CN104696490B - Buncher - Google Patents

Abstract

The invention provides a buncher having an input shaft, an output shaft, a driving force input portion, a crankshaft linkrod mechanism and a single direction rotary stop mechanism; the crankshaft linkrod mechanism has a swing rod, an eccentric adjusting mechanism and a linkrod; the driving force input portion has a cam portion, an eccentric part and a pinion shaft; the eccentric part has a contain hole containing the cam portion; the link rod supports an annular portion on an edge of an eccentric plate in a rotary manner, thus forming an oil path penetrating a certain part of the contain hole of the eccentric part from an inner periphery to an outer periphery; the oil path has an inlet used for supplying oil to the contain hole of the eccentric part and an outlet discharging lubrication oil to an outer side; at least the outlet of the oil path is arranged in a special zone following the conditions: when eccentric state is set by the eccentric adjusting mechanism and the linkrod enables the swing rod to swing, the annular portion of the linkrod bears most load because of counter effect of the swing rod.

Description

Buncher

Technical field

The present invention relates to the oil supply structure of 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, The reciprocating motion for being converted to connecting rod of its input shaft that will be connected with engine, by one-way clutch by the reciprocal of connecting rod Motion is converted to the rotary motion of output shaft.

The connecting rod load of above-mentioned four sections linkage type buncher can occur in a period of the circle of eccentric part rotation 1 Change, the connecting-rod bearing for bearing the load bears the region of peak load within each cycle and can concentrate on specific position, should The caloric value of privileged site can increase.Accordingly, it would be desirable to be cooled down to the privileged site concentrated supply lubricating oil.

The content of the invention

The present invention in view of above-mentioned problem and complete, its object is to realize a kind of oil supply structure, its by company The privileged site of the caloric value increase of rod bearing supplies necessary minimal lubricating oil such that it is able to which efficiency carries out cold well But.

In order to solve above-mentioned problem, reached purpose, the 1st form of the invention provides a kind of buncher 1, and it has： Input shaft 2, it is input into driving force from traveling with driving source；Output shaft 3, it is abreast configured with the input shaft 2；Driving force Input unit 4~7, it is by the rotation driving of the input shaft 2；Toggle 20, it has the pendulum linked with the output shaft 3 Bar 18, the rotary motion of the driving force input unit 4~7 is converted to the oscillating motion of the swing rod 18, when the driving force When the rotation of input unit 41 is enclosed, the swing rod carries out 1 reciprocal oscillating motion；And single direction rotation prevents mechanism, it is described The swing rod 18 is fixed on the output shaft 3 when swing rod 18 is to be swung aside, is intended to another side oscillation in the swing rod 18 When the swing rod 18 is dallied relative to the output shaft 3, wherein, the toggle 20 has：Offset adjusts machine Structure 8~14, it makes the pivot P3 of the driving force input unit 4~7 inclined relative to the pivot P1 of the input shaft 2 The heart；And connecting rod 15, it links the driving force input unit 4 and the swing rod 18, and the driving force input unit 4~7 has：It is convex Wheel portion 5, it is prejudicially rotated integrally relative to the pivot P1 of the input shaft 2；Eccentric part 6, it is can rotate Mode is supported in the cam part 5；And pinion shaft 7, it can be rotated against relative to the input shaft 2 so that Offset R1 can be adjusted by the offset governor motion 8~14, the pinion shaft 7 is via pinion bearing 7b with energy The mode of enough rotations is supported in the input shaft 2, and the eccentric part 6 has a reception hole 6a, and reception hole 6a is can make branch Support the pinion shaft 7 the cam part 5 rotation mode receive the cam part 5, be formed with the reception hole 6a with The pinion shaft 7 external tooth 7a engagement internal tooth 6b, the connecting rod 15 have via bearing 16 in the way of it can rotate branch Support in the annulus on the outer edge of the eccentric disc, the cam part 5 is in the way of the external tooth 7a for clipping the pinion shaft 7 It is adjacent in the axial direction, the buncher 1 is formed with the reception hole 6a from eccentric part 6 described in the insertion of inner circumferential periphery A part oil circuit 33, the oil circuit 33 has：Ingate 33a, it is supplied profit from the reception hole 6a of the eccentric part 6 Lubricating oil；And outlet opening 33b, be discharged to the outside for lubricating oil by it, at least described outlet opening 33b of the oil circuit 33 be arranged at as Under specific region, the specific region be included in by the offset governor motion 8~14 be adjusted to regulation offset R1b In the state of, when the connecting rod 15 makes the swing rod 18 carry out oscillating motion, the annulus 15a of the connecting rod 15 is by from institute The load stated reaction force that swing rod 18 is subject to and bear is maximum region.

