CN105984321B - Power transmission - Google Patents

Abstract

The present invention provides a kind of power transmission, the power transmission is in due course supplies lubricating oil to the path annulus of connection connecting rod and the link pin for swinging end of swing rod, it can prevent from wearing and realizing the long-life, and can prevent link pin from producing strike note.Lubricating oil is supplied to be lubricated to the path annulus (15b) of the connecting rod (15) pivotally supported by link pin (19) and the fitting portion of the swing end (18a) of swing rod (18) from the tap (45) of oil pipe (32).Oil pipe (32) is made up of outboard tube (41) and the inside tube (42) that has oil circuit (46) and can be rotated against with outboard tube (41), pass through the rotation of the inside tube (42) with input shaft (2) synchronous rotary, only in defined phase, oil circuit (46) connects with tap (45).

Description

Power transmission

Technical field

The present invention relates to the power transmission of the drive device for vehicle.

Background technology

In the past, the buncher of known a kind of four sections linkage type, it possesses：Hollow input shaft, it is passed Driving force from driving sources such as the engines on vehicle；Output shaft, it is abreast configured with input shaft；Multiple eccentric machines Structure, they are located at input shaft；Swing rod, its by swing freely in a manner of e axle supporting in output shaft；And connecting rod, one end thereof tool There is the big footpath annulus on eccentric stiffener outside in a manner of rotating freely, another end has the swing end with swing rod The path annulus of link (referring for example to patent document 1).Buncher described in patent document 1 will be connected with engine The reciprocating motion for being converted to connecting rod of input shaft, and the reciprocating motion of connecting rod is converted into output shaft using one-way clutch Rotary motion.

Prior art literature

Patent document

Patent document 1：Japanese Unexamined Patent Publication 2012-251612 publications

The content of the invention

Invent problem to be solved

In the buncher of patent document 1, the oil line pipe configuration that lubricating oil is flowed through is in the swing end of swing rod Top, multiple taps for removal of lubricant are arranged in correspondence with swinging end on the oil line pipe, to the company of being formed at The path annulus of bar oilhole supply from tap discharge lubricating oil, so as to link connecting rod path annulus with The link pin of the swing end of swing rod is lubricated.

On the other hand, it is larger negative when starting rotation by closure of the swing rod that connecting rod drives along one-way clutch Load acts on link pin, also, when starting rotation along the direction for the connection for relieving one-way clutch, due to link pin with Chimeric gap between the path annulus of connecting rod or the embedded hole of the swing end of swing rod so that they are impinging one another and produce Impact sound.Therefore, it is intended that appropriate lubricating oil is supplied to link pin on suitable opportunity.But according to patent document 1, lubrication Oil is persistently discharged from the tap of oil line pipe all the time, and a part of lubricating oil of discharge is advantageous to the lubrication of link pin, and big portion Lubricating oil of sharing in the benefit may not effectively act as acting on.Therefore, extra load, frictional force are acted on oil pump, have room for improvement.

It is an object of the invention to provide a kind of power transmission, the power transmission is in due course to connection The path annulus of connecting rod and the link pin of the swing end of swing rod supply appropriate lubricating oil, so as to prevent fitting portion Wear and realize long service life, and can prevent link pin from producing impact sound.

Means for solving the problems

To achieve these goals, the invention of technical scheme 1 is a kind of power transmission (such as embodiment described later In power transmission TA), wherein, pair be connected with driving source (such as engine (not shown) in embodiment described later) The rotation of input shaft (such as input shaft 2 in embodiment described later) carry out speed change and to be transferred to output shaft (such as aftermentioned Embodiment in output shaft 3) power transfer unit (such as buncher 1 in embodiment described later) possess： Input side fulcrum (such as center point P 3 of the wobble-plate in embodiment described later), its from the axis of the input shaft (such as Input center axis P1 in embodiment described later) eccentric offset (such as offset R1 in embodiment described later) It is variable, and the input side fulcrum rotates together with the input shaft；One-way clutch (such as the list in embodiment described later To clutch 17), it is connected to the output shaft；Outlet side fulcrum (such as swing end 18a in embodiment described later), It is on the exterior part (such as swing rod 18 in embodiment described later) of the one-way clutch；Connecting rod (such as it is described later Connecting rod 15 in embodiment), its both ends is connected to the input side fulcrum and the outlet side fulcrum, and is back and forth transported It is dynamic；And shifting actuator (such as differential attachment 8 in embodiment described later), it changes the bias of the input side fulcrum Amount, one end of the connecting rod possesses the 1st ring portion of ring-type (such as path annulus 15b in embodiment described later), described Outlet side fulcrum possesses the 2nd ring portion (such as swing end 18a in embodiment described later) of ring-type, the 1st ring portion and 2nd ring portion is pivotally supported by link pin (such as link pin 19 in embodiment described later), the power transmission Device possesses the oil pump (such as oil pump 31 in embodiment described later) of supply lubricating oil and imported to lubrication portion by described The oil pipe (such as oil pipe 32 in embodiment described later) of the lubricating oil of oil pump supply, the oil pipe possesses：Hollow shape Outboard tube (such as outboard tube 41 in embodiment described later), it has the discharge that the lubricating oil is discharged to the lubrication portion Hole (such as tap 45 in embodiment described later), and be configured to rotate；And inside tube (the example of hollow shape The inside tube 42 in embodiment as be described hereinafter), it is configured on the outside of this in a manner of it can be rotated against with the outboard tube The inside of pipe, and with the oil circuit (such as oil circuit 46 in embodiment described later) passed through for the lubricating oil, the inner side The rotation same speed rotation of driving source described in Guan Yiyu, is provided with outlet (such as implementation described later in the inside tube Outlet 47 in mode) so that the oil circuit is formed in a period of the inside tube rotates a circle and is connected with the tap Logical connected state and the oil circuit and the disconnected dissengaged positions of the tap, the lubrication portion is the link pin, Turn into the connected state when the power transfer unit is located at defined phase.

