the face of described large end of described penetration hole is the circular arc jointly with described outer circumferential face with center.
In addition, according to the invention described in technological scheme 2, provide a kind of power transmission apparatus for vehicle, it is characterized in that, on the basis of the structure of technological scheme 1, the radius of the outer circumferential face of large end is little described in the radius ratio of the inner edge portion of described penetration hole.
In addition, according to the invention described in technological scheme 3, provide a kind of power transmission apparatus for vehicle, it is characterized in that, on the basis of the structure of technological scheme 1 or technological scheme 2, the outer edge of described penetration hole is secant-shaped with the outer circumferential face of described large end and is connected.
And the ball bearing 20 of mode of execution is corresponding to bearing of the present invention, the motor E of mode of execution is corresponding to driving source of the present invention.
According to the structure of technological scheme 1, when input shaft when rotation being connected with driving source, large end be connected to input shaft integratedly the connecting rod of the eccentric disc of eccentric rotary move back and forth, the swing chain link being connected with the small end of connecting rod carries out reciprocally swinging.In the time swinging chain link and swing to direction, overrunning clutch engages, and in the time swinging chain link and swing in the other direction, overrunning clutch is removed and engaged, and therefore, the to-and-fro motion of connecting rod is converted into the rotatablely moving an of direction of output shaft.In the time changing the offset of eccentric disc by shifting actuator, the reciprocating stroke of connecting rod changes and the angle of oscillation that swings chain link is changed, and therefore, after the rotation speed change of input shaft, is passed to output shaft.
Connecting rod possesses: the large end of ring-type, and it is pressed into the bearing arranging on the outer circumferential face of eccentric disc; Small end, it is connected with swing chain link; And linking department, it links large end and small end, therefore, the rigidity of the large end of connecting rod uprises in the part, part place being connected with linking department, in the time that the large end of connecting rod is pressed into bearing, there is such possibility: make bearing deflection owing to being pressed into the unbalanced of reaction force, thereby cause circularity to decline.
And, be formed with through-shaft to two surperficial penetration holes at the linking department of connecting rod, the center of the outer circumferential face of large end is with respect to the middle mind-set small end lateral deviation heart of inner peripheral surface, the inner edge portion in the face of large end of penetration hole is the circular arc jointly with outer circumferential face with center, therefore, sharply change in a circumferential direction by the rigidity that prevents large end, gently change in a circumferential direction thereby can make to be pressed into reaction force the circularity that improves bearing.And, be formed as on the whole compared with the situation of circularity that heavy wall improves bearing, the increase of the weight of connecting rod and size to be suppressed to inferior limit with making large end.
In addition, according to the structure of technological scheme 2, because the radius of the outer circumferential face of the large end of radius ratio of the inner edge portion of penetration hole is little, therefore, by dwindling the radius of inner edge portion of penetration hole, can be reduced in the rigidity that the part place being connected with linking department becomes excessive large end, thereby can make the rigidity of large end evenly further improve in a circumferential direction the circularity of bearing.
In addition, according to the structure of technological scheme 3, because being secant-shaped, the outer circumferential face of the Yu great end, outer edge of penetration hole connects, therefore, the variation of the wall thickness at the part place being connected with linking department in large end of connecting rod can be suppressed for inferior limit, can make that bearing bears from large end to be pressed into reaction force more even in a circumferential direction, thereby further improve the circularity of bearing.
Brief description of the drawings
Fig. 1 is the skeleton diagram of power transmission apparatus for vehicle.
Fig. 2 is the details drawing of 2 of Fig. 1.
Fig. 3 is along the sectional view of the 3-3 line of Fig. 2 (the highest (TOP) state).
Fig. 4 is along the sectional view of the 3-3 line of Fig. 2 (minimum (LOW) state).
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 that the shape of connecting rod is shown.
Fig. 8 is the figure of the circularity of the large end of comparison mode of execution and comparative example 1～3.
Fig. 9 is the figure of the circularity of the large end of comparison mode of execution and comparative example 4.