Additionally, as the 2nd form of the invention, if by the company of the offset governor motion 8~14 and the connecting rod 15 The center P3 of knot point as input side fulcrum, using the center P5 of the swing rod 18 and the linking portion of the connecting rod 15 as defeated Go out collateral point, then the outlet opening 33b of the oil circuit 33 is set in the end on observation from the input shaft 2 and the output shaft 3 It is placed on the link input side fulcrum and the line Lcon of the outlet side fulcrum, the offset R1b of the regulation corresponds to institute The output torque for stating output shaft 3 is maximum gear ratio UD.

Additionally, used as the 3rd form of the invention, the offset R1b of the regulation corresponds to the output torsion of the output shaft 3 Square is the minimum speed reducing ratio in maximum gear ratio Lower-UD~UD.

Additionally, used as the 4th form of the invention, the buncher is by making the input shaft 2 and the little gear Axle 7 maintains the offset so that same speed rotates, by making the input shaft 2 with the pinion shaft 7 with friction speed Rotate and change the offset R1, even if there is the internal tooth 6b of the eccentric part 6 the offset R1 to be changed into most from minimum The big region also engage with the external tooth 7b and out of mesh region V, described in the ingate 33a of the oil circuit 33 is formed at The bottom of the tooth of out of mesh region V.

Additionally, as the 5th form of the invention, prolonging along its center axis in being internally formed for the pinion shaft 7 The 1st hollow oil circuit 31 stretched, with from the 1st oil circuit 31 radially pinion shaft 7 described in insertion and with the little gear The mode of the connection of space 34 between bearing 7b, the external tooth 7a and the cam part 5 this three is formed with the 2nd oil circuit 32, from The lubricating oil of the external tooth 7a that the 2nd oil circuit 32 reaches the pinion shaft 7 by the space 34 is supplied to the oil The ingate 33a on road 33.

According to the present invention, necessary minimal lubrication is supplied by the privileged site increased to the caloric value of the connecting-rod bearing Oil such that it is able to which efficiency is cooled down well.

Specifically, the 1st form of the invention, is supplied by the privileged site increased to the caloric value of the connecting-rod bearing 16 Necessary minimal lubricating oil such that it is able to which efficiency is cooled down well in the case where the load of oil pump is not increased, and And the friction caused by the shearing force of lubricating oil can be suppressed in Min..

Additionally, the 2nd and the 3rd form of the invention, supplies by the caloric value highest region V of the connecting-rod bearing 16 Lubricating oil such that it is able to which efficiency is cooled down well in the case where the load of oil pump is not increased.

Additionally, the 4th form of the invention, it can be ensured that outer with pinion shaft 7 on the internal tooth 6b of eccentric part 6 The intensity of the part of tooth 7a engagements.

Additionally, the 5th form of the invention, it can be ensured that pass through from the 1st oil circuit 31 of the hollow inside of pinion shaft 7 Radially the 2nd oil circuit 32 of insertion pinion shaft 7 and reach the feed path of the lubricating oil of the external tooth 7a of pinion shaft 7.

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 An example of the 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 of the buncher for representing present embodiment.

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

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

Fig. 4 A-4C are pendulum of the change with swing rod for representing the offset that the offset governor motion of present embodiment is brought The figure of the relation of the pendulum angle scope of dynamic motion.

Fig. 5 A-5B are the figures of the change for representing the connecting rod load that the connecting rod of toggle is born.

Fig. 6 is the figure of the gear ratio mapping of the buncher for representing present embodiment.

Fig. 7 A-7B are the figures of the change of the output shaft torque of the buncher for representing present embodiment.

Fig. 8 A-8B are the figures for representing the oil circuit being formed on the toggle of present embodiment.

Fig. 9 A-9B are the figures for representing the oil circuit being formed on the toggle of present embodiment.

