CN104827894B - Power transmission apparatus for vehicle - Google Patents

Abstract

The present invention provides a kind of power transmission apparatus for vehicle.Power transmission apparatus for vehicle has：Input shaft, it is inputted driving force from driving source；Output shaft, it is abreast configured with input shaft；Eccentric rotating member, its integratedly eccentric rotary with input shaft；Swing rod, it links with output shaft；One-way clutch, swing rod is fixed on output shaft by it when swing rod is to be swung aside, and is intended in swing rod to making swing rod be dallied relative to output shaft during another side oscillation；Offset governor motion, it makes the pivot of eccentric rotating member eccentric relative to the pivot of input shaft；And connecting rod, it, which links eccentric rotating member and swing rod, connecting rod, has：The one end of ring-type, it is supported in the outer peripheral face of eccentric rotating member via bearing in a manner of rotating freely；And the other end linked with swing rod, the internal diameter in the defined region of the inner peripheral surface of the lasso of bearing or the one end of connecting rod are the shape less than the theoretic positive round on the basis of the pivot of eccentric rotating member.

Description

Power transmission apparatus for vehicle

Technical field

The present invention relates to the bearing arrangement of the power transmission apparatus for vehicle such as the buncher of four section linkage types.

Background technology

For example, four following section linkage type bunchers are described in Japanese Unexamined Patent Publication 2012-1048 publications, It is by the reciprocating motion for being converted to connecting rod for the input shaft being connected with engine, by one-way clutch by the reciprocal of connecting rod Motion is converted to the rotary motion of output shaft.

Above-mentioned four save linkage type buncher as shown in Figure 5A, in a period of the rotation of eccentric disc 6 is turned around, alternately Repeat pushing or the action of traction link 15 between input shaft side and output shaft side, swing swing rod 18.As above inclined In a period of the rotation of cartridge 6 is turned around, as shown in Figure 5 B, the big footpath annulus 15a load of connecting rod 15 is applied to (hereinafter referred to as Connecting rod load) to be maximum, hereafter drastically vanishing.Therefore, the rolling element (spheroid) of the connecting-rod bearing 16 of connecting rod load is being born On lasso (inner ring and outer ring), in a period of connecting rod load Nmax is maximum in each cycle, due to connecting rod 15 Push-and-pull and the change of load occurred, cause to produce gap, the load after load just vanishing in defined region S1 and S2 The action direction of lotus produces the timing of switching, and gap can drastically reduce, so as to produce the rolling element and lasso of the connecting-rod bearing 16 Impact sound.For example, in the state of the big footpath annulus 15a of the connecting rod 15 shown in Fig. 5 B pushes swing rod 18, in connecting rod 15 The opposite side for the region S1 that the reaction force that big footpath annulus 15a is subject to from swing rod 18 is acted on region S2 (90 °≤θ 1≤ 270 °) in caused gap can drastically reduce, so as to produce the impact sound of the rolling element of the connecting-rod bearing 16 and lasso, turn into NVH The reason for (noise, vibration and sound vibration roughness) deteriorates.

As this NVH countermeasures, such as such as the following countermeasure can be taken：Using the corner connection that conical section is set on lasso Structure is touched, or lasso is assigned preloading in an initial condition so that lasso and rolling element when load is applied in It will not separate, yet with assigning preloading, thus worry increase and the service life reduction of friction.

The content of the invention

The present invention in view of above-mentioned problem and complete, its object is to realize a kind of bearing arrangement, it can be reduced The lasso of the connecting-rod bearing and the impact sound of rolling element for the reason for deteriorating as NVH (noise, vibration and sound vibration roughness).

In order to solve above-mentioned problem, reached purpose, the 1st form of the invention provides a kind of power transmission apparatus for vehicle 1, It has：Input shaft 2, it is inputted driving force from driving source；Output shaft 3, it is abreast configured with the input shaft 2；It is eccentric Rotary part 6, its integratedly eccentric rotary with the input shaft 2；Swing rod 18, it links with the output shaft 3；One-way clutch 17, the swing rod 18 is fixed on the output shaft 3 by it when the swing rod 18 is to be swung aside, and in the swing rod 18 It is intended to making the swing rod 18 be dallied relative to the output shaft 3 during another side oscillation；Offset governor motion 4, it makes described inclined The pivot P3 of heart rotary part 6 is eccentric relative to the pivot P1 of the input shaft 2；And connecting rod 15, it links institute Eccentric rotating member 6 and the swing rod 18 are stated, wherein, the connecting rod 15 has：The one end 15a of ring-type, it passes through bearing 16 The outer peripheral face of the eccentric rotating member 6 is supported in a manner of it can rotate freely；And the other end 15b, its with it is described Swing rod 18 links, the defined region S1 or S2 of the lasso of the bearing 16 or the one end 15a of the connecting rod 15 inner peripheral surface Internal diameter α 2 be shape less than the theoretic positive round α 1 on the basis of the pivot of the eccentric rotating member 6.

