CN106164540A - Power transmission - Google Patents

Abstract

The auxiliary power transfer part (80) of power transmission (1) possesses auxiliary one-way clutch (82) and disconnecting clutch (83).Disconnecting clutch (83) is set to connection status under the 1st state that the 1st gear ratio (MR) of active force transfer part (79) is bigger than the 2nd gear ratio (AR) of auxiliary power transfer part (80), is set to dissengaged positions under the 2nd state that the 1st gear ratio (MR) is less than the 2nd gear ratio (AR).When the difference assisting the rotary speed of the both sides of one-way clutch (82) under the 1st state converges on 0, disconnecting clutch (83) is temporarily set to dissengaged positions.

Description

Power transmission

Technical field

The present invention relates to the power transmission of a kind of four joint linkage types, it possesses: by driving of traveling driving source Power is transferred to the active force transfer part of differential gear；Move with by the auxiliary that power is transferred to traveling driving source from differential gear Power transfer part.

Background technology

Power transmission as follows known in Yi Wang, it possesses: passed by the driving force in the traveling driving source of vehicle It is handed to the active force transfer part of the differential gear of vehicle；Move with by the auxiliary that power is transferred to traveling driving source from differential gear Power transfer part (referring for example to No. 5019080 publication of Japanese Patent).

In the power transmission of No. 5019080 publication of Japan's patent, active force transfer part possesses: be transfused to row Sail the input unit with the driving force in driving source；Configure abreast with the center of rotation axis of input unit and be connected with differential gear Output shaft；And the rotary motion of input unit is converted to the crank rocker machine that axle props up the oscillating motion of fork in output shaft Structure.The oscillating motion of fork is passed to output shaft via one-way clutch as rotary motion.

When fork is intended to relatively rotate relative to the axial side of output, fork is fixed on output shaft by one-way clutch, When fork is intended to relatively rotate relative to the axial opposite side of output, one-way clutch makes fork dally relative to output shaft.Main The gear ratio of power transfering part is controlled by utilizing radius of turn adjustment structure to adjust the radius of turn of crank and rocker mechanism.

Auxiliary power transfer part be use can disconnect or connect the drive shaft in traveling driving source and differential gear from The synchromesh mechanism of the power transmission between moving gear is constituted.This synchromesh mechanism possesses: the 1st gear, and it is all the time Engage with driven gear, and the drive shaft being provided around traveling driving source is rotatable；2nd gear, it is arranged to detour Sail the drive shaft with driving source to rotate integratedly with this drive shaft；And sleeve, it makes the 1st gear and the 2nd gear combine or solve Remove.

In the case of there is deceleration request, traveling driving source is stopped, and synchromesh mechanism is set to connect shape State.Thus, the brake force in traveling driving source acts on the driving wheel of vehicle as engine braking.Now, be plugged in from The output shaft of active force transfer part is dissengaged positions to the clutch in the driving force bang path of differential gear.

Prior art literature

Patent documentation

Patent documentation 1: No. 5019080 publications of Japanese Patent Publication No.

Summary of the invention

Invent problem to be solved

But, undisclosed in No. 5019080 publication of above-mentioned Japanese Patent: how according to the master in power transmission Relation between gear ratio and the gear ratio of auxiliary power transfer part of power transfering part, makes the synchronization in auxiliary power transfer part Engaging mechanism, clutch operating.

The present invention provides a kind of power transmission in view of the above, and power transmission considers active force transfer part The relation of gear ratio of gear ratio and auxiliary power transfer part, and suitably control the biography of the power in auxiliary power transfer part Pass or it cuts off, it is possible to effectively utilize the brake force transmitted based on this power.

For solving the means of problem

[1] power transmission of the present invention is characterised by, it possesses: active force transfer part, and it is regulating The driving force in the traveling driving source of vehicle is transferred to the differential gear of this vehicle by the 1st gear ratio；And auxiliary power transmission Portion, power is transferred to described traveling driving source, described active force biography from described differential gear with the 2nd gear ratio of regulation by it The portion of passing possesses: input unit, and it is transfused to the driving force in described traveling driving source；Output shaft, it is configured to and described input The center of rotation axis in portion is parallel, is connected with described differential gear；Crank and rocker mechanism, it has by output shaft described in axle Zhi Yu Fork, the rotary motion of described input unit is converted to the oscillating motion of described fork；Radius of turn governor motion, it is used for Including that controlling the described 1st in the range of described 2nd gear ratio becomes by adjusting the radius of turn of described crank and rocker mechanism Speed ratio；And the 1st one-way clutch, when described fork is intended to relatively rotate relative to the axial side of described output, the described 1st This fork is fixed on this output shaft by one-way clutch, when this fork is intended to relatively rotate relative to the axial opposite side of this output Time, described 1st one-way clutch makes this fork dally relative to this output shaft, and described auxiliary power transfer part possesses: disconnecting from Clutch, it is for switching to connection status and dissengaged positions by the power transfer path of this auxiliary power transfer part；And control Portion, it controls described disconnecting clutch, and described control portion is under the 1st state that described 1st gear ratio is bigger than described 2nd gear ratio Described disconnecting clutch is set as connection status, will under the 2nd state that described 1st gear ratio is less than described 2nd gear ratio Described disconnecting clutch is set as dissengaged positions.