Figure 10 is the figure of comparison mode of execution and comparative example 5.
Label declaration
11: input shaft;
12: output shaft;
13: swing chain link;
14: shifting actuator;
18: eccentric disc;
19: connecting rod;
19a: large end;
19b: small end;
19c: linking department;
19d: penetration hole;
20: ball bearing (bearing);
21: overrunning clutch;
E: motor (driving source);
Ea: the inner edge portion of penetration hole;
Eb: the outer edge of linking department;
Oa: the center of the inner peripheral surface of large end;
Ob: the center of the outer circumferential face of large end;
Pa: the inner peripheral surface of large end;
Pb: the outer circumferential face of large end;
Rb: the radius of the outer circumferential face of large end;
Rc: the radius of the inner edge portion of penetration hole.
Embodiment
Below, based on Fig. 1～Figure 10, embodiments of the present invention are described.
As shown in Figure 1, the power transmission apparatus for vehicle that the driving force of motor E is passed to driving wheel W, W through the axletree 10,10 of left and right possesses curved shaft type stepless speed variator T and differential mechanism D.
Next, based on Fig. 2～Fig. 6, the structure of stepless speed variator T is described.
As shown in Figures 2 and 3, the stepless speed variator T of present embodiment will have multiple (being 4 in mode of execution) power transfer unit U of same structure ... overlapping form vertically, these power transfer units U ... possess abreast the shared input shaft 11 of configuration and shared output shaft 12, being rotated in of input shaft 11 slowed down or accelerate after be passed to output shaft 12.
Below, as representative, the structure of a power transfer unit U is described.The input shaft 11 connecting with motor E and rotate runs through the inside of the running shaft 14a of the hollow of the such shifting actuator of electric motor 14 in relative mode of rotating freely.The rotor 14b of shifting actuator 14 is fixed on running shaft 14a, and stator 14c is fixed on housing.The running shaft 14a of shifting actuator 14 can rotate with the speed identical with input shaft 11, and can relatively rotate with different speed with respect to input shaft 11.
On the input shaft 11 of running shaft 14a that runs through shifting actuator 14, be fixed with the 1st small gear 15, the planet carrier 16 of bent axle shape is connected in the running shaft 14a of shifting actuator 14 to cross over the mode of the 1st small gear 15.2 the 2nd small gears 17,17 that diameter is identical with the 1st small gear 15 are supported in the 1st small gear 15 and cooperate and be configured to the position of equilateral triangle through small gear pin 16a, 16a respectively, gear ring 18a engages with these the 1st small gears 15 and the 2nd small gear 17,17, and described gear ring 18a is formed at the inside of the eccentric disc 18 of circular plate type prejudicially.
Connecting rod 19 possesses large end 19a, small end 19b and links the linking department 19c of large end 19a and small end 19b.Large end 19a is embedded in the periphery of eccentric disc 18 in the mode freely of relatively rotating through ball bearing 20, small end 19b sells 26 pivot suspensions in swinging chain link 13, and described swing chain link 13 is supported on the periphery of output shaft 12 in the mode that can swing.
The overrunning clutch 21 that is configured in output shaft 12 and swing between chain link 13 possesses: the exterior part 22 of ring-type, and it is pressed into the inner peripheral surface that swings chain link 13; Inner piece 23, it is disposed at the inside of exterior part 22 and is fixed on output shaft 12; And roller 25 ..., they are disposed between exterior part 22 and inner piece 23 space of the wedge-like forming and engaged spring 24 ... the application of force.
Can know clearly 4 power transfer unit U according to Fig. 2 ... jointly have the planet carrier 16 of bent axle shape, the phase place that is supported on the eccentric disc 18 of planet carrier 16 through the 2nd small gear 17,17 differs respectively 90 ° at each power transfer unit U.For example, in Fig. 2, the eccentric disc 18 of the power transfer unit U of left end with respect to input shaft 11 to top displacement in figure, from the eccentric disc 18 of the 3rd power transfer unit U of left beginning with respect to input shaft 11 to below displacement figure, be positioned at the centre of above-below direction from the eccentric disc 18,18 of the 2nd and the 4th power transfer unit U, U of left beginning.