In addition, the 2nd form as the present invention, the 1st shape of the swing rod 18 is pushed in the one end 15a of the connecting rod 15 Under state, defined the region S1 or S2 are the opposite with face of the region of the swing rod 18 of the one end 15a of the connecting rod 15 Side region S2.

In addition, the 3rd form as the present invention, the 2nd shape of the swing rod 18 is drawn in the one end 15a of the connecting rod 15 Under state, defined the region S1 or S2 are the one end 15a of the connecting rod 15 region S1 in face of the swing rod 18.

In accordance with the invention it is possible to reduce the change of the load due to being acted between connecting rod and swing rod and caused, connecting rod The lasso of bearing and the impact sound of rolling element, the deterioration of NVH (noise, vibration and sound vibration roughness) can be suppressed.

Specifically, according to the 1st of the present invention the aspect, it is configured to the inner circumferential of the outer ring of the connecting-rod bearing or the one end of connecting rod The internal diameter for being easy to produce the region of the collision of rolling element and lasso on face be less than using the pivot of eccentric rotating member as The shape of the theoretic positive round of benchmark, so as to suppress NVH deterioration.

In addition, according to the 2nd or the 3rd of the present invention the aspect, by making the region that application preloads as far as possible to be necessary minimum Limit, so as to which the increase of friction and service life reduction are suppressed in Min..

On other objects and advantages in addition to the foregoing, those skilled in the art are according to following of the invention one The description of individual preferred embodiment can be obtained apparently.Disconnected accompanying drawing is referred in the de-scription, it illustrates The example of the present invention.However, this example is not intended to exhaustive various embodiments of the present invention, therefore, with reference to following Claims after the description determine the scope of the present invention.

Brief description of the drawings

Fig. 1 is the sectional view of the structure for the buncher for representing present embodiment.

Fig. 2 is the figure of the offset governor motion from end on observation Fig. 1 buncher, connecting rod and swing rod.

Fig. 3 A-3D are the figures of the change of offset caused by the offset governor motion for the buncher for representing Fig. 1.

Fig. 4 A-4C are to represent the pendulum of the change of offset and swing rod caused by the offset governor motion of present embodiment The figure of the relation of the swing angle scope of dynamic motion.

Fig. 5 A-5B are the figures for the change for representing region that connecting rod load acted on and load.

Fig. 6 A-6B are the figures of the shape of the lasso for the connecting-rod bearing for representing present embodiment.

Label declaration

1：Buncher, 2：Input shaft, 3：Output shaft, 4：Offset governor motion, 5：Cam disc, 6：Eccentric disc, 15： Connecting rod, 15a：Big footpath annulus, 15b：Path annulus, 16：The connecting-rod bearing, 17：One-way clutch, 18：Swing rod.

Embodiment

Hereinafter, the embodiment that present invention will be described in detail with reference to the accompanying.In addition, embodiments described below is to be used as this One of the realization rate of invention, the present invention can be applied to carry out to mode is implemented as follows in the range of its purport is not departed from Structure after modification or deformation.In addition, the buncher of the present invention can also be applied to other purposes beyond automobile, this is Self-evident.

The structure ＞ of ＜ bunchers first, referring to Figures 1 and 2, illustrates the knot of the buncher of present embodiment Structure.

The buncher 1 of present embodiment is can to make the gear ratio i (rotations of rotary speed/output shaft of i=input shafts Rotary speed) for infinitely great (∞) make the rotary speed of output shaft be the speed changer of " 0 ", i.e. so-called IVT (Infinity Variable Transmission：Limitless speed variator) one kind.

