CN104930171B - Buncher - Google Patents
Buncher Download PDFInfo
- Publication number
- CN104930171B CN104930171B CN201510122828.9A CN201510122828A CN104930171B CN 104930171 B CN104930171 B CN 104930171B CN 201510122828 A CN201510122828 A CN 201510122828A CN 104930171 B CN104930171 B CN 104930171B
- Authority
- CN
- China
- Prior art keywords
- offset
- input shaft
- shaft
- swing rod
- buncher
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Fee Related
Links
- 239000003921 oil Substances 0.000 claims abstract description 66
- 230000033001 locomotion Effects 0.000 claims abstract description 42
- 239000010687 lubricating oil Substances 0.000 claims abstract description 29
- 238000003780 insertion Methods 0.000 claims abstract description 7
- 230000037431 insertion Effects 0.000 claims abstract description 7
- 230000008859 change Effects 0.000 claims description 8
- 230000007246 mechanism Effects 0.000 claims description 6
- 230000010355 oscillation Effects 0.000 claims description 2
- 239000000314 lubricant Substances 0.000 description 11
- 230000002093 peripheral effect Effects 0.000 description 6
- 238000005461 lubrication Methods 0.000 description 3
- 230000009471 action Effects 0.000 description 2
- 230000003247 decreasing effect Effects 0.000 description 2
- 230000006866 deterioration Effects 0.000 description 2
- 238000013507 mapping Methods 0.000 description 2
- 238000003756 stirring Methods 0.000 description 2
- 230000005540 biological transmission Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 239000011148 porous material Substances 0.000 description 1
- 230000008439 repair process Effects 0.000 description 1
- 239000007921 spray Substances 0.000 description 1
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
- F16H57/00—General details of gearing
- F16H57/04—Features relating to lubrication or cooling or heating
- F16H57/042—Guidance of lubricant
- F16H57/043—Guidance of lubricant within rotary parts, e.g. axial channels or radial openings in shafts
-
- 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
- F16H57/00—General details of gearing
- F16H57/04—Features relating to lubrication or cooling or heating
- F16H57/042—Guidance of lubricant
- F16H57/043—Guidance of lubricant within rotary parts, e.g. axial channels or radial openings in shafts
- F16H57/0431—Means for guiding lubricant directly onto a tooth surface or to foot areas of a gear, e.g. by holes or grooves in a tooth flank
-
- 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
- F16H57/00—General details of gearing
- F16H57/04—Features relating to lubrication or cooling or heating
- F16H57/0434—Features relating to lubrication or cooling or heating relating to lubrication supply, e.g. pumps ; Pressure control
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Details Of Gearings (AREA)
- Transmission Devices (AREA)
Abstract
The present invention provides a kind of buncher.The buncher (1) is formed with the oil circuit (33) of the part from the reception hole (6a) of inner circumferential periphery insertion eccentric part (6), and 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), lubricating oil is discharged to the outside by it, the at least described outlet opening (33b) of the oil circuit (33) is in the state of defined offset (R1 (R10≤R1≤R1max)) is adjusted to by offset governor motion (8~14), on the extended line (Ra1) for being arranged at the pivot (P1) with the line (Ra) at the center (P2) of cam part (5) that link input shaft (2), offset (R1) corresponds to the gear ratio (TD) that can occur max. speed when flat road surface is travelled as defined in described.
Description
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,
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 sections linkage type buncher is provided with the oil circuit that periphery is penetrated into from the inner circumferential of eccentric disc, passes through
Oil pump and supply to the lubricating oil in the central shaft hole of input shaft rely on rotation with input shaft and the centrifugal force that produces and by
It is supplied to the connecting-rod bearing for the periphery for being assembled in eccentric disc.
Here, above-mentioned four sections linkage type buncher carries out gear ratio by increasing and decreasing the offset of input shaft
Change, therefore under the max. speed condition (when gear ratio is TD) that offset is larger or engine speed is higher, due to even
Inertia force of bar etc., can apply larger load, thus friction increase to the bearing of input shaft.Rubbed into due to that can produce with this
The heat of ratio, thus set lubricants capacity when according to gear ratio being TD.
However, the oil drain quantity of common oil pump is proportional to engine speed, the inertia force and engine speed of connecting rod etc.