In addition, the invention of technical scheme 2 is in the invention of technical scheme 1, the one-way clutch possesses：Multiple rollings Body (such as rolling element 17a in embodiment described later), they are configured in wedge shape space (such as in embodiment described later Space S) in, the wedge shape space is formed between the inner peripheral surface of the exterior part and the outer peripheral face of inner part；And force application part (such as helical spring 17b in embodiment described later), it exerts a force to the multiple rolling element to circumferencial direction, when described outer Part to circumferential side rotate when, defined opportunity transmit moment of torsion, when the exterior part rotates to circumferential opposite side, do not pass Torque delivery, it is described as defined in phase be the one-way clutch from torque transmission status begin breaking moment of torsion when phase.

In addition, the invention of technical scheme 3 is in the invention of technical scheme 2, the tap is configured to described in The link pin under defined phase when offset is maximum.

In addition, the invention of technical scheme 4 is in the invention of technical scheme 2 or 3, the link pin is with not revolvable side Formula is fixed on any one party in the 1st ring portion and the 2nd ring portion, and the tap is located at the axial direction one of the link pin Side, an axially end-side openings for the link pin, and axially another side closing, in the link of the link pin axle The lubrication hole radially extended is provided with to the surrounding wall portion of a side and the axial another side (such as in embodiment described later Lubrication hole 19b), from end on observation, the lubrication hole is relative to axis (such as the embodiment party described later for linking the output shaft Axis P5 in formula) be arranged on the straight line (such as straight line L in embodiment described later) of the outlet side fulcrum it is described Circumferential opposite side.

In addition, the invention of technical scheme 5 is in the invention of technical scheme 1, the one-way clutch possesses：Multiple rollings Body (such as rolling element 17a in embodiment described later), they are configured in wedge shape space (such as in embodiment described later Space S) in, the wedge shape space is formed between the inner peripheral surface of the exterior part and the outer peripheral face of inner part；And force application part (such as helical spring 17b in embodiment described later), it exerts a force to the multiple rolling element to circumferencial direction, when described outer Part to circumferential side rotate when, defined opportunity transmit moment of torsion, when the exterior part rotates to circumferential opposite side, do not pass Torque delivery, the defined phase are the phases when one-way clutch transmits moment of torsion since moment of torsion off-state.

In addition, the invention of technical scheme 6 is in the invention of technical scheme 5, the tap is configured to towards as follows The offset when it is described as defined in the link pin under phase, the wherein offset is that the output of the output shaft is turned round Square is maximum offset.

In addition, the invention of technical scheme 7 is in the invention of technical scheme 5 or 6, the link pin is with not revolvable side Formula is fixed on any one party in the 1st ring portion and the 2nd ring portion, and the tap is located at the axial direction one of the link pin Side, an axially end-side openings for the link pin, and axially another side closing, in the link of the link pin axle The lubrication hole radially extended is provided with to the surrounding wall portion of a side and the axial another side (such as in embodiment described later Lubrication hole 19b), from end on observation, the lubrication hole is relative to axis (such as the embodiment party described later for linking the output shaft Axis P5 in formula) be arranged on the straight line (such as straight line L in embodiment described later) of the outlet side fulcrum it is described Circumferential side.

The effect of invention

According to the invention described in technical scheme 1, from the tap of oil pipe to the connecting rod pivotally supported by link pin The fitting portion supply lubricating oil of 1st ring portion and the 2nd ring portion of outlet side fulcrum.Oil pipe is by outboard tube and with oil circuit and can be with The inside tube that outboard tube rotates against is formed, and by the rotation of inside tube, only in defined phase, oil circuit turns into tap Connected state.Thus, lubricating oil only is supplied on the opportunity of required lubricating oil, therefore lubricating oil will not flow out in vain, so as to lubricate Efficiency improves.

According to the invention described in technical scheme 2, the defined phase for supplying lubricating oil is the moment of torsion biography from one-way clutch The state of passing begins breaking phase during moment of torsion, therefore link pin when can reduce moment of torsion missing and the 1st ring portion or the 2nd ring portion Strike note caused by collision, so as to undisturbedly operate power transmission.

According to the invention described in technical scheme 3, tap is configured to maximum towards offset, from one-way clutch Torque transmission status begins breaking link pin during moment of torsion, thus can will lubrication load suppress it is relatively low in the state of, more Effectively reduce strike note during moment of torsion missing.

According to the invention described in technical scheme 4, link pin diametrically has between the 1st ring portion or the 2nd ring portion Fitting portion supplies the lubrication hole of lubricating oil, and the lubrication hole is relative to the axis for linking output shaft and the straight line quilt at the center of link pin The direction of rotation side of exterior part idle running is arranged on, the position supply lubricating oil of strike note is produced during therefore, it is possible to be lacked to moment of torsion, Produced so as to more effectively suppress sound, improve commodity value.

According to the invention described in technical scheme 5, the defined phase for supplying lubricating oil is broken from the moment of torsion of one-way clutch Open state start transmit moment of torsion when phase, therefore can will lubrication load suppress it is relatively low in the state of, reduce moment of torsion pass Strike note when passing, so as to undisturbedly operate power transmission.