In Fig. 1～Fig. 6, schematically show the shape of connecting rod 19, still, based on Fig. 7, the true form of connecting rod 19 is described.
The large end 19a of connecting rod 19 possesses the outer circumferential face Pb of the inner peripheral surface Pa of radius R a and the radius R b larger than Ra, and the center O b of outer circumferential face Pb leans on to small end 19b lateral deviation with the amount apart from a with respect to the center O a of inner peripheral surface Pa.Therefore, the wall thickness radially of large end 19a is inhomogeneous in a circumferential direction, and wall thickness diminishes in the side away from small end 19b, and wall thickness is becoming large near a side of small end 19b.
In the central authorities of the linking department 19c of triangle, be formed with the penetration hole 19d of triangle, described penetration hole 19d runs through axial two faces of connecting rod 19, and penetration hole 19d is made up of the circular arc that jointly has a radius R c of center O b with the outer circumferential face Pb of large end 19a towards the inner edge portion Ea of large end 19a.The radius R c of the inner edge portion Ea of penetration hole 19d sets than the amount of the radius R b small distance b of the outer circumferential face Pb of large end 19a.
Linking department 19c possesses 2 outer edge Eb, Eb, and these 2 outer edge Eb, Eb mutually extend on one side and extend on one side towards large end 19a side from small end 19b side, and outer edge Eb, Eb are secant-shaped with the outer circumferential face Pb of large end 19a and are connected.
Next, the effect of the embodiments of the present invention that possess said structure is described.
First, the effect of stepless speed variator T power transfer unit U is described.If the running shaft 14a of shifting actuator 14 is rotated relatively with respect to input shaft 11, planet carrier 16 is around the axis L1 of input shaft 11 rotation.The center of the equilateral triangle that now, the center O of planet carrier 16, i.e. the 1st small gear 15 and two the 2nd small gears 17,17 form is around the axis L1 of input shaft 11 rotation.
The center O that Fig. 3 and Fig. 5 show planet carrier 16 is input shaft 11 with respect to the 1st small gear 15() be positioned at the state of a side contrary with output shaft 12, now, the offset with respect to input shaft 11 of eccentric disc 18 becomes maximum, and the gear ratio of stepless speed variator T becomes high state.The center O that Fig. 4 and Fig. 6 show planet carrier 16 is input shaft 11 with respect to the 1st small gear 15() be positioned at the state of a side identical with output shaft 12, now, the offset with respect to input shaft 11 of eccentric disc 18 becomes minimum, and the gear ratio of stepless speed variator T becomes minimum state.
Under the high state shown in Fig. 5, if input shaft 11 is rotated and made the running shaft 14a rotation of shifting actuator 14 with the speed identical with input shaft 11 by motor E, input shaft 11, running shaft 14a, planet carrier 16, the 1st small gear 15, two the 2nd small gears 17,17 and eccentric disc 18 carry out eccentric rotary around counterclockwise (reference arrow A) under the state becoming one centered by input shaft 11.During (A) from Fig. 5 rotates to the state of Fig. 5 (C) through Fig. 5 (B), large end 19a is rotatably freely supported on the periphery of eccentric disc 18 relatively connecting rod 19 through ball bearing 20 makes to swing chain link 13 around counterclockwise (reference arrow B) swing, and described swing chain link 13 is sold 26 pivot suspensions in the small end 19b of connecting rod 19.(A) of Fig. 5 and (C) of Fig. 5 show and swing the two ends that chain link 13 swings to described arrow B direction.
Like this, in the time that swing chain link 13 swings to arrow B direction, roller 25 ... the space of the wedge-like between exterior part 22 and the inner piece 23 of engaging-in overrunning clutch 21, thereby the rotation of exterior part 22 is passed to output shaft 12 via inner piece 23, therefore, output shaft 12 is around counterclockwise (reference arrow C) rotation.