In the present invention, when vehicle travels, it is poor that the driving force in traveling driving source is passed to by active force transfer part Speed gear, thus drive vehicle.Herein, active force transfer part transmits driving force through the 1st one-way clutch, the most not from differential tooth Take turns and transmit power to traveling driving source.

Therefore, when vehicle deceleration or when stopping, it is impossible to obtain from differential gear, power is transferred to traveling driving source And the effect of the so-called engine braking of abrupt deceleration vehicle, it is transferred to travel with driving by power hence with auxiliary power transfer part Dynamic source and obtain this effect.

In this case, the 1st gear ratio of active force transfer part bigger than the 2nd gear ratio of auxiliary power transfer part the 1st Under state, disconnecting clutch is set to connection status.Therefore, disconnecting clutch is set as connection status, it is possible to carry out by Active force transfer part realize for vehicle traction power transmit and by auxiliary power transfer part realize for car braking Power transmission.

Therefore, in the 2nd state that the 1st gear ratio of active force transfer part is less than the 2nd gear ratio of auxiliary power transfer part Under, it is assumed that disconnecting clutch is configured to connection status, then, when driving force is passed to differential gear from traveling driving source, produce The problem of raw interlocking.

Therefore, in order to avoid this interlocking, under the 2nd above-mentioned state, disconnecting clutch is set to dissengaged positions.

[2] in the present invention, the gear ratio along with described active force transfer part change and from described 2nd status transition During to described 1 state, described control portion is controlled so that described disconnecting clutch is gradually transferred to from dissengaged positions connect State, when the rotary speed of the described both sides of described 2nd one-way clutch is consistent or becomes being fully connected state the most later.

As it has been described above, the 1st shape that the 1st gear ratio of active force transfer part is bigger than the 2nd gear ratio of auxiliary power transfer part Under state, disconnecting clutch is set to connection status, under the 2nd state that the 1st gear ratio is less than the 2nd gear ratio, and disconnecting clutch It is set to dissengaged positions.But, if vehicle deceleration when from the 2nd status transition to 1 state time immediately by disconnecting from Clutch switches to connection status, then because of the rotary speed between active force transfer part side and the differential gear side of disconnecting clutch it Differ from and produce big impact.Therefore, as it has been described above, gradually carry out from dissengaged positions to the transfer of connection status.Thus, gradually open Begin to utilize auxiliary power transfer part to carry out power transmission from differential gear to traveling driving source, improve the traveling rotation in driving source Rotary speed, the rotary speed of the both sides of disconnecting clutch is the most consistent.Therefore, it is possible to not impact and promptly carry out disconnecting from Clutch is to the transfer of connection status.

[3] in the present invention, described vehicle because of power under described 1st state through described auxiliary power transfer part quilt When being transferred to described traveling driving source and slow down, described control portion along with the speed of described vehicle become regulation value below and Make described traveling driving source stop, and described disconnecting clutch is set as dissengaged positions.

Thereby, it is possible to stop following situation: after below the value that the speed of vehicle reaches regulation, again speed up or again Power during starting passes through auxiliary power transfer part to be carried out.It is prevented from active force transfer part and auxiliary power transfer part Conflict.

[4,5] and, the preferably auxiliary power transfer part of the present invention possesses the 2nd one-way clutch, when described travel with driving Dynamic source is time rotary speed is big compared with described differential gear side, and described 2nd one-way clutch idle running, when the driving of described travelings Source from described differential gear side joint by power time, described 2nd one-way clutch engagement.

According to this structure, the traveling at the 2nd one-way clutch drives source and differential gear side all to making vehicle advance Direction rotate in the case of, when the rotary speed of differential gear side exceedes the rotary speed that traveling drives source, the 2nd is single Automatically the state that can transmit power is switched to from idling conditions such that it is able to make engine braking come into force to clutch.