According to the invention described in technical scheme 6, tap be configured to towards under following offset from one-way clutch The moment of torsion off-state of device start transmit moment of torsion when phase under link pin, the wherein offset is the output torque of output shaft For maximum offset, therefore can will lubrication load suppress it is relatively low in the state of, more effectively reduce moment of torsion transmit when Strike note.Furthermore it is possible to abrasion when suppressing high capacity, so as to improve durability.

According to the invention described in technical scheme 7, link pin diametrically has between the 1st ring portion or the 2nd ring portion Fitting portion supplies the lubrication hole of lubricating oil, and the lubrication hole is relative to the axis for linking output shaft and the straight line quilt at the center of link pin Direction of rotation side when exterior part starts to be fixed on inner part is arranged on, strike note is produced during therefore, it is possible to be transmitted to moment of torsion Position supplies lubricating oil, produces so as to more effectively suppress sound and improves durability.

Brief description of the drawings

Fig. 1 is the sectional view of the power transmission of the 1st embodiment of the present invention.

Fig. 2 is Fig. 1 sectional view along II-II line.

Fig. 3 is the explanation figure from the main portions for the power transmission for axially showing Fig. 1.

Fig. 4 is the explanation figure of the change of the offset for the eccentric stiffener for illustrating Fig. 1.

Fig. 5 be the offset for showing eccentric stiffener change and swing rod oscillating motion angle of oscillation θ 2 relation explanation Figure, wherein the angle of oscillation of the oscillating motion of swing rod when (a) shows offset maximum, (b) shows swing rod when offset is medium Oscillating motion angle of oscillation, (c) shows the angle of oscillation of the oscillating motion of the swing rod of offset hour.

Fig. 6 is to show the curve with the change of relative, swing rod the angular velocity omega 2 of change of the offset of eccentric stiffener Figure.

Fig. 7 is the song for showing the state that output shaft differs 60 degree of 6 four section linkages by phase and rotated respectively Line chart.

Fig. 8 (a) is Fig. 2 sectional view along line A-A, and Fig. 8 (b) is Fig. 2 sectional view along line B-B, Fig. 8's (c) be Fig. 1 the sectional view along line C-C, Fig. 8 (d) is Fig. 1 sectional view along line D-D, and Fig. 8 (e) is Fig. 1 along E-E The sectional view of line, Fig. 8 (f) is Fig. 1 sectional view along F-F lines.

Fig. 9 is the schematic diagram of the position relationship of the swing end of the tap and swing rod that show oil pipe.

Figure 10 is the angle of oscillation and the curve map of the relation of transmission moment of torsion for showing swing rod when offset is maximum.

Figure 11 is the schematic diagram for showing to supply the state of lubricating oil from the tap of oil pipe to link pin.

Figure 12 is Figure 11 sectional view along G-G lines.

Figure 13 is to show that the swing end from the tap of oil pipe to swing rod supplies lubrication according to the rotatable phase of input shaft The explanation figure of the state of oil.

Figure 14 be show the output torque of output shaft for it is maximum when a swing rod relation of the angle of oscillation with transmitting moment of torsion Curve map.

Figure 15 is the tap for the oil pipe for showing the 2nd embodiment of the present invention and the position relationship for swinging end of swing rod Schematic diagram.

Figure 16 is the schematic diagram for showing to supply the state of lubricating oil from the tap of oil pipe to link pin.

Figure 17 is Figure 16 sectional view along H-H lines.

Label declaration

1：Buncher (power transfer unit)；

2：Input shaft；

3：Output shaft；

8：Differential attachment (shifting actuator)；

15：Connecting rod；

15b：Path annulus (the 1st ring portion)；

17：One-way clutch；

17a：Rolling element；

17b：Helical spring (force application part)；

18：Swing rod (exterior part)；

18a：Swing end (outlet side fulcrum, the 2nd ring portion)；

19：Link pin；

19a：Oil circuit；

19b：Lubrication hole；

20：Four section linkages；

30：Fueller；

31：Oil pump；

32：Oil pipe；

41：Outboard tube；

42：Inside tube；

43：Fuel feeding arm；

45：Tap；

46：Oil circuit；

47A~47F：Outlet；

IDP：Inner dead point；

L：Link the axis of output shaft and the straight line of outlet side fulcrum；

ODP：Outer dead point；

P1：Input center axis (axis of input shaft)；

P3：The central point (input side fulcrum) of wobble-plate；

P5：The axis of output shaft；

R1：Offset；

S：Space；

TA：Power transmission.

Embodiment

<1st embodiment>

Hereinafter, the embodiments of the present invention are explained with reference to.The power transmission TA of present embodiment possesses： Buncher 1 as power transfer unit；And the fueller of lubricating oil is supplied to the main portions of buncher 1 30。

Buncher 1 is that gear ratio i (rotating speed of rotating speed/output shaft of i=input shafts) can be made to be infinitely great (∞) So that the rotating speed of output shaft is the speed changer of " 0 ", i.e., so-called Limitless speed variator (Infinity Variable Transmission (IVT)) one kind.

Reference picture 1~3, buncher 1 possess：Hollow input shaft 2, it receives in the conduct for eliminating diagram The rotary power of the vehicle traveling driving source such as engine or motor of combustion engine, is thus revolved centered on input center axis P1 Turn；Output shaft 3, it is configured to parallel with input shaft 2, and moves rotation via differential gear (not shown) or power transmission shaft etc. Power is transferred to the driving wheel (omitting diagram) of vehicle；And 6 eccentric stiffeners 4, they are arranged on input shaft 2.