If input shaft 11 and the 1st small gear 15 are further rotated, the eccentric disc 18 that gear ring 18a engages with the 1st small gear 15 and the 2nd small gear 17,17 carries out eccentric rotary around counter clockwise direction (reference arrow A).During (C) from Fig. 5 rotates to the state of Fig. 5 (A) through Fig. 5 (D), large end 19a is rotatably freely supported on the periphery of eccentric disc 18 relatively connecting rod 19 through ball bearing 20 makes to swing chain link 13 (reference arrow B ') swing clockwise, and described swing chain link 13 is sold 26 pivot suspensions in the small end 19b of connecting rod 19.(C) of Fig. 5 and (A) of Fig. 5 show and swing the two ends that chain link 13 swings to described arrow B ' direction.
Like this, in the time swinging chain link 13 to the swing of arrow B ' direction, roller 25 ... compressive engagement spring 24 on one side ... released by the space of the wedge-like between exterior part 22 and inner piece 23 on one side, make thus exterior part 22 skid with respect to inner piece 23, thereby output shaft 12 does not rotate.
As described above, in the time of swing chain link 13 reciprocally swinging, only have output shaft 12 in the time that the swaying direction of swing chain link 13 is counter clockwise direction (reference arrow B) just to rotate around counter clockwise direction (reference arrow C), therefore, output shaft 12 intermittent rotaries.
Fig. 6 is the figure that is illustrated in the effect while turning round stepless speed variator T under minimum state.Now, because the position of input shaft 11 is consistent with eccentric disc 18 center, therefore eccentric disc 18 is zero with respect to the offset of input shaft 11.If input shaft 11 rotated by motor E under this state and make the running shaft 14a rotation of shifting actuator 14 with the speed identical with input shaft 11, input shaft 11, running shaft 14a, planet carrier 16, the 1st small gear 15, two the 2nd small gears 17,17 and eccentric disc 18 carry out eccentric rotary around counterclockwise (reference arrow A) under the state becoming one centered by input shaft 11., because the offset of eccentric disc 18 is zero, therefore the reciprocating stroke of connecting rod 19 is also zero, and output shaft 12 does not rotate.
Therefore, if drive shifting actuator 14 by the set positions of planet carrier 16 between the high state and the minimum state of Fig. 4 of Fig. 3, can realize the running under any gear ratio between zero gear ratio and predetermined gear ratio.
In stepless speed variator T, 4 power transfer unit U that are set up in parallel ... eccentric disc 18 ... phase place stagger mutually 90 °, therefore, 4 power transfer unit U ... alternately transmission of drive force, i.e. 4 overrunning clutchs 21 ... in any one is inevitable in jointing state, can make thus output shaft 12 continuous rotations.
, in the time the outer circumferential face of ball bearing 20 being pressed into the inner peripheral surface Pa of large end 19a of connecting rod 19, ball bearing 20 is subject to being out of shape towards being pressed into reaction force of radially inner side from the inner peripheral surface Pa of large end 19a.Now, if towards radially inner side to be pressed into reaction force even in a circumferential direction, can guarantee the circularity of the ball bearing 20 after being pressed into, but the rigidity of in fact large end 19a is inhomogeneous in a circumferential direction, near of the part being connected with linking department 19c at large end 19a, rigidity is local to raise, and therefore, thereby exists ball bearing 20 to cause circularity to reduce such problem because loading of pressing in is out of shape.
The comparative example 1 of Fig. 8 is the radius R b comparative example identical with the radius R c of inner edge portion Ea that makes the center O a of inner peripheral surface Pa and the center O b of outer circumferential face Pb unanimously and make outer circumferential face Pb, the wall thickness of large end 19a is set littlely in order to realize miniaturization and lightweight, and its weight is 422g.