Figure 10 is the figure of the scope of the oil circuit for representing the toggle to form present embodiment.

Label declaration

1：Buncher, 2：Input shaft, 3：Output shaft, 4：Offset governor motion, 5：Cam disc, 6：Eccentric disc, 6a： Reception hole, 6b：Internal tooth, 7：Pinion shaft, 7a：External tooth, 7b：Pinion bearing, 14：Offset regulation driving source, 14a：Rotation Rotating shaft, 15：Connecting rod, 15a：Big footpath annulus, 15b：Path annulus, 16：The connecting-rod bearing, 17：One-way clutch (single direction rotation Prevent mechanism), 18：Swing rod, 20：Toggle, 31：1st oil circuit, 32：2nd oil circuit, 33：3rd oil circuit, 33a：Entrance Hole, 33b：Outlet opening, 34：Space.

Specific embodiment

Hereinafter, the implementation method that present invention will be described in detail with reference to the accompanying.Additionally, embodiments described below is as this One of the realization rate of invention, the present invention can be applied to carried out to mode is implemented as follows in the range of its purport not departing from Structure after modification or deformation.In addition, buncher of the 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 the rotary speed/output shaft of i=input shafts Rotary speed) make the rotary speed of output shaft for infinitely great (∞) for speed changer, the i.e. so-called IVT (Infinity of " 0 " 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 in the horizontal direction separate 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 respectively driving force input unit, be arranged to be with the center of rotation axis P1 of input shaft 2 Central rotation, with the cam disc 5 as cam part, the eccentric disc 6 as eccentric part and pinion shaft 7.

Cam disc 5 is disc-shape, is rotated integrally with 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 pass 6 groups Cam disc 5 is in input shaft 2 circumferentially around one week.

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

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

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

Incision hole 2a is formed 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 The internal tooth 6b engagements of 6 reception hole 6a.

Differential attachment 8 is planetary gears, and it has the 1st gear ring 10 that central gear 9 and input shaft 2 link and small The 2nd gear ring 11 that gear shaft 7 links and by ladder little gear 12 by can in the way of rotation and revolution axle support planet carrier 13, what the ladder little gear 12 was 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 constituted.Additionally, the central gear 9 of differential attachment 8 with by the driving of pinion shaft 7 motor drive mechanism into bias Amount regulation is linked with the rotary shaft 14a of driving source 14.

And, 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, as central gear 9, the 1st gear ring 10, the 2nd gear ring 11 and row The lock-out state that carrier 13 this 4 key elements cannot be rotated against, the pinion shaft 7 linked with the 2nd gear ring 11 with input The same speed of axle 2 rotates.

Additionally, 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 for NR1, the gear ring 10 of central gear 9 and the 1st gear ratio (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 Outward, 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 number of teeth of the number of teeth of the large-diameter portion 12a of terraced little gear 12/minor diameter part 12b)) 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 from P1 to P2 apart from Ra with from P2 to P3 apart from Rb phases Same mode is eccentric.Center P3 therefore, it is possible to make eccentric disc 6 is located at the center of rotation axis P1 identical lines with input shaft 2 On, 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 be " 0 ".

Connecting rod 15 is supported by the way 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, has 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.It is unidirectional 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 be rotated to side Axle 3, makes swing rod 18 be dallied relative to output shaft 3 in the case where being intended to be rotated to opposite side.

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

Then, reference picture 2~Fig. 4 A-4C illustrate the song of the buncher of present embodiment to ＜ toggles ＞ 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 Constitute 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 heart axis P4.The buncher 1 of present embodiment adds up to 6 crank connecting links as shown in figure 1, having Mechanism 20.

In toggle 20, in the offset R1 not in the case of " 0 " of offset governor motion 4, 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.

And, one-way clutch 17 is provided between swing rod 18 and output shaft 3, therefore in the case where swing rod 18 is pushed, The moment of torsion produced by the oscillating motion of swing rod 18 is fixed and transmitted to output shaft 3 to swing rod 18 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 produced 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.