[6] it is a feature of the present invention that it possesses: active force transfer part, it can with the 1st gear ratio that can regulate The driving force in the traveling driving source being equipped in vehicle is transferred to the differential gear of this vehicle；And auxiliary power transfer part, Power is transferred to described traveling driving source from described differential gear with the 2nd gear ratio of regulation by it, and described active force is transmitted Portion possesses: input unit, and it is transfused to the driving force in described traveling driving source；Output shaft, it is configured to and described input unit Center of rotation axis parallel, to described differential gear export driving force；Crank and rocker mechanism, it has by defeated described in axle Zhi Yu The fork of shaft, is converted to the oscillating motion of described fork by the rotary motion of described input unit；Radius of turn governor motion, its For including controlling in the range of described 2nd gear ratio described the by adjusting the radius of turn of described crank and rocker mechanism 1 gear ratio；And the 1st one-way clutch, when described fork is intended to relatively rotate relative to the axial side of described output, described Described fork is fixed on described output shaft by the 1st one-way clutch, when described fork be intended to relative to described output axially another When side relatively rotates, described 1st one-way clutch makes described fork dally relative to described output shaft, and described auxiliary power passes The portion of passing possesses: disconnecting clutch, its for the power transfer path of described auxiliary power transfer part switched to connection status and Dissengaged positions；And control portion, it controls described disconnecting clutch, and the engaging condition of described disconnecting clutch includes: relative to Main engaging rotating speed, the actual driving source rotating speed as present driving source rotating speed is relatively low, and wherein, described main engaging rotating speed is by institute State the radius of turn of radius of turn governor motion and the power that can carry out described 1st one-way clutch that car speed determines passes The driving source rotating speed passed is i.e.；And according to described 2nd gear ratio drive driving source rotating speed i.e. assist engaging rotating speed relative to In the case of described main engaging rotating speed is relatively low, it is allowed to the joint of described disconnecting clutch.

According to the present invention, when the state that the reality driving source main engaging rotating speed of rotating ratio is low, at main engaging rotating speed than auxiliary In the case of engaging rotating speed height, it is allowed to disconnecting clutch engages.Thus, the present invention it can be avoided that may from active force transfer part and Both auxiliary power transfer part transmit the state (interlocking state) of power.

Further, according to the present invention, if not the state that the actual driving source main engaging rotating speed of rotating ratio is low, disconnecting is not the most allowed The joint of clutch.Therefore, when needs control driving source rotating speed based on the source of driving moment of torsion, actual driving source rotating speed is only controlled into Less than main engaging rotating speed, therefore need not adjust driving source moment of torsion accurately, it becomes possible to stably control driving source Rotating speed.

[7] and, in the present invention, about the radius of turn of described radius of turn governor motion, preferably from accelerate shape State, when deceleration regime transition, controls radius of turn so that described main engaging rotating speed is more auxiliary than drive according to described 2nd gear ratio Help engaging rotating speed high.

According to this structure, by radius of turn is controlled less, it is possible to make main engaging rotating speed connect to higher than auxiliary rapidly Close the rotating speed transfer of rotating speed such that it is able to gently carry out transmitting via the power of auxiliary power transfer part.

Accompanying drawing explanation

Fig. 1 is the skeleton diagram of the power transmission of the 1st embodiment illustrating the present invention.

Fig. 2 is the explanatory diagram of the main portions of the power transmission illustrating the 1st embodiment with part section.

Fig. 3 is the explanatory diagram of the crank and rocker mechanism illustrating the 1st embodiment.

Fig. 4 A to Fig. 4 D is the explanatory diagram of the change of the radius of turn illustrating the 1st embodiment.

Fig. 4 A illustrates that radius of turn is maximum state, Fig. 4 B be illustrate radius of turn be in state, Fig. 4 C is to illustrate Radius of turn is little state, and Fig. 4 D illustrates the state that radius of turn is 0.

Fig. 5 is saying of the change of the hunting range illustrating corresponding, the fork of change with the radius of turn of the 1st embodiment Bright figure.Fig. 5 A illustrates the hunting range that offset R1 is maximum state, Fig. 5 B illustrate radius of turn be in the swing of state Scope, Fig. 5 C illustrates the hunting range that radius of turn is little state.

Fig. 6 is that the 1st gear ratio MR of the active force transfer part of the power transmission illustrating the 1st embodiment is dynamic with auxiliary The curve chart of the relation between the 2nd gear ratio AR of power transfer part, transverse axis be vehicle velocity V [km/h], the longitudinal axis be traveling driving source Rotary speed Ne [rpm] of ENG.

Fig. 7 A～Fig. 7 D be illustrate in the 1st embodiment travel in vehicle deceleration, stop so start to walk and be transferred to row The sequential chart of the control method of friction clutch when sailing state, Fig. 7 A is the figure of the change illustrating vehicle velocity V, and Fig. 7 B is to illustrate master The figure of the change of the 1st gear ratio MR of power transfering part and the 2nd gear ratio AR of auxiliary power transfer part, Fig. 7 C is to illustrate driving Rotary speed Na of the outer shaft 84a of rotary speed Ns of axle 93 and composition auxiliary power transfer part and the rotary speed of outer shaft 84c The figure of the change of Nc, Fig. 7 D is to illustrate on the clutch plate being applied to be plugged in the friction clutch in auxiliary power transfer part The figure of change of crimping load M.