Each eccentric stiffener 4 is made up of fixed disk 5 and wobble-plate 6.Fixed disk 5 is discoid, with from input center axis P1 Mode two that is eccentric and being rotated integrally with input shaft 2 is separately positioned on input shaft 2 by one group.Each group fixed disk 5 makes respectively Phase differs 60 degree, is configured to by 6 groups of fixed disks 5 in input shaft 2 circumferentially around one week.In addition, possess for accommodating fixation The receiving hole 6a of disk 5 discoid wobble-plate 6 in the state of bias in a manner of it can rotate freely outside consolidate embedded in each group Price fixing 5.

The central point of fixed disk 5 is set to P2, the central point of wobble-plate 6 is set to P3, wobble-plate 6 is to cause input center axle The mode that the line P1 and distance Rx of center point P 2 is equal to the center point P 2 and distance Ry of center point P 3 is eccentric relative to fixed disk 5.

The internal tooth 6b being provided with the receiving hole 6a of wobble-plate 6 between 1 group of fixed disk 5.On input shaft 2 formed with Cut hole 2a, cut hole 2a between 1 group of fixed disk 5, and make at the position relative with the eccentric direction of fixed disk 5 inner peripheral surface with Outer peripheral face connects.

Configured with one heart with input shaft 2 and the pinion shaft 7 with 6 corresponding position of wobble-plate with external tooth 7a with The mode that input shaft 2 rotates against freely is configured in hollow input shaft 2.The external tooth 7a of pinion shaft 7 is via input shaft 2 Cut hole 2a engages with the internal tooth 6b of wobble-plate 6.

Pinion shaft 7 is connected with differential attachment 8.Differential attachment 8 is made up of planetary gears, have central gear 9, with The 2nd gear ring 11 and planet carrier 13 that the 1st gear ring 10 and pinion shaft 7 that input shaft 2 links link, the planet carrier 13 is with energy Enough free rotations and the mode e axle supporting staged little gear 12 of revolution, the staged little gear 12 by with central gear 9 and The large-diameter portion 12a of 1st gear ring 10 engagement and the minor diameter part 12b engaged with the 2nd gear ring 11 are formed.

Be linked with central gear 9 motor drive mechanism by pinion shaft 7 into driving source 14 rotary shaft 14a.When making When the rotating speed of driving source 14 is identical with the rotating speed of input shaft 2, the gear ring 10 of central gear 9 and the 1st is rotated with same speed, sun tooth The 9, the 1st gear ring 10 of wheel, the 2nd gear ring 11 and planet carrier 13 this 4 components are changed into the lock-out state that can not be rotated against, with the 2nd The pinion shaft 7 that gear ring 11 links is rotated with input shaft 2 with same speed.

When making the rotating speed of rotating ratio input shaft 2 of driving source 14 slow, the rotating speed of central gear 9 is set to Ns, the 1st gear ring 10 rotating speed is set to Nr1, the gearratio (number of teeth of the number of teeth/central gear 9 of the 1st gear ring 10) of the gear ring 10 of central gear 9 and the 1st J is set to, then the rotating speed of planet carrier 13 is (jNr1+Ns)/(j+1).Also, when the biography of the setting gear ring 11 of central gear 9 and the 2nd Move than ((number of teeth of the number of teeth/central gear 9 of the 2nd gear ring 11) × (the large-diameter portion 12a of staged little gear 12 number of teeth/path The portion 12b number of teeth)) when being k, then the rotating speed of the 2nd gear ring 11 is { j (k+1) Nr1+ (k-j) Ns }/{ k (j+1) }.

In the case of the rotating speed identical of the rotating speed of input shaft 2 of fixed disk 5 and pinion shaft 7 is fixed with, wobble-plate 6 with Fixed disk 5 together integratedly rotates.In the case where the rotating speed of input shaft 2 and the rotating speed of pinion shaft 7 have differences, wobble-plate 6 are rotated centered on the center point P 2 of fixed disk 5 on the periphery of fixed disk 5.

As shown in figure 3, wobble-plate 6 is eccentric relative to fixed disk 5 in a manner of distance Rx is equal with distance Ry, therefore can also Enough make wobble-plate 6 center point P 3 be located at on input center axis P1 identical axis so that input center axis P1 with The distance of center point P 3 is that offset R1 is " 0 ".

On one end the big footpath annulus 15a with major diameter, on another end with than big footpath annulus The big footpath annulus 15a of small path annulus (the 1st ring portion) 15b of 15a diameter connecting rod 15 is by roller bearing 16 with energy The periphery of wobble-plate 6 is embedded in outside the mode enough rotated freely.On output shaft 3, across the list that mechanism is prevented as single direction rotation To clutch 17,6 swing rods 18 are accordingly provided with connecting rod 15.One-way clutch 17 be configured to possess multiple rolling element 17a with And the helical spring 17b that rolling element 17a exerts a force to circumferencial direction, these rolling elements 17a and helical spring 17b are configured in wedge shape Space S in, exterior part that the wedge-shaped space S forms in one-way clutch 17 is the inner peripheral surface of swing rod 18 with forming output shaft Between the outer peripheral face of the inner part of 3 one-way clutch 17.

Swing rod 18 is formed as ring-type, is provided with the swing end (the linked with the path annulus 15b of connecting rod 15 thereunder 2 ring portions) 18a.A pair of the tabs protruded in a manner of sandwiching path annulus 15b in the axial direction are provided with end 18a is swung 18b.Through hole 18c corresponding with path annulus 15b internal diameter is provided through on a pair of tab 18b.In through hole 18c With in path annulus 15b inserted with link pin 19.Thus, connecting rod 15 links with swing rod 18.