Quadratic power it is proportional, if therefore set lubrication amount according to TD, in the relatively low high speed condition of engine speed, (gear ratio is
During OD) and the less low speed condition of offset (when gear ratio is UD) under the lubricants capacity that supplies become unnecessary (reference picture
8B).The unnecessary lubricating oil turns into the stirring resistance of bearing and causes deterioration of efficiency.
Thus, it is preferable to which the lubrication of necessary amount can either be provided under the gear ratio (during especially TD) required by lubricants capacity
Lubricating oil, can be set as appropriate quantity delivered by oil under gear ratio when OD (during UD and) in addition again.
The content of the invention
The present invention in view of above-mentioned problem and complete, its object is to realize that one kind can be according to gear ratio suitably
Set the oil supply structure of lubricants capacity.
In order to solve above-mentioned problem, reached purpose, the 1st form of the invention is a kind of buncher 1, and it has：It is defeated
Enter axle 2, it is inputted driving force from traveling with driving source；Output shaft 3, it is abreast configured with the input shaft 2；Driving force is defeated
Enter portion 4~7, it is by the rotation driving of input shaft 2；Toggle 20, it has the swing rod linked with the output shaft 3
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 is defeated
When entering 1 circle of rotation of portion 4, the swing rod 18 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 in the swing rod 18 to another side oscillation
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 enough rotated 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 rotate mode store 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 part 6, the cam part 5 is to clip the external tooth 7a of the pinion shaft 7
Mode is adjacent in the axial direction, and the buncher 1 is formed with the storage from eccentric part 6 described in the insertion of inner circumferential periphery
The oil circuit 33 of a hole 6a part, the oil circuit 33 has：Ingate 33a, it is by the reception hole 6a confessions from the eccentric part 6
To lubricating oil；And outlet opening 33b, lubricating oil is discharged to the outside by it, and at least described outlet opening 33b of the oil circuit 33 is logical
Cross the offset governor motion 8~14 to be adjusted in the state of defined offset R1 (R10≤R1≤R1max), be arranged at
On the extended line Ra1 for the line Ra for linking the pivot P1 of the input shaft 2 and the center P2 of the cam part 5, the regulation
Offset R1 correspond to can occur the gear ratio TD of max. speed when flat road surface is travelled.
In addition, as the 2nd form of the present invention, the ingate 33a and the outlet opening 33b of the oil circuit 33 are set
In on the pivot P1 and the center P2 of the cam part 5 line Ra extended line Ra1 for linking the input shaft 2.
In addition, as the 3rd form of the present invention, the buncher 1 is by making the input shaft 2 and the little gear
Axle 7 rotates to maintain the offset R1 with same speed, and by making the input shaft 2 and the pinion shaft 7 with not
The offset R1 is changed with speed rotation, the internal tooth 6b of the eccentric part 6 has when the offset R1 becomes from minimum
With the external tooth 7b regions engaged and out of mesh region S during for maximum, the ingate 33a of the oil circuit 33 is formed at
The bottom of the tooth of the out of mesh region S.
In accordance with the invention it is possible to which realize a kind of can suitably set the oil supply structure of lubricants capacity according to gear ratio.
Specifically, according to the 1st form of the present invention, lubricants capacity is most when gear ratio is TD, in change in addition
Lubricating oil can be set as appropriate amount by speed than lower, therefore, it is possible to suppress the excess supply of lubricating oil by simple structure,
And friction can be reduced.
In addition, according to the 2nd form of the present invention, the centrifugal action of maximum can be made when gear ratio is TD in lubrication
Oil.
In addition, according to the 3rd form of the present invention, it can be ensured that the internal tooth 6b's of eccentric part 6 engages with little gear 7a
Partial intensity.
Description according to a preferred embodiment of the present invention, other objects and advantages of the present invention are for art technology
It will be apparent from for personnel.In the description, refer to the attached drawing shows the example of the present invention.However, such
Example is not intended to exhaustive various embodiments of the present invention, therefore, should refer to claims following the description to 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 from the offset governor motion, connecting rod and swing rod of end on observation Fig. 1 buncher.
Fig. 3 A-3D are the figures of the change of offset that are brought of offset governor motion for the buncher for representing Fig. 1.
Fig. 4 A-4C are change and the pendulum of swing rod for representing the offset that the offset governor motion of present embodiment is brought
The figure of the relation of the swing angle scope of dynamic motion.