In comparative example 1, the wall thickness of large end 19a is thinner, and the local rising of the rigidity of the part that end 19a is connected with linking department 19c greatly, therefore, the being pressed into reaction force part of this part increases and causes ball bearing 20 to radially inner side distortion, causes thus circularity to deteriorate to 52.5 μ m.Circularity refers to the poor of the maximum radius of rolling track of the ball of ball bearing 20 and least radius, and just round in the situation that, circularity is 0 μ m, and numerical value is larger, represents that circularity is poorer.
Comparative example 2 is comparative examples that the wall thickness of the large end 19a of comparative example 1 is increased, and other are identical with comparative example 1.In comparative example 2, increase by the wall thickness that makes large end 19a, weight is increased to 918g, and the radius R 2 of the outer circumferential face Pb of large end 19a also increases., improve on the whole because the increase of wall thickness makes the rigidity of large end 19a, alleviated the part place that rigidity is connected with linking department 19c at large end 19a and sharply changed this situation, therefore circularity significantly reduces and becomes 12.5 μ m.
Comparative example 3 is the comparative examples that the center O b of outer circumferential face Pb moved with respect to the center O a of the inner peripheral surface Pa of the large end 19a of comparative example 2 to small end 19b lateral deviation, and weight becomes the 640g of the centre of comparative example 1 and comparative example 2.The wall thickness increase at the part place being connected with linking department 19c due to large end 19a further relaxes the sharply variation of rigidity, and therefore circularity further reduces and becomes 9.5 μ m., in comparative example 3, the part place being connected with linking department 19c at large end 19a, rigidity unbalanced still remaining, therefore circularity is impaired.
In mode of execution, the radius R c of the inner edge portion Ea of the penetration hole 19d of comparative example 3 is set littlely than the radius R b of outer circumferential face Pb, make rigidity local reduce of large end 19a in the face of the part of inner edge portion Ea.Thus, the weight of the connecting rod 19 of mode of execution is suppressed in 625g, and, circularity be increased to than in comparative example 1～comparative example 3 any one all good 3.8.
Fig. 9 is the figure of the effect for penetration hole 19d is described, in the comparative example 4 shown in (B) of Fig. 9, the part suitable with the penetration hole 19d of mode of execution do not run through, but stopped up by the web 19e of thin-walled.Known, because making the rigidity of the large end 19a of the inner edge portion Ea that faces penetration hole 19d, this web 19e significantly improves, and circularity significantly worsens.On the other hand, known in the mode of execution shown in (A) of Fig. 9, by forming penetration hole 19d, the rigidity of facing the large end 19a of the inner edge portion Ea of penetration hole 19d reduces, and circularity is significantly improved.
Figure 10 is the figure of the effect of outer edge Eb, Eb for linking department 19c is described, and in the comparative example 5 shown in (B) of Figure 10, outer edge Eb, the Eb of linking department 19c is secant-shaped with the outer circumferential face Pb of large end 19a to be connected, but connects across.Consequently, there is such problem: the wall thickness of large end 19a sharply changes near cross part, due to the sharply variation of the rigidity causing thus, circularity is worsened.On the other hand, in the mode of execution shown in (A) of Figure 10, outer edge Eb, the Eb of linking department 19c is secant-shaped with the outer circumferential face Pb of large end 19a and is connected, and therefore, prevented that the wall thickness of large end 19a from sharply changing near cross part, thereby improved circularity.
As described above, according to present embodiment, can, the weight increase of connecting rod 19 to be suppressed to the minimal rigidity of large end 19a that makes even in a circumferential direction simultaneously, can guarantee the circularity of the ball bearing 20 that is pressed into large end 19a and realize the reduction of friction and the raising of durability.
Above, embodiments of the present invention are illustrated, but the present invention can carry out various design alterations in the scope that does not depart from its main points.
For example, bearing of the present invention is not limited to the ball bearing 20 of mode of execution, can be the bearing arbitrarily such as needle bearing, roller bearing, sliding bearing.
In addition, driving source of the present invention is not limited to the motor E of mode of execution, can be also the driving source arbitrarily such as motor generator set.