The buncher 1 of present embodiment has input shaft 2, output shaft 3 and 6 offset governor motions 4.

Input shaft 2 is made up of hollow part, and it receives the driving force from the travelling driving source such as engine or motor, It is driven in rotation centered on center of rotation axis P1.

Output shaft 3 is abreast configured at the position separated in the horizontal direction with input shaft 2 with input shaft 2, via differential Gear etc. transmits driving force to the axletree of automobile.

Offset governor motion 4 is driving force input unit respectively, be arranged to using the center of rotation axis P1 of input shaft 2 as Central rotation, there is the cam disc 5 as cam part, the eccentric disc 6 as eccentric part and pinion shaft 7.

Cam disc 5 is disc-shape, to rotate integrally from the center of rotation axis P1 of input shaft 2 bias and with input shaft 2 Mode 21 group be arranged at input shaft 2.Each group cam disc 5 is each set to 60 ° of phase shifting, is configured to by 6 groups Cam disc 5 is in input shaft 2 circumferentially around one week.

Eccentric disc 6 is disc-shape, reception hole 6a is being provided with heart P3 eccentric positions therefrom, to clip the reception hole 6a mode, 1 group of cam disc 5 is supported as that can rotate.

The reception hole 6a of eccentric disc 6 center is formed such that from the center of rotation axis P1 of input shaft 2 to cam disc 5 center P2 (reception hole 6a center) distance Ra and the center P2 from cam disc 5 to the center P3 of eccentric disc 6 distance Rb It is identical.In addition, formed with internal tooth 6b on the reception hole 6a of eccentric disc 6 inner peripheral surface clamped by 1 group of cam disc 5.

Pinion shaft 7 and input shaft 2 are concentrically arranged in the hollow bulb of input shaft 2, and via pinion bearing 7b and The inner peripheral surface of input shaft 2 is supported in a manner of it can rotate against.In addition, external tooth is provided with the outer peripheral face of pinion shaft 7 7a.And then differential attachment 8 is connected with pinion shaft 7.

Formed with incision hole 2a between 1 group of cam disc 5 on input shaft 2, incision hole 2a is in the bias with cam disc 5 The opposed position in direction connects inner peripheral surface with outer peripheral face, via incision hole 2a, the external tooth 7a and eccentric disc of pinion shaft 7 6 reception hole 6a internal tooth 6b engagements.

Differential attachment 8 is planetary gears, its have central gear 9, with input shaft 2 link the 1st gear ring 10, with it is small The 2nd gear ring 11 that gear shaft 7 links and by ladder little gear 12 by being capable of axle supports in a manner of rotation and revolution planet carrier 13, what the ladder little gear 12 engaged by the large-diameter portion 12a that is engaged with the gear ring 10 of central gear 9 and the 1st and with the 2nd gear ring 11 Minor diameter part 12b is formed.In addition, the central gear 9 of differential attachment 8 with by the driving of pinion shaft 7 motor drive mechanism into bias Regulation is measured with the rotary shaft 14a of driving source 14 to be linked.

Moreover, in the rotary speed and the rotary speed identical feelings of input shaft 2 that make the offset regulation driving source 14 Under condition, central gear 9 is rotated with the 1st gear ring 10 with identical speed, turns into central gear 9, the 1st gear ring 10, the 2nd gear ring 11 and row The lock-out state that this 4 key elements of carrier 13 can not be rotated against, with the 2nd gear ring 11 link pinion shaft 7 with input The same speed of axle 2 rotates.

In addition, make offset regulation driving source 14 rotary speed it is slower than the rotary speed of input shaft 2 in the case of, If set the rotating speed of central gear 9 as Ns, the 1st gear ring 10 rotating speed be NR1, the gear ratio of the gear ring 10 of central gear 9 and the 1st (number of teeth of the number of teeth/central gear 9 of the 1st gear ring 10) is j, then the rotating speed of planet carrier 13 is (jNR1+Ns)/(j+1).This Outside, if setting gear ratio ((number of teeth of the number of teeth/central gear 9 of the 2nd gear ring 11) × (rank of the gear ring 11 of central gear 9 and the 2nd The large-diameter portion 12a of the terraced little gear 12 number of teeth/minor diameter part 12b number of teeth)) be k, then the rotating speed of the 2nd gear ring 11 is { j (k+1) NR1+(k-j)Ns}/{k(j+1)}。

Therefore, make the rotary speed of offset regulation driving source 14 slower than the rotary speed of input shaft 2 and be fixed with In the case of the rotary speed of the input shaft 2 of cam disc 5 and the rotary speed identical of pinion shaft 7, eccentric disc 6 and cam disc 5 Rotate integrally.On the other hand, in the case where the rotary speed of input shaft 2 and the rotary speed of pinion shaft 7 have differences, partially Cartridge 6 is rotated centered on the center P2 of cam disc 5 in the periphery of cam disc 5.