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

Fig. 3 A represent the state for making offset R1 be " maximum ", and pinion shaft 7 and eccentric disc 6 are with so that the rotation of input shaft 2 Turn the mode that central axis P1 is arranged on straight line with the center P2 of cam disc 5 with the center P3 of eccentric disc 6 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 are represented makes offset R1 To be further less than the state of " small " of Fig. 3 B.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 is positioned with one heart with the center P3 of eccentric disc 6.Gear ratio i now is infinity (∞)。

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

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

It can be seen from Fig. 4 A-4C, as offset R1 diminishes, the pendulum 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 no longer swings.

Then, reference picture 5A-5B to Figure 10 illustrates the crank of present embodiment to the oil supply structure ＞ of ＜ toggles The oil supply structure of the connecting-rod bearing 16 of linkage 20.

The buncher 1 of present embodiment as shown in Figure 5A, eccentric disc 6 rotation 1 circle 1 cycle in a period of, The load (hereinafter referred to as connecting rod load) for being applied to the big footpath annulus 15a of connecting rod 15 can significantly change.Therefore, such as Fig. 5 B institutes Show, the position that the connecting-rod bearing 16 for bearing connecting rod load bears maximum load Nmax in each cycle can concentrate on big footpath annulus 15 specific region X, the caloric value of region X can increase.Thus, present embodiment is a kind of to the connecting rod for bearing connecting rod load The structure that specific region X concentrated supply lubricating oil on bearing 16 is cooled down.

In the case that the buncher 1 of present embodiment is applied into the power drive system of automobile, according to offset The change of the offset that governor motion 4 is brought and the output shaft torque that passes to output shaft 3 is based on characteristic etc. of vehicle, such as scheme Gear ratio mapping graph shown in 6 changes like that.

In figure 6, (offset R1 exists between gear ratio i is Lower-UD (maximum deceleration is than side)~UD (low or first gear) The situation of below setting R1b) when, output shaft torque turns into by the skidding pole of the determinations such as the coefficient of friction of driving wheel of the vehicle Limit (maximum), hereafter, as gear ratio i is (most high-grade from TD：The gear ratio i) for max. speed occur is transferred to OD (top gears： Minimum deceleration is than side), output shaft torque is gradually reduced (offset R1 gets over increase, and output shaft torque gets over reduction).

Additionally, in figure 6, even if in the case where output shaft torque is slip limit, sharing the song of the output shaft torque The quantity of handle linkage 20 is also not identical all the time.For example, in the case where offset R1 is the R1a close to 0, such as Fig. 7 A institutes Show, in certain moment t, the quantity for sharing the toggle 20 of certain output shaft torque is 4.On the other hand, in offset R1 is in the case that more than R1a, output shaft torque will start the R1b before reducing, as shown in Figure 7 B, with Fig. 7 A identicals The quantity that moment t shares the toggle 20 of output shaft torque is 3.That is, offset R1 gets over increase, then 1 crank connects The connecting rod load that linkage 20 is shared is bigger.

Additionally, being the average of output shaft torque in the interval of Lower-UD~UD in gear ratio i it can be seen from Fig. 7 A-7B Value is roughly the same, and as shown in Figure 7 B, offset R1 bigger (gear ratio i is closer to UD) is then applied to 1 toggle 20 connecting rod load is bigger, thus the maximum load condition that the connecting-rod bearing 16 is born is in the interval of Lower-UD~UD When speed reducing ratio is minimum UD (offset R1 is R1b).

Fig. 8 A-8B and Fig. 9 A-9B represent the oil circuit being arranged on the toggle 20 of present embodiment.Fig. 8 A are figures The A-A sectional views of 5B, Fig. 8 B are the outside drawings of pinion shaft.Additionally, Fig. 9 A are the outside drawings of eccentric disc, Fig. 9 B are outside eliminating The outside drawing of the pinion shaft, cam disc and eccentric disc of tooth and pinion bearing.

As shown in Fig. 8 A-8B and Fig. 9 A-9B, in the present embodiment, in order to be supplied to the connecting-rod bearing 16 of specific region X Lubricating oil, is formed with insertion pinion shaft 7 and by the space between pinion bearing 7b, external tooth 7a and cam disc 5 this three 34 and the oil circuit 31~34 of the inner circumferential periphery insertion from the reception hole 6a of eccentric disc 6.