Claims (3)
1. a power transmission apparatus for vehicle, it possesses:
Input shaft (11), it is connected with driving source (E);
Output shaft (12), itself and described input shaft (11) configure abreast;
Swing chain link (13), it is supported on described output shaft (12) in the mode that can swing;
Overrunning clutch (21), it is configured between described output shaft (12) and described swing chain link (13), described in the time that this swing chain link (13) swings to direction, overrunning clutch (21) engages, in the time that this swing chain link (13) swings in the other direction described in overrunning clutch (21) remove and engage;
Eccentric disc (18), itself and described input shaft (11) eccentric rotary integratedly;
Shifting actuator (14), it changes the offset of described eccentric disc (18); With
Connecting rod (19), it connects described eccentric disc (18) and described swing chain link (13),
Described power transmission apparatus for vehicle is characterised in that,
Described connecting rod (19) possesses: the large end (19a) of ring-type, and it is pressed into the bearing (20) arranging on the outer circumferential face of described eccentric disc (18); Small end (19b), it is connected with described swing chain link (13); And linking department (19c), it links described large end (19a) and described small end (19b),
Be formed with through-shaft to two surperficial penetration holes (19d) at described linking department (19c), the center (Ob) of the outer circumferential face (Pb) of described large end (19a) is with respect to the center (Oa) of inner peripheral surface (Pa) to described small end (19b) the lateral deviation heart, and the inner edge portion (Ea) in the face of described large end (19a) of described penetration hole (19d) is the circular arc jointly with described outer circumferential face (Pb) with center (Ob).
2. power transmission apparatus for vehicle according to claim 1, is characterized in that,
The radius (Rc) of the inner edge portion (Ea) of described penetration hole (19d) is less than the radius (Rb) of the outer circumferential face (Pb) of described large end (19a).
3. according to claim 1 or power transmission apparatus for vehicle claimed in claim 2, it is characterized in that,
The outer edge (Eb) of described penetration hole (19d) is secant-shaped with the outer circumferential face (Pb) of described large end (19a) and is connected.
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 true CN103968026A (en) | 2014-08-06 |
| CN103968026B 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) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108026959A (en) * | 2015-09-25 | 2018-05-11 | Ntn株式会社 | Link assembly and its manufacture method |
| 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 |
Families Citing this family (1)
| 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 |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US20050039572A1 (en) * | 2001-09-26 | 2005-02-24 | Oswald Friedmann | Drive assembly |
| JP2012001049A (en) * | 2010-06-15 | 2012-01-05 | Honda Motor Co Ltd | Power transmission device for vehicle |
| CN202500976U (en) * | 2012-03-12 | 2012-10-24 | 周有强 | Connecting-rod tooth-engaging type speed reducing and changing device |
| 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 |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2003322138A (en) * | 2002-04-30 | 2003-11-14 | Ntn Corp | Connecting rod and connecting rod with bearing |
| WO2012026181A1 (en) * | 2010-08-27 | 2012-03-01 | 本田技研工業株式会社 | Engine starting device for vehicle |
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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
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US20050039572A1 (en) * | 2001-09-26 | 2005-02-24 | Oswald Friedmann | Drive assembly |
| JP2012001049A (en) * | 2010-06-15 | 2012-01-05 | Honda Motor Co Ltd | Power transmission device for vehicle |
| 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 |
| CN202500976U (en) * | 2012-03-12 | 2012-10-24 | 周有强 | Connecting-rod tooth-engaging type speed reducing and changing device |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108026959A (en) * | 2015-09-25 | 2018-05-11 | Ntn株式会社 | Link assembly and its manufacture method |
| CN108026959B (en) * | 2015-09-25 | 2020-09-01 | Ntn株式会社 | Connecting rod assembly and method of manufacturing the same |
| 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 |
Also Published As
| Publication number | Publication date |
|---|---|
| JP6011971B2 (en) | 2016-10-25 |
| CN103968026B (en) | 2017-01-11 |
| JP2014152808A (en) | 2014-08-25 |
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