As shown in Fig. 2 eccentric disc 6 is relative to cam disc 5, with the distance Ra from P1 to P2 and the distance Rb phases from P2 to P3 Same mode is eccentric.Therefore, it is possible to make the center P3 of eccentric disc 6 positioned at the center of rotation axis P1 identical lines with input shaft 2 On, it is " 0 " to make the distance between the center of rotation axis P1 of input shaft 2 and the center P3 of eccentric disc 6, i.e. offset R1.

Connecting rod 15 is supported by a manner of it can rotate on the outer edge of eccentric disc 6.Connecting rod 15 has an end The big footpath annulus 15a in big footpath, there is the path annulus 15b of path in another end.The big footpath annulus 15a of connecting rod 15 The outer edge of eccentric disc 6 is supported in via the connecting-rod bearing 16.

On output shaft 3, the one-way clutch 17 of mechanism is prevented to be linked with swing rod 18 via as single direction rotation.Unidirectionally from Swing rod 18 is fixed on output by clutch 17 in the case where being intended to centered on the center of rotation axis P4 of output shaft 3 rotate to side Axle 3, swing rod 18 is set to be dallied relative to output shaft 3 in the case where being intended to rotate to opposite side.

It is provided with swing rod 18 and swings end 18a, is provided with end 18a is swung so that path ring-type axially can be being clamped A pair of tab 18b that portion 15b mode is formed.The internal diameter pair with path annulus 15b is provided through on a pair of tab 18b The through hole 18c answered.Connecting pin 19 is inserted in through hole 18c and path annulus 15b, so as to which connecting rod 15 and swing rod 18 be connected Knot gets up.In addition, annulus 18d is provided with swing rod 18.

＜ toggles ＞ then, reference picture 2~Fig. 4 A-4C, illustrates the song of the buncher of present embodiment Handle linkage.

As shown in Fig. 2 in the buncher 1 of present embodiment, offset governor motion 4, connecting rod 15 and swing rod 18 Form toggle 20 (four section linkages).

By toggle 20, by the rotary motion of input shaft 2 be converted to swing rod 18 with the rotation of output shaft 3 Oscillating motion centered on mandrel line P4.The buncher 1 of present embodiment is as shown in figure 1, with total 6 crank connecting links Mechanism 20.

In toggle 20, in the case where the offset R1 of offset governor motion 4 is not " 0 ", if made Input shaft 2 and pinion shaft 7 are rotated with identical speed, then each connecting rod 15 staggers 60 degree of phase respectively, and input shaft 2 with Alternately repeat to be pushed to the side of output shaft 3 between output shaft 3 or be pulled to the side of input shaft 2, swing swing rod 18.

Moreover, one-way clutch 17 is provided between swing rod 18 and output shaft 3, therefore in the case where pushing swing rod 18, Swing rod 18 is fixed and transmits the moment of torsion as caused by the oscillating motion of swing rod 18 to output shaft 3 so that output shaft 3 rotates, and is leading In the case of drawing swing rod 18, swing rod 18 dallies without transmitting the moment of torsion as caused by the oscillating motion of swing rod 18 to output shaft 3.6 Individual offset governor motion 4 be stagger respectively 60 degree phase and configure, therefore output shaft 3 is by 6 offset governor motions 4 Rotation driving in order.

In addition, in the buncher 1 of present embodiment, as shown in figs. 3 a-3d, offset governor motion can be passed through 4 regulation offset R1.