Fig. 5 is the figure of the gear ratio mapping for the buncher for representing present embodiment.
Fig. 6 is the figure for schematically showing the oil circuit on the toggle for being arranged at present embodiment.
Fig. 7 A-7C are the figures for schematically showing the oil circuit on the toggle for being arranged at present embodiment.
Fig. 8 A-8B are the figures of the effect for the oil circuit that explanation is arranged on the toggle of present embodiment.
Fig. 9 is the figure for the lubricating oil supplies for representing the buncher for 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, 18：Swing rod,
20：Toggle, 31：1st oil circuit, 32：2nd oil circuit, 33：3rd oil circuit, 33a：Ingate, 33b：Outlet opening.
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) make the rotary speed of output shaft be the speed changer of " 0 ", i.e. so-called IVT (Infinity for infinitely great (∞)
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, 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, 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 provided with heart P3 eccentric positions therefrom, to clip the reception hole
6a mode, 1 group of cam disc 5 is supported to 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) the center P2 apart from Ra and from cam disc 5 is to the center P3 of eccentric disc 6 apart from Rb
It is identical.In addition, being 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 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.In addition, 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
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 is supported in the way of rotation and revolution 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.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, as 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 setting the rotating speed of central gear 9 as gear ratio that Ns, the 1st gear ring 10 rotating speed are NR1, 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 from P1 to P2 apart from Ra with from P2 to P3 apart from Rb phases
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 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, swing rod 18 is linked with via the one-way clutch 17 of mechanism is prevented 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 rotate to side centered on the center of rotation axis P4 of output shaft 3
Axle 3, makes swing rod 18 be dallied relative to output shaft 3 in the case where being intended to rotate to opposite side.
Provided with end 18a is swung on swing rod 18, be provided with the 18a of end being 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 that connecting rod 15 be connected with swing rod 18
Knot gets up.In addition, 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 is as shown in figure 1, with total 6 crank connecting links
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.
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 transmitted to output shaft 3 by the moment of torsion of the oscillating motion generation of 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 being transmitted to output shaft 3 by the moment of torsion of the oscillating motion generation of swing rod 18.6
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 to make the state that offset R1 is " maximum ", and pinion shaft 7 and eccentric disc 6 are 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 to make offset R1 for less than Fig. 3 A " in " state, Fig. 3 C represent to make offset R1
For the state of " small " that is further less than 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 for the offset R1 that the offset governor motion 4 of present embodiment is brought
Oscillating motion swing angle scope relation.
Fig. 4 A represent during " maximum " that offset R1 is Fig. 3 A the swing rod 18 of (when gear ratio i is minimum) 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 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 big (gear ratio i for) 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 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.
Then, reference picture 5 to Fig. 9 illustrates the crank connecting link of present embodiment to the oil supply structure ＞ of ＜ toggles
The oil supply structure of the connecting-rod bearing 16 of mechanism 20.
The buncher 1 of present embodiment is in order to solve to produce the class of the excess supply of lubricating oil due to gear ratio
Topic, with following structure：The inner circumferential insertion from the reception hole 6a of eccentric disc 6 is formd on the specific position of eccentric disc 6
To the oil circuit of periphery, the lubricating oil of necessary amount can be provided under the gear ratio (during especially TD) for needing lubricants capacity, and
And lubricating oil can be set as to appropriate quantity delivered under gear ratio when OD (during UD and) in addition.
In the case that the buncher 1 of present embodiment is applied into the power drive system of automobile, according to offset
The change for the offset R1 that governor motion 4 is brought and pass to the characteristic of output shaft torque based on vehicle of output shaft 3 etc., such as
Gear ratio mapping graph shown in Fig. 5 changes like that.
In Figure 5, gear ratio i be maximum deceleration than between side~UD (low or first gear) (offset R1 setting R10 with
Under situation) when, output shaft torque turn into by the determinations such as the coefficient of friction of driving wheel of the vehicle slip limit (maximum),
Hereafter, as gear ratio i is (most high-grade from TD：The gear ratio i) that max. speed can occur is transferred to OD (top gears：Minimum subtracts
Speed is than side), output shaft torque is gradually reduced (offset R1 more increases, and output shaft torque is more reduced), and (offset R1 is in OD
Maximum R1max) when for minimum.