1st oil circuit 31 is formed as the hollow bulb extended along central axis in the inside of pinion shaft 7.The shape of 2nd oil circuit 32 As from the 1st oil circuit 31 towards pinion bearing 7b radially insertion pinion shafts 7, and with pinion bearing 7b, external tooth 7a and Space 34 between cam disc 5 this three connects.3rd oil circuit 33 is formed as the reception hole from inner circumferential periphery insertion eccentric disc 6 A part of 6a, and with ingate 33a and outlet opening 33b, ingate 33a is supplied to from the 2nd oil circuit 32 by space 34 And the lubricating oil of the external tooth 7a of pinion shaft 7 is reached, be discharged to the outside for lubricating oil by outlet opening 33b.From outlet opening 33b discharges Lubricating oil dispersed by the centrifugal force produced by the rotary motion as eccentric disc 6, and be supplied to the connecting-rod bearing 16.

At least outlet opening 33b of the 3rd oil circuit 33 is arranged on the X of specific region, and specific region X includes making pendulum when connecting rod 15 When bar 18 carries out oscillating motion, the company that the big footpath annulus 15a of connecting rod 15 is born due to the reaction force being subject to from swing rod 18 Bar load is maximum region.

It is specific as shown in Figure 5 B, if by offset governor motion 4 (eccentric disc 6) and the center of the linking portion of connecting rod 15 P3, using the center P5 of swing rod 18 and the linking portion of connecting rod 15 as outlet side fulcrum, will link these as input side fulcrum The line of input side fulcrum and outlet side fulcrum as Lcon, then at least outlet opening 33b, preferably ingate 33a of the 3rd oil circuit 33 and Outlet opening 33b is arranged on Lcon when from end on observation.And, it is maximum that offset R1 now corresponds in connecting rod load Gear ratio i be offset R1b when speed reducing ratio is minimum UD in the interval of Lower-UD~UD.As above, by connecting rod Supply lubricating oil in caloric value highest region on bearing such that it is able to which efficiency is well in the case where the load of oil pump is not increased Cooled down.

In addition, in the present embodiment, illustrating from the 1st oil circuit 31 and reaching the 3rd oil circuit 33 via the 2nd oil circuit 32 The structure of oil circuit, and as lubricating oil reach the 3rd oil circuit 33 path, for example can also enumerate adjacent toggle 20 it Between gap etc., in addition also there are myriad situations, this is self-evident.

As described above, the toggle 20 of present embodiment is a kind of synchronized with phase with pinion shaft 7 in input shaft 2 Maintained during degree rotation offset R1, when input shaft 2 and pinion shaft 7 produce speed difference change offset R1 mechanism, pressing According to gear ratio i by offset governor motion 4 cause offset R1 from minimum (=0) be changed to maximum when, there is eccentric disc 6 Region and out of mesh region that internal tooth 6b is engaged with the external tooth 7a of pinion shaft 7.Then, as shown in Figure 10, by the 3rd oil circuit 33 Ingate 33a be formed at the bottom of the tooth of the region V that the internal tooth 6b of eccentric disc 6 is not engaged with the external tooth 7a of pinion shaft 7.As above, The angle do not engaged with external tooth 7a in the case of offset is at all events planted by the way that the ingate 33a of the 3rd oil circuit 33 is formed at The bottom of the tooth of the internal tooth 6b in degree scope V such that it is able to ensure the internal tooth 6b of eccentric disc 6 the part engaged with external tooth 7a it is strong Degree.

As above, according to present embodiment, supplied by the privileged site increased to the caloric value on the connecting-rod bearing 16 necessary Minimal lubricating oil such that it is able to which efficiency is cooled down well in the case where the load of oil pump is not increased, and energy Enough frictions by caused by the shearing force of lubricating oil suppress in Min..