Fig. 4 show to make the offset R1 of eccentric stiffener 4 change in the state of the position of pinion shaft 7 and wobble-plate 6 close System.Fig. 4 (a) shows the state for making offset R1 be " maximum ", and pinion shaft 7 and wobble-plate 6, which are located at, makes input center axis P1, the center point P 2 of fixed disk 5 and wobble-plate 6 center point P 3 arrange position in alignment.Gear ratio i now into For minimum.

Fig. 4 (b) show to make offset R1 be it is smaller than Fig. 4 (a) " in " state, Fig. 4 (c) shows to make offset R1 is the state of " small " smaller than Fig. 4 (b).In Fig. 4 (b), the gear ratio i that gear ratio i is changed into (a) than Fig. 4 is big " in ", in Fig. 4 (c), gear ratio i is changed into " big " of the gear ratio i of (b) than Fig. 4 greatly.Fig. 4 (d) shows to make bias The state that R1 is " 0 " is measured, input center axis P1 and wobble-plate 6 center point P 3 are located at concentric position.Gear ratio i now Become infinitely great (∞).

As shown in figure 3, the eccentric stiffener 4 of present embodiment, connecting rod 15, swing rod 18 form four section linkages 20.This reality The buncher 1 for applying mode possesses 6 four section linkages 20 altogether.When offset R1 is not " 0 ", if making input shaft 2 Rotation, and make pinion shaft 7 to be rotated with the same speed of input shaft 2, then each connecting rod 15 is each on one side changes 60 degree of phases, While alternately pushed or to the side of input shaft 2 to the side of output shaft 3 between input shaft 2 and output shaft 3 repeatedly based on offset R1 Pull and swung.

The path annulus 15b of connecting rod 15 links with the swing rod 18 being located at by one-way clutch 17 on output shaft 3, because This, if swing rod 18 is swung by the push-and-pull of connecting rod 15, only when swing rod 18 is any one into press direction side or direction of draw side When side rotates, output shaft 3 rotates, and when swing rod 18 rotates to opposite side, the power of the oscillating motion of swing rod 18 will not be transferred to defeated Shaft 3, swing rod 18 dally.Illustrated with reference to present embodiment, one-way clutch 17 is only when swing rod 18 is along counterclockwise in Fig. 3 Turn into torque transmission status when direction rotates, when swing rod 18 is along turning into moment of torsion off-state when being rotated clockwise in Fig. 3. In addition, as shown in figs.10 and 14, in the case where swing rod 18 is along the counterclockwise rotates in Fig. 3 also not all the time in torsion Square transmission state, during swing rod 18 rotates in the counterclockwise direction, in 1 time beginning moment of torsion transmission of defined angle of oscillation α, Defined 2 times disconnection moments of torsion of angle of oscillation α.In addition, in Figure 10 and Figure 14, angle of oscillation α 1, α 2 are identical, but moment T1, T2 are different. Because each eccentric stiffener 4 is configured to change phase every 60 degree, therefore, output shaft 3 revolves successively by each eccentric stiffener 4 Turn.

Fig. 5 (a) is shown a case that under (a) that offset R1 is Fig. 4 " maximum " (gear ratio i is minimum) The swing rod 18 corresponding with the rotary motion of eccentric stiffener 4 hunting range θ 2, Fig. 5 (b) show that offset R1 is Fig. 4 (b) " in " situation (gear ratio i is medium situation) under the swing rod 18 corresponding with the rotary motion of eccentric stiffener 4 Hunting range θ 2, Fig. 5 (c) shows a case that " small " (the gear ratio i for big) of (c) that offset R1 is Fig. 4 Under the swing rod 18 corresponding with the rotary motion of eccentric stiffener 4 hunting range θ 2.As shown in Figure 5, as offset R1 becomes Small, the hunting range θ 2 of swing rod 18 narrows.In addition, when offset R1 is " 0 ", swing rod 18 is no longer swung.In addition, in this implementation In mode, in the swing end 18a of swing rod 18 hunting range θ 2, inner dead point will be set to closest to the position of input shaft 2 IDP, farthest away from the position of input shaft 2 it is set to outer dead point ODP.

Fig. 6 is vertical using the anglec of rotation θ of the eccentric stiffener 4 of buncher 1 as transverse axis, with the angular velocity omega 2 of swing rod 18 Axle, the relation of the change for the angular velocity omega 2 that the change with the offset R1 of eccentric stiffener 4 is accompanied is shown.Clearly may be used by Fig. 6 Know, offset R1 bigger (gear ratio i is smaller), the angular velocity omega 2 of swing rod 18 is bigger.

During 6 eccentric stiffeners 4 rotation that Fig. 7 shows to make phase differ 60 degree respectively (make input shaft 2 and pinion shaft 7 with During the rotation of same speed) each swing rod 18 relative with the anglec of rotation θ of eccentric stiffener 4 angular velocity omega 2.As shown in Figure 7, lead to 6 four section linkages 20 are crossed so that output shaft 3 successfully rotates.

Fig. 1 and Fig. 2 is returned to, fueller 30 possesses oil pump 31 and oil pipe 32.For example, the pump of the oil pump 31 in trochoid type Belt wheel 34 is fixed with axle 33, the belt wheel 34 is by between the belt wheel 34 and the belt wheel 35 being fixed on input shaft 2 Band 36 is driven.The effective diameter of belt wheel 34,35 is formed objects, and pump shaft 33 is sent with being rotated with the same speed of input shaft 2 Go out lubricating oil.