Fig. 6 schematically shows the oil circuit for the toggle 20 for being arranged at present embodiment.
As shown in fig. 6, in the present embodiment, in order to will not be according to gear ratio when supplying lubricating oil to the connecting-rod bearing 16
And require oil mass and supply oil mass between produce it is inconsistent, provided with the 1st to the 3rd oil circuit 31~33, the 1st to the 3rd oil circuit 31
~33 insertion pinion shafts 7 and by the space between external tooth 7a or pinion bearing 7b and cam disc 5, and from eccentric disc 6
Reception hole 6a inner circumferential penetrate into periphery.
1st oil circuit 31 is formed as the hollow bulb extended in the inside of pinion shaft 7 along central axis.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 external tooth 7a or pinion bearing 7b and
Space connection between cam disc 5.3rd oil circuit 33 is formed as one of the reception hole 6a from inner circumferential periphery insertion eccentric disc 6
Point, and be supplied to from the 2nd oil circuit 32 and small tooth is reached by space with ingate 33a and outlet opening 33b, ingate 33a
Lubricating oil is discharged to the outside by the external tooth 7a of wheel shaft 7 lubricating oil, outlet opening 33b.In addition, the outlet opening 33b of the 3rd oil circuit 33
It can not be located on the outer peripheral face of eccentric disc 6.
Specifically, at least outlet opening 33b of the 3rd oil circuit 33, it is preferably entrance when from end on observation shown in Fig. 6
Hole 33a and outlet opening 33b, which are arranged at, links the center of rotation axis P1 of input shaft 2 with the center P2 of cam disc 5 and from P1 to P2
On the straight line Ra of extension extended line Ra1.Moreover, offset R1_TD now is at defined scope (R10≤R1≤R1max)
It is interior, and correspond to the gear ratio (TD) that can occur max. speed when flat road surface is travelled.
As shown in figure 9, the lubricating oil sprayed from oil pump V distributes oil mass by throttle orifice etc., the of the side of input shaft 2 is provided to
The driving factors such as 1 oil circuit 31, the swing rod 18 of the side of output shaft 3, the differential gear linked with output shaft 3 and drive shaft.In addition, by oil
Pump V is supplied to the lubricating oil of the 1st oil circuit 31 to pass through the space between pinion bearing 7b and cam disc 5, arrival from the 2nd oil circuit 32
The ingate 33a of 3rd oil circuit 33.In addition, rotation of the lubricating oil discharged from the outlet opening 33b of the 3rd oil circuit 33 by eccentric disc 6
The brought centrifugal force of motion and disperse and be provided to the connecting-rod bearing 16.
Here, reference picture 7A-7C and Fig. 8 A-8B, illustrates the profit sprayed when gear ratio is TD, UD, OD from the 3rd oil circuit 33
The difference of lubricating oil pressure.In addition, let it be assumed, for the purpose of illustration, that secure eccentric disc 6 in Fig. 7 A-7C, and show that external tooth 7a is relative
In the action of eccentric disc 6, and under actual conditions external tooth 7a only carry out rotation and without revolution.
The lubricating oil for reaching the ingate 33a of the 3rd oil circuit 33 is sprayed by the centrifugal force of eccentric disc 6 from outlet opening 33b.
If the oil pressure of lubricating oil now is centrifugal oil pressure C, then it can be showed by following formula 1.
C=ρ LGear ratio·ω2···(1)
Here, ρ represents the density of lubricating oil, LGear ratioRepresent the input shaft 2 under each gear ratio (TD, UD, OD) in traveling
Center of rotation axis P1 and the 3rd oil circuit 33 outlet opening 33b distance, ω represents the rotating speed (angular speed) of input shaft 2.