Fig. 3 A represent the state for making offset R1 be " maximum ", pinion shaft 7 and eccentric disc 6 to cause the rotation of input shaft 2 Turn the central axis P1 and center P2 of the cam disc 5 and center P3 of eccentric disc 6 modes being arranged on straight line to be positioned.This When gear ratio i for minimum.Fig. 3 B represent make offset R1 be less than Fig. 3 A " in " state, Fig. 3 C represent make offset R1 To be further less than the state of Fig. 3 B " small ".On gear ratio i, represent in figure 3b gear ratio i more than Fig. 3 A " in " State, in fig. 3 c represent more than Fig. 3 B gear ratio i " big " state.Fig. 3 D represent the shape for making offset R1 be " 0 " State, the center of rotation axis P1 of input shaft 2 are positioned with one heart with the center P3 of eccentric disc 6.Gear ratio i now is infinity (∞)。

Fig. 4 A-4C represent offset R1 change caused by the offset governor motion 4 of present embodiment and swing rod 18 Oscillating motion swing angle scope relation.

Swing rod 18 when " maximum " that Fig. 4 A expressions offset R1 is Fig. 3 A (when gear ratio i is minimum) is relative to offset The hunting range θ 2 of the rotary motion (anglec of rotation θ 1) of governor motion 4, Fig. 4 B represent offset R1 be Fig. 3 B " in " when (become Speed than i be it is middle when) swing rod 18 relative to the rotary motion (anglec of rotation θ 1) of offset governor motion 4 hunting range θ 2, Swing rod 18 when " small " that Fig. 4 C expressions offset R1 is Fig. 3 C (when gear ratio i is big) is relative to offset governor motion 4 The hunting range θ 2 of rotary motion (anglec of rotation θ 1).Here, from the center of rotation axis P4 of output shaft 3 to connecting rod 15 with swinging End 18a point of contact, the length R2 that the distance for the center P5 for arriving connecting pin 19 is swing rod 18.

It can be seen from Fig. 4 A-4C, as offset R1 diminishes, the swing angle range Theta 2 of swing rod 18 also diminishes, in bias In the case that amount R1 is changed into " 0 ", swing rod 18 is no longer swung.

The structure ＞ of the ＜ connecting-rods bearing then, reference picture 5A-5B and Fig. 6 A-6B, illustrates the crank connecting link of present embodiment The structure of the connecting-rod bearing 16 of mechanism 20.

In order to solve the problem illustrated using Fig. 5 A-5B, the buncher 1 of present embodiment employs following structure： Bear easy on the outer ring of the connecting-rod bearing 16 of connecting rod load or big footpath annulus 15a (being integrally formed with outer ring) inner peripheral surface In defined the region S1 or region S2 of the collision for producing rolling element and lasso internal diameter α 2 be less than with the rotation of eccentric disc 6 The shape of theoretic positive round α 1 on the basis of heart P3, so as to inhibit NVH deterioration.

Here, as defined region, the 1st state (reaction force from swing rod 18 of swing rod 18 is pushed in connecting rod 15 Act on the state in Fig. 6 A negative x-direction) under, refer to the area with facing swing rod 18 on the big footpath annulus 15a of connecting rod 15 The region S2 of the opposite side in domain, it is that the anglec of rotation θ 1 of eccentric disc 6 shown in Fig. 6 A is 270 °~90 ° of range Theta s2.Separately Outside, it is illustrated that x directions be the direction of reaction force being subject to from swing rod 18, as shown in Figure 5A, its rotation with linking eccentric disc 6 Center P3 is consistent with the line Lcon of connecting rod 15 and the center P5 of the linking portion of swing rod 18.

In addition, the maximum for entering the amount t of inner side from positive round α 1 is 20~50 μm or so.In addition, in general bearing is just Circularity is 1~3 μm or so, and the situation more than 5 μm belongs to the rank of non-certified products.

As above, by the outer ring of the connecting-rod bearing 16 that makes to bear connecting rod load or big footpath annulus 15a (with outer ring one Forming) the internal diameter α 2 for being easy to produce the defined region S2 of the collision of rolling element and lasso on inner peripheral surface is less than with bias The shape of theoretic positive round α 1 on the basis of the pivot P3 of disk 6, it is achieved thereby that according to internal diameter α 2 less than positive round α's 1 Degree applies the setting preloaded.Therefore, as shown in Figure 6B, the 1st state (internal diameter α 22) acted in load in negative x-direction Under, outer ring to negative x-direction produce displacement, it is specified that region S2 also produce displacement in the negative x direction, but due to as not acting on The state (internal diameter α 21) of preloading, i.e. region S2 outer ring are applied with the original state of load in positive x direction in positive x side Drawn upwards and be connected to the state of rolling element, it is thus possible to which being configured to rolling element will not separate with lasso.Moreover, by making It is necessary Min. as far as possible to apply the region preloaded, so as to which the increase of friction and service life reduction are suppressed in minimum Limit.