Fig. 8 and Fig. 9 are referred again to, oil pipe 32 embeds by the outboard tube 41 of hollow shape and in a manner of it can rotate against Inside tube 42 in outboard tube 41 is formed.In outboard tube 41 highlightedly be provided with respectively with 6 connecting rods, 15 corresponding 6 fuel feeding Arm 43.Fuel feeding arm 43 is the pipe internally with oil circuit 44 and front end closing, configures the swing end 18a in adjacent swing rod 18 Between (reference picture 2).Tap 45 is formed about in the front end of fuel feeding arm 43, path of the tap 45 to connection connecting rod 15 Annulus 15b (the 1st ring portion) and swing end (the 2nd ring portion) 18a of swing rod 18 link pin 19 discharge the profit from oil circuit 44 Lubricating oil.The particular location of explained later tap 45.

Inside tube 42 is integrally formed with pump shaft 33.Thus, inside tube 42 is in the inner side of outboard tube 41, to be changed with pump shaft 33 Speech rotates with the same speed of input shaft 2.Inside tube 42 is the pipe of the hollow shape for the axial oil circuit 46 that there is front end to close. Oil circuit 46 is connected to the outlet (not shown) of oil pump 31.Radially being provided with inside tube 42 makes oil circuit 46 and inside tube 42 6 connected outlets 47 (47A~47F) of outer peripheral face.6 outlet 47A~47F be formed as respectively with 6 fuel feeding arms 43 The correspondence of oil circuit 44.

As shown in figure 8,6 outlet 47A~47F are formed with the phase for differing 60 ° respectively, so that they are respectively corresponding Swing rod 18 swing end 18a as aftermentioned moment of torsion missing point TRP phase under connected with the oil circuit 44 of fuel feeding arm 43.Cause This, is when being transfused to the inside tube 42 of the driving of axle 2 in the rotation of the inner side of outboard tube 41, in a period of input shaft 2 rotates a circle, Inside tube 42 also rotates a circle, the oil circuit of outlet 47A~47F and corresponding fuel feeding arm 43 during rotating a circle 44 connections are once.Thus, the lubricating oil supplied from oil pump 31 to differ the tap 45 of 60 ° of phase from each fuel feeding arm 43 respectively Discharge.In addition, outlet 47A~47F shown in Fig. 8 shows each injection (ス ロ ー) interval with 60 ° is set to by the 1st Phase in the case of the sequential working of injection, the 6th injection, the 2nd injection, the 4th injection, the 3rd injection and the 5th injection.

As shown in figure 9, the tap 45 of fuel feeding arm 43 is configured in the swing end 18a of the swing rod 18 of swing moving rail On mark (circular arc centered on the axis P5 of output shaft 3) X.Specifically, the tap 45 of present embodiment is configured in bias Amount R1 be maximum and one-way clutch 17 from torque transmission status begin breaking moment of torsion when phase under swing rod 18 swinging end Portion 18a position.More specifically, as shown in Figure 10, when offset R1 is maximum, exist in the swing end 18a of swing rod 18 One-way clutch 17 from torque transmission status begin breaking moment of torsion at the time of the positions that are located at of T2, tap 45 is towards link pin 19 side opening.In addition, in the following description, when offset R1 for it is maximum when, the swing end 18a of swing rod 18 unidirectionally from Clutch 17 from torque transmission status begin breaking moment of torsion at the time of the positions that are located at of T2 be referred to as moment of torsion missing point TRP.

As shown in figure 11, link pin 19 is fixed on the path of connecting rod 15 using alignment pin 21 in a manner of it can not rotate against Annulus 15b.In addition, link pin 19 is provided with：The poroid oil circuit 19a of pocket, it is the side opening of tap 45, another in fuel feeding arm The axis hole of side closing；And lubrication hole 19b, it connects and radially extended with oil circuit 19a.Lubrication hole 19b is formed as and put The swing end 18a of bar 18 is corresponding.As shown in figure 12, from end on observation, lubrication hole 19b is relative to the axle for linking output shaft 3 Line P5 and the straight line L at the center of link pin 19 are arranged on the side of connecting rod 15.In other words, lubrication hole 19b is located at the hair of link pin 19 The side of raw moment of torsion missing described later.

In the case where link pin 19 is fixed on the path annulus 15b of connecting rod 15 (reference picture 11), in moment of torsion missing point Near TRP, swing end 18a and so-called moment of torsion missing occurs.That is, in moment of torsion missing point TRP, end 18a is swung because of inertia force And rotate against in the counterclockwise direction equivalent to end 18a and the amount in the chimeric gap of link pin 19 is swung, so that and link pin 19 collisions, produce strike note.In addition, when offset R1 is maximum, swinging end 18a translational speed turns into maximal rate, Therefore collided with speed quickly and link pin 19.

Next, reference picture 13 is carried out to supply of the lubricating oil to the fitting portion between link pin 19 and swing end 18a Explanation.As shown in figure 13, in the state of offset R1 is set as into maximum, if making input shaft 2 using driving sources such as engines Rotation, then because the effect of four section linkages 20, swing rod 18 are swung.In addition, the pump shaft 33 being connected by band 36 with input shaft 2 revolves Turn, oil circuit 46 from oil pump 31 to oil pipe 32 send out lubricating oil, also, the inside tube 42 of oil pipe 32 the inner side of outboard tube 41 with The same speed of input shaft 2 rotates.

Swing rod 18 is swung with the rotation of input shaft 2, but the phase (figure beyond the moment of torsion missing point TRP of swing rod 18 13 (a)~Figure 13 (d), Figure 13 (f)), the outlet 47 of inside tube 42 and the oil circuit 44 of fuel feeding arm 43 are inconsistent, lubrication Oil does not supply to fuel feeding arm 43.Also, when swing rod 18 is in phase (Figure 13 (e)) for moment of torsion missing point TRP, inside tube 42 outlet 47 connects with the oil circuit 44 of fuel feeding arm 43, so as to by lubricating oil from the tap 45 of fuel feeding arm 43 to positioned at moment of torsion The oil circuit 19a discharges of missing point TRP link pin 19.