It can be seen from formula 1, centrifugal oil pressure C at outlet opening 33b and between the center of rotation axis P1 of input shaft 2 away from
It is proportional from L.Moreover, as shown in Figure 8 A, L when gear ratio is TD is most long.If when being TD i.e., by the gear ratio shown in Fig. 7 A
Offset R1 is labeled as R1_TD, then in R1_TD apart from LTDIt is most long, it is UD and OD in the gear ratio shown in Fig. 7 B and 7C
When (R1_UD, R1_OD) (L is gradually decreased apart from LTD＞ LUD＞ LOD)。
Therefore, as in the embodiment described in, the outlet opening 33b of the 3rd oil circuit 33 is arranged to the pivot from input shaft 2
Axis P1 is on the center P2 of the cam disc 5 straight line Ra extended extended line Ra1, so that when gear ratio is TD from outlet opening
The centrifugal oil pressure C that 33b sprays is maximum.As above, necessary lubricants capacity when gear ratio is TD can either be ensured, again can be
Gear ratio in addition reduces lubricants capacity when being UD and OD, therefore, it is possible to be carried under the gear ratio (TD) for requiring lubricants capacity
For the lubricating oil of necessary amount, and lubricating oil can be set as to appropriate supply under gear ratio (UD and OD) in addition
Measure (reference picture 8B).
In addition, as described above, the toggle 20 of present embodiment is to work as to make input shaft 2 and pinion shaft 7 with same
Offset R1 is maintained when one speed rotates and offset R1 machine is changed when making input shaft 2 and pinion shaft 7 produces speed difference
Structure, it has when make it that offset R1 becomes maximum from minimum (=0) by offset governor motion 4 according to gear ratio i,
The internal tooth 6b of eccentric disc 6 and the external tooth 7a of pinion shaft 7 regions engaged and out of mesh region.Then, the 3rd oil circuit 33 enters
Oral pore 33a as shown in Figure 7 A-7C, is formed at the internal tooth 6b of eccentric disc 6 not with the external tooth 7a of the pinion shaft 7 region S's engaged
Bottom of the tooth.As above, the ingate 33a of the 3rd oil circuit 33 is formed at the angle model which kind of offset is not engaged with external tooth 7a
The bottom of the tooth of the internal tooth 6b in S is enclosed, so as to the intensity with the external tooth 7a parts engaged for the internal tooth 6b for ensuring eccentric disc 6.
In addition, in the present embodiment, it is illustrated that reaching the 3rd oil circuit 33 from the 1st oil circuit 31 via the 2nd oil circuit 32
Oil channel structures, but as lubricating oil reach the 3rd oil circuit 33 path, for example also adjacent crank linkage 20 is mutual
, in addition also there are countless paths, needless to say in gap etc..
As described above, according to present embodiment, lubricants capacity can be suitably set according to gear ratio, therefore, it is possible to prevent
Unnecessary lubricating oil is provided under the gear ratio beyond TD and turns into the stirring resistance of bearing so that deterioration of efficiency.
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, in order that public awareness the scope of the present invention, herein proposes claims below.
Claims (3)
1. a kind of buncher (1), it has：
Input shaft (2), it is inputted driving force from traveling with driving source；
Output shaft (3), it is abreast configured with the input shaft (2)；
Driving force input unit, 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
Rotary motion is converted to the oscillating motion of the swing rod (18), when driving force input unit rotation 1 is enclosed, the swing rod (18)
Carry out 1 reciprocal oscillating motion；And
Single direction rotation prevents mechanism, and the swing rod (18) is fixed on described defeated by it when the swing rod (18) is to be swung aside
Shaft (3), the swing rod (18) be intended to make during another side oscillation the swing rod (18) relative to the output shaft (3) dally,
The buncher (1) is characterised by,
The toggle (20) has：Offset governor motion, it makes the pivot of the driving force input unit
(P3) pivot (P1) relative to the input shaft (2) is eccentric；And connecting rod (15), it links the driving force input unit
With the swing rod (18),
The driving force input unit has：Cam part (5), its relative to the input shaft (2) pivot (P1) 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), its
It can be rotated against relative to the input shaft (2) so that offset can be adjusted by the offset governor motion
(R1),
The pinion shaft (7) is supported in the input shaft (2) via pinion bearing (7b) in the way of it can rotate,
The eccentric part (6) has reception hole (6a), and the reception hole (6a) is can make the institute of the support pinion shaft (7)
The mode for stating cam part (5) rotation stores 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) has the outer edge for being supported in the eccentric part (6) in the way of it can rotate via bearing (16)
On annulus,
The cam part (5) to be 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 one of the reception hole (6a) from eccentric part (6) described in the insertion of inner circumferential periphery
The oil circuit (33) divided,
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), lubricating oil is discharged to the outside by it,
At least described outlet opening (33b) of the oil circuit (33) is being adjusted to defined bias by the offset governor motion
Measure in the state of (R1), be arranged at the center (P2) for linking the pivot (P1) of the input shaft (2) with the cam part (5)
Line (Ra) extended line (Ra1) on, it is described as defined in offset (R1) correspond to can occur most when flat road surface is travelled
The gear ratio (TD) of high speed.