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 (5)

1. a kind of buncher (1), it has：

Input shaft (2), it is input into driving force from traveling with driving source；

Output shaft (3), it is abreast configured with the input shaft (2)；

Driving force input unit (4~7), it is by the input shaft (2) rotation driving；

Toggle (20), it has the swing rod (18) linked with the output shaft (3), by the driving force input unit (4 ~rotary motion 7) is converted to the oscillating motion of the swing rod (18), when the driving force input unit (4) rotation 1 is enclosed, institute Stating swing rod carries out 1 reciprocal oscillating motion；And

Single direction rotation prevents mechanism, and be fixed on for the swing rod (18) when the swing rod (18) is to be swung aside described defeated by it Shaft (3), makes the swing rod (18) be dallied relative to the output shaft (3) when the swing rod (18) is intended to another side oscillation,

The toggle (20) has：Connecting rod (15), it links the driving force input unit (4) and the swing rod (18),

The driving force input unit (4~7) has：Cam part (5), its pivot (P1) relative to the input shaft (2) Prejudicially rotate integrally；Eccentric part (6), it is supported in the cam part (5) in the way of it can rotate；And pinion shaft (7), it can be rotated against relative to the input shaft (2),

Characterized in that,

The toggle (20) also has：Offset governor motion (8~14), its make the driving force input unit (4~ 7) pivot (P3) is eccentric relative to the pivot (P1) of the input shaft (2),

Offset (R1) can be adjusted by the offset governor motion (8~14),

The pinion shaft (7) is supported in the input shaft (2) via pinion bearing (7b) in the way of it can rotate,

With reception hole (6a), the reception hole (6a) is can make the institute of the support pinion shaft (7) for the eccentric part (6) The mode for stating cam part (5) rotation receives the cam part (5), is formed with the reception hole (6a) and the pinion shaft (7) internal tooth (6b) of external tooth (7a) engagement,

The connecting rod (15) in the way of it can rotate via bearing (16) with being supported on the outer edge of the eccentric disc Annulus,

The cam part (5) is adjacent in the axial direction in the way of the external tooth (7a) for clipping the pinion shaft (7),

The buncher (1) is formed with of the reception hole (6a) from eccentric part (6) described in the insertion of inner circumferential periphery The oil circuit (33) for dividing,

The oil circuit (33) has：Ingate (33a), it supplies lubricating oil by the reception hole (6a) from the eccentric part (6)； And outlet opening (33b), be discharged to the outside for lubricating oil by it,

At least described outlet opening (33b) of the oil circuit (33) is arranged at following specific region, and the specific region is included in logical Cross the offset governor motion (8~14) to be adjusted in the state of the offset (R1b) of regulation, when the connecting rod (15) makes institute When stating swing rod (18) and carrying out oscillating motion, the annulus (15a) of the connecting rod (15) is anti-due to what is be subject to from the swing rod (18) Active force and the load born is maximum region.

2. buncher according to claim 1, it is characterised in that

If using the center (P3) of the offset governor motion (8~14) and the linking portion of the connecting rod (15) as input side Fulcrum, using the center (P5) of the swing rod (18) and the linking portion of the connecting rod (15) as outlet side fulcrum,

Then the outlet opening (33b) of the oil circuit (33) is in the end on observation from the input shaft (2) and the output shaft (3), It is arranged on the link input side fulcrum and the line (Lcon) of the outlet side fulcrum,

The output torque that the offset (R1b) of the regulation corresponds to the output shaft (3) is maximum gear ratio (UD).

3. buncher according to claim 2, it is characterised in that

The output torque that the offset (R1b) of the regulation corresponds to the output shaft (3) is maximum gear ratio (Lower-UD ~UD) in minimum speed reducing ratio.

4. buncher according to claim 1, it is characterised in that

The buncher maintains institute by making the input shaft (2) and the pinion shaft (7) so that same speed rotates Offset is stated, the offset is changed so that friction speed rotates with the pinion shaft (7) by making the input shaft (2) (R1),

The internal tooth (6b) of the eccentric part (6) though have the offset (R1) from minimum become maximum also with the external tooth The region of (7b) engagement and out of mesh region (V),

The ingate (33a) of the oil circuit (33) is formed at the bottom of the tooth of the out of mesh region (V).

5. the buncher described in any one in Claims 1-4, it is characterised in that

In the 1st hollow oil circuit (31) being internally formed along its center axis extension of the pinion shaft (7),

With from the 1st oil circuit (31) radially pinion shaft (7) described in insertion and with the pinion bearing (7b), described The mode of space (34) connection between external tooth (7a) and the cam part (5) this three is formed with the 2nd oil circuit (32),

The lubricating oil of the external tooth (7a) for reaching the pinion shaft (7) by the space (34) from the 2nd oil circuit (32) It is supplied to the ingate (33a) of the oil circuit (33).