The lubricating oil supplied to oil circuit 19a is supplied to the swing end of link pin 19 and swing rod 18 by lubrication hole 19b The side face of the side that moment of torsion missing occurs of fitting portion between 18a, the i.e. side opposite with the side face of moment of torsion transmission side, so as to Suppress impact sound caused by the collision between link pin 19.6 swing rods 18 reach moment of torsion missing point successively with 60 ° of interval TRP, but moment of torsion missing point TRP phase is reached in swing rod 18, lubricating oil is respectively from the quilt of tap 45 of corresponding fuel feeding arm 43 Supply to the oil circuit 19a of link pin 19, so as to be supplied to the side that moment of torsion missing occurs for swinging end 18a.

One in 6 fuel feeding arms 43 is observed, only when swing rod 18 reaches moment of torsion missing point TRP phase, inside tube 42 Outlet 47 connected with the oil circuit 44 of fuel feeding arm 43, be then changed into dissengaged positions in phase in addition, do not supply lubricating oil. Also compared with the existing apparatus that lubricating oil is continuously supplied when therefore, with that need not lubricate, 6 can be realized with the oil mass of 1 injection The oil mass of secondary injection, so as to which the required oil mass and frictional force of link pin 19 are controlled 1/6.

As described above, according to the power transmission TA of present embodiment, from the tap 45 of oil pipe 32 to logical Cross path annulus (the 1st ring portion) 15b for the connecting rod 15 that link pin 19 is pivotally supported and swing end (the 2nd ring of swing rod 18 Portion) fitting portion supply lubricating oil between 18a.Oil pipe 32 is by outboard tube 41 and with oil circuit 46 and can be relative with outboard tube 41 The inside tube 42 of rotation is formed, and by the rotation of inside tube 42, oil circuit 46 turns into tap 45 and connected only in defined phase Logical state.Thus, only lubricating oil must be being supplied at the time of lubricating oil, therefore lubricating oil will not flow out in vain, so as to lubricate effect Rate improves.

In addition, the defined phase of supply lubricating oil is to begin breaking moment of torsion from the torque transmission status of one-way clutch 17 When phase, therefore can reduce moment of torsion missing when link pin 19 with swing end 18a collision caused by strike note, so as to Power transmission TA can undisturbedly be operated.

In addition, tap 45 be configured to that offset R1 towards one-way clutch 17 is maximum and one-way clutch 17 from Torque transmission status begins breaking the link pin 19 during moment of torsion, thus can will lubrication load suppress it is relatively low in the state of, More effectively reduce strike note during moment of torsion missing.

In addition, link pin 19 diametrically has the profit for supplying lubricating oil with the fitting portion swung between the 18a of end to it Slide opening 19b, lubrication hole 19b are arranged on generation relative to the axis and the straight line L at the center of link pin 19 for linking output shaft 3 The side of moment of torsion missing, the position supply lubricating oil of strike note is produced during therefore, it is possible to be lacked to moment of torsion, so as to more effective Ground suppresses sound and produced, and improves commodity value.

<2nd embodiment>

Next, 14~Figure 17 of reference picture, is illustrated to the power transmission of the 2nd embodiment.In addition, this implementation Phases and fuel feeding position of the power transmission TA of mode only to the fitting portion fuel feeding between link pin 19 and swing end 18a Difference, it is identical with the 1st embodiment in addition to this, therefore identical label or equivalent label are put on simultaneously to identical or equal parts Simplify or omit the description.

As shown in Figure 14 and Figure 15, the tap 45 of 6 fuel feeding arms 43 of present embodiment is configured in so that output shaft 3 Output torque turn into that maximum mode sets offset R1 and one-way clutch 17 transmits since moment of torsion off-state The swing end 18a of swing rod 18 under phase during moment of torsion position.More specifically, as shown in figure 14, it is defeated when output shaft 3 When going out the offset R1 that moment of torsion is maximum, opened in the swing end 18a of swing rod 18 in one-way clutch 17 from moment of torsion off-state The position that T1 is located at the time of beginning to transmit moment of torsion, side opening of the tap 45 towards link pin 19.In addition, in following explanation In, when output shaft 3 output torque for maximum offset R1 when, the swing end 18a of swing rod 18 one-way clutch 17 from The position that T1 is located at the time of moment of torsion off-state starts to transmit moment of torsion is referred to as moment of torsion and transmits starting point TTP.Moment of torsion transmission Starting point TTP is that swing rod 18 is fixed on output shaft 3 using the effect of one-way clutch 17 and reaction force starts to connecting rod The phase of 15 effects.

In addition, as shown in Figure 16 and Figure 17, from end on observation, lubrication hole 19b relative to link the axis P5 of output shaft 3 with The straight line L at the center of link pin 19, is located at the side opposite with connecting rod 15.In other words, lubrication hole 19b is located at moment of torsion and transmits side Side face.

When moment of torsion transmission starts, high capacity is loaded on the fitting portion between link pin 19 and swing end 18a, but Because lubricating oil supplies from the lubrication hole 19b for the high capacity side for being located at link pin 19 to fitting portion, therefore act smooth and resistance to Long property also improves.

It is as discussed above, according to the power transmission TA of present embodiment, supply the defined of lubricating oil Phase is phase when one-way clutch 17 transmits moment of torsion since moment of torsion off-state, therefore can be suppressed by lubrication load It is relatively low in the state of, reduce moment of torsion transmit when strike note, so as to undisturbedly operate power transmission TA.