In addition, region as defined in being used as, the 2nd state (reaction force from swing rod 18 of swing rod 18 is drawn in connecting rod 15 Act on the state of Fig. 6 A positive x direction) under, refer to above the big footpath annulus 15a of connecting rod 15 to the region S1 of swing rod 18, It is that the anglec of rotation θ 1 of the eccentric disc 6 shown in Fig. 6 A is 90 °~270 ° of range Theta s1.

That is, according to engine performance curve etc., by defined region S1, S2 is suitably set as the eccentric disc shown in Fig. 6 A 6 anglec of rotation θ 1 is 270 °~90 ° of range Theta s2 or is 90 °~270 ° of range Theta s1 or is the scope of both sides, So as to realize appropriate NVH countermeasures.

As described above, according to present embodiment, by making the outer ring of the connecting-rod bearing 16 or the big footpath annulus 15a of connecting rod 15 Inner peripheral surface on the internal diameter α 2 for being easy to produce the defined region S1 or S2 of the collision of rolling element and lasso be less than with bias The shape of theoretic positive round α 1 on the basis of the pivot P3 of disk 6, so as to reduce due to acting on connecting rod 15 and pendulum The change of load between bar 18 and the impact sound of caused, the connecting-rod bearing 16 lasso and rolling element, can suppress NVH and (make an uproar Sound, vibration and sound vibration roughness) deterioration.

The present invention is not limited to above-described embodiment, can within the spirit and scope of the present invention make a variety of changes and repair Change.Therefore, scope disclosed in this invention is explained by claims below.

Claims (3)

1. A kind of 1. power transmission apparatus for vehicle（1）, it has：

   Input shaft（2）, it is inputted driving force from driving source；

   Output shaft（3）, itself and the input shaft（2）Abreast configure；

   Eccentric rotating member（6）, itself and the input shaft（2）Integratedly eccentric rotary；

   Swing rod（18）, itself and the output shaft（3）Link；

   One-way clutch（17）, it is in the swing rod（18）By the swing rod when to be swung aside（18）It is fixed on the output Axle（3）, and in the swing rod（18）It is intended to making the swing rod during another side oscillation（18）Relative to the output shaft（3）It is empty Turn；

   Offset governor motion（4）, it makes the eccentric rotating member（6）Pivot（P3）Relative to the input shaft （2）Pivot（P1）It is eccentric；And

   Connecting rod（15）, it links the eccentric rotating member（6）With the swing rod（18）,

   The power transmission apparatus for vehicle（1）It is characterised by,

   The connecting rod（15）Have：The one end of ring-type（15a）, it passes through bearing（16）Supported in a manner of it can rotate freely In the eccentric rotating member（6）Outer peripheral face；And the other end（15b）, itself and the swing rod（18）Link,

   The bearing（16）Outer ring or the connecting rod that is integrally formed with the outer ring（15）One end（15a）Inner peripheral surface Be easy to produce the bearing（16）Rolling element and the outer ring collision defined region（S1 or S2）Internal diameter（α2） For less than with the eccentric rotating member（6）Pivot on the basis of theoretic positive round（α1）Shape,

   Region as defined in described（S1 or S2）Positioned at the link eccentric rotating member（6）Pivot（P3）With the connecting rod （15）With the swing rod（18）Linking portion center（P5）Line（Lcon）On.
2. 2. power transmission apparatus for vehicle according to claim 1, it is characterised in that

   In the connecting rod（15）One end（15a）Push the swing rod（18）The 1st state under, it is described as defined in region（S1 Or S2）It is the connecting rod（15）One end（15a）With in face of the swing rod（18）The opposite side in region region （S2）.
3. 3. power transmission apparatus for vehicle according to claim 1 or 2, it is characterised in that

   In the connecting rod（15）One end（15a）Draw the swing rod（18）The 2nd state under, it is described as defined in region（S1 Or S2）It is the connecting rod（15）One end（15a）Face the swing rod（18）Region（S1）.