2. buncher according to claim 1, it is characterised in that
The ingate (33a) of the oil circuit (33) and the outlet opening (33b) are arranged at the rotation for linking the input shaft (2)
On the extended line (Ra1) for the line (Ra) for turning center (P1) and the center (P2) of the cam part (5).
3. buncher according to claim 1 or 2, it is characterised in that
The buncher (1) is maintained by making the input shaft (2) and the pinion shaft (7) be rotated with same speed
The offset (R1), and by making the input shaft (2) and the pinion shaft (7) with friction speed rotation to change
Offset (R1) is stated,
The internal tooth (6b) of the eccentric part (6) has when the offset (R1) becomes maximum from minimum and the external tooth
The region of (7a) engagement and out of mesh region (S),
The ingate (33a) of the oil circuit (33) is formed at the bottom of the tooth of the out of mesh region (S).
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2014-057077 | 2014-03-19 | ||
| JP2014057077A JP6068381B2 (en) | 2014-03-19 | 2014-03-19 | Continuously variable transmission |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN104930171A CN104930171A (en) | 2015-09-23 |
| CN104930171B true CN104930171B (en) | 2017-07-11 |
Family
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201510122828.9A Expired - Fee Related CN104930171B (en) | 2014-03-19 | 2015-03-19 | Buncher |
Country Status (2)
| Country | Link |
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| JP (1) | JP6068381B2 (en) |
| CN (1) | CN104930171B (en) |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106555867B (en) * | 2017-01-20 | 2018-09-11 | 蔡明� | A kind of gearbox |
| CN107489757A (en) * | 2017-08-30 | 2017-12-19 | 湘电风能有限公司 | A kind of exposed gear lubricating device |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102009031506A1 (en) * | 2008-07-21 | 2010-01-28 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Adjustment arrangement for an electrical adjustment of a crank CVT |
| CN103562042A (en) * | 2011-06-02 | 2014-02-05 | 本田技研工业株式会社 | Drive system |
Family Cites Families (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5752449Y2 (en) * | 1979-08-17 | 1982-11-15 | ||
| JPH03239806A (en) * | 1990-02-19 | 1991-10-25 | Nissan Motor Co Ltd | Lubricating device of engine |
| JP5142234B2 (en) * | 2011-01-06 | 2013-02-13 | 本田技研工業株式会社 | Continuously variable transmission mechanism and automobile drive system |
| DE112012001285A5 (en) * | 2011-03-18 | 2014-01-09 | Schaeffler Technologies AG & Co. KG | transmission device |
| JP5694858B2 (en) * | 2011-06-03 | 2015-04-01 | 本田技研工業株式会社 | Lubricating oil supply structure for continuously variable transmission |
| JP2012251618A (en) * | 2011-06-03 | 2012-12-20 | Honda Motor Co Ltd | Power transmission device for vehicle |
| JP5676380B2 (en) * | 2011-07-07 | 2015-02-25 | 本田技研工業株式会社 | Four-bar link type continuously variable transmission |
| JP5825684B2 (en) * | 2012-08-09 | 2015-12-02 | 本田技研工業株式会社 | Power transmission device for vehicle |
-
2014
- 2014-03-19 JP JP2014057077A patent/JP6068381B2/en not_active Expired - Fee Related
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2015
- 2015-03-19 CN CN201510122828.9A patent/CN104930171B/en not_active Expired - Fee Related
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102009031506A1 (en) * | 2008-07-21 | 2010-01-28 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Adjustment arrangement for an electrical adjustment of a crank CVT |
| CN103562042A (en) * | 2011-06-02 | 2014-02-05 | 本田技研工业株式会社 | Drive system |
Also Published As
| Publication number | Publication date |
|---|---|
| JP6068381B2 (en) | 2017-01-25 |
| CN104930171A (en) | 2015-09-23 |
| JP2015178877A (en) | 2015-10-08 |
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