In addition, tap 45 is configured to disconnect shape towards under following offset R1, one-way clutch 17 from moment of torsion The link pin 19 under phase when state starts to transmit moment of torsion, wherein offset R1 is the output torque of output shaft 3 to be maximum Offset, thus can will lubrication load suppress it is relatively low in the state of, more effectively reduce moment of torsion transmit when strike note. Furthermore it is possible to abrasion when suppressing high capacity, so as to improve durability.

In addition, link pin 19 diametrically has the profit for supplying lubricating oil with the fitting portion swung between the 18a of end to it Slide opening 19b, lubrication hole 19b are arranged on progress relative to the center for linking output shaft 3 and the straight line L at the center of link pin 19 The side of moment of torsion transmission, the position supply lubricating oil of strike note is produced during therefore, it is possible to be transmitted to moment of torsion, so as to more effective Ground suppresses sound and produces and improve durability.

Also, the present invention is not limited to foregoing each embodiment, can suitably be deformed, improved.For example, In the above-described embodiment, link pin 19 is integrally fixed on the path annulus 15b of connecting rod 15, but can also be fixed on swing rod 18 swing end 18a.In this case, lubrication hole 19b is located at position corresponding with the path annulus 15b of connecting rod 15.

In addition, the inner part of one-way clutch 17 can be integral with output shaft 3, can also be with the split of output shaft 3.

Claims (7)

1. a kind of power transmission, wherein, by the rotation speed change for the input shaft being connected with driving source and it is transferred to output shaft Power transfer unit possesses：

Input side fulcrum, it is variable from the offset of the eccentric axis of the input shaft, and the input side fulcrum is defeated with this Enter axle to rotate together with；

One-way clutch, it is connected to the output shaft；

Outlet side fulcrum, it is on the exterior part of the one-way clutch；

Connecting rod, its both ends is connected to the input side fulcrum and the outlet side fulcrum, and moves back and forth；And

Shifting actuator, it changes the offset of the input side fulcrum,

One end of the connecting rod possesses the 1st ring portion of ring-type,

The outlet side fulcrum possesses the 2nd ring portion of ring-type,

1st ring portion and the 2nd ring portion are pivotally supported by link pin,

Characterized in that,

The power transmission possesses the oil pump of supply lubricating oil and the lubrication supplied by the oil pump is imported to lubrication portion The oil pipe of oil,

The oil pipe possesses：The outboard tube of hollow shape, it has the tap that the lubricating oil is discharged to the lubrication portion, and It is configured to rotate；And the inside tube of hollow shape, it is configured in a manner of it can be rotated against with the outboard tube In the inside of the outboard tube, and there is the oil circuit passed through for the lubricating oil,

The inside tube is rotated with the rotation same speed with the driving source,

Outlet is provided with the inside tube so that form the oil circuit and institute in a period of the inside tube rotates a circle The connected state and the oil circuit and the disconnected dissengaged positions of the tap of tap connection are stated,

The lubrication portion is the link pin,

Turn into the connected state when the power transfer unit is located at defined phase.

2. power transmission according to claim 1, wherein,

The one-way clutch possesses：

Multiple rolling elements, they are configured in wedge shape space, and the wedge shape space forms the inner peripheral surface and inside in the exterior part Between the outer peripheral face of part；And

Force application part, it exerts a force to the multiple rolling element to circumferencial direction,

When the exterior part rotates to circumferential side, moment of torsion is transmitted on defined opportunity, when the exterior part is another to circumference When side rotates, moment of torsion is not transmitted,

Phase as defined in described be the one-way clutch from torque transmission status begin breaking moment of torsion when phase.

3. power transmission according to claim 2, wherein,

The tap be configured to towards the offset be maximum when it is described as defined in the link pin under phase.

4. the power transmission according to Claims 2 or 3, wherein,

The link pin is fixed on any one party in the 1st ring portion and the 2nd ring portion in a manner of not revolvable,

The tap is located at an axially side for the link pin,

An axially end-side openings for the link pin, and axially another side closing,

Surrounding wall portion in the link side of axial direction one of the link pin and the axial another side, which is provided with, to be radially extended Lubrication hole,

From end on observation, the lubrication hole is set relative to the straight line of the axis and the outlet side fulcrum that link the output shaft Put in the circumferential opposite side.

5. power transmission according to claim 1, wherein,

The one-way clutch possesses：

Multiple rolling elements, they are configured in wedge shape space, and the wedge shape space forms the inner peripheral surface and inside in the exterior part Between the outer peripheral face of part；And

Force application part, it exerts a force to the multiple rolling element to circumferencial direction,

When the exterior part rotates to circumferential side, moment of torsion is transmitted on defined opportunity, when the exterior part is another to circumference When side rotates, moment of torsion is not transmitted,

Phase as defined in described is the phase when one-way clutch transmits moment of torsion since moment of torsion off-state.

6. power transmission according to claim 5, wherein,

The tap is configured to towards the link pin under defined phase during the following offset, its In the offset be that the output torque of the output shaft is maximum offset.

7. the power transmission according to claim 5 or 6, wherein,

The link pin is fixed on any one party in the 1st ring portion and the 2nd ring portion in a manner of not revolvable,

The tap is located at an axially side for the link pin,

An axially end-side openings for the link pin, and axially another side closing,

Surrounding wall portion in the link side of axial direction one of the link pin and the axial another side, which is provided with, to be radially extended Lubrication hole,

From end on observation, the lubrication hole is set relative to the straight line of the axis and the outlet side fulcrum that link the output shaft Put in the circumferential side.