Fig. 8 A～Fig. 8 D be illustrate in the 1st embodiment travel in vehicle deceleration, stop so start to walk and be transferred to row Other sequential charts of the control method of friction clutch when sailing state, Fig. 8 A is the figure of the change illustrating vehicle velocity V, and Fig. 8 B is to show Going out the figure of the change of the 1st gear ratio MR of active force transfer part and the 2nd gear ratio AR of auxiliary power transfer part, Fig. 8 C is to illustrate Rotary speed Na of the outer shaft 84a of rotary speed Ns of drive shaft 93 and composition auxiliary power transfer part and the rotation of outer shaft 84c The figure of the change of speed Nc, Fig. 8 D is to illustrate the clutch being applied to be plugged in the friction clutch in auxiliary power transfer part The figure of the change of the crimping load M on plate.

Fig. 9 is the flow chart of the action in the control portion of the power transmission of the 2nd embodiment illustrating the present invention.

Figure 10 is sequential chart during the low speed of the power transmission illustrating the 2nd embodiment.

Figure 11 is sequential chart during the high speed of the power transmission illustrating the 2nd embodiment.

Detailed description of the invention

[the 1st embodiment]

Use the 1st embodiment of the power transmission of the four joint linkage types of the accompanying drawing explanation present invention below.1st The power transmission of embodiment has one can be by (the rotation of the rotary speed/output shaft of h=input unit of gear ratio h Speed) it is set to infinity (∞) and the rotary speed of output shaft is set to the buncher of " 0 ", the most so-called IVT (Infinity Variable Transmission: unlimited speed changing type buncher).

Seeing figures.1.and.2, the power transmission 1 of four joint linkage types possesses: as the power shaft end of input unit 2a, it is communicated to the driving force from traveling driving source ENG such as electromotor or motor such as internal combustion engines, thus with center of rotation Rotate centered by axis P1；Output shaft 3, it is configured to parallel with center of rotation axis P1, and via omitting the differential tooth of diagram Rotary power is transferred to the driving wheel (omitting diagram) of vehicle by wheel；And 6 radius of turn governor motions 4, they are arranged on On center of rotation axis P1.It addition, power transmission shaft can be inserted with between output shaft 3 and differential gear.

With reference to Fig. 2 and Fig. 3, each radius of turn governor motion 4 possesses the cam disc 5 as cam part and as rotating part Rotating disk 6.Cam disc 5 is discoid, and cam disc 5 is eccentric relative to center of rotation axis P1, and to rotate half relative to 1 Footpath governor motion 4 is that the mode of 21 group is arranged at each radius of turn governor motion 4.It addition, be provided with on cam disc 5 along rotation Turn the through hole 5a that the direction of central axis P1 is through.And, cam disc 5 is provided with cut hole 5b, this cut hole 5b to phase For the direction opening in opposite direction that center of rotation axis P1 is eccentric, and make the outer peripheral face of cam disc 5 and constitute through hole The inner peripheral surface connection of 5a.

Every 1 group of cam disc 5 makes phase 60 degree respectively, 6 groups of cam discs 5 be configured to the week around center of rotation axis P1 To a circle.

Cam disc 5 forms with the cam disc 5 of adjacent radius of turn governor motion 4, thus it is convex to be integrally formed type Wheel portion 5c.This one-piece type cam part 5c can be formed by one-body molded, or can also be that 2 cam part are welded on one Rise and realize integration.The cam disc 5 of 21 group of each radius of turn governor motion 4 is solid each other by bolt (omitting diagram) Fixed.It is located most closely to traveling on center of rotation axis P1 and drives the cam disc 5 of source position with input unit end 2a integratedly Formed.So, input unit end 2a and multiple cam disc 5 constitute the power shaft 2 (camshaft) possessing cam disc 5.

Power shaft 2 have run through insertion hole 60, this run through insertion hole 60 be by the through hole 5a of cam disc 5 be connected and structure Become.Thus, power shaft 2 be configured to the one end open of the side contrary with traveling driving source ENG and during the other end closes Empty shape shaft.The cam disc 5 of the other end being positioned at traveling driving source forms as one with power shaft end 2a.As making this The method that cam disc 5 forms with input unit end 2a, can use one-body molded, alternatively, it is also possible to by cam disc 5 He Input unit end 2a welds and realizes integration.

Additionally, there is the discoid rotating disk 6 of receiving hole 6a for accommodating cam disc 5 when eccentric with rotation Turn and be embedded in each group of cam disc 5 outside mode freely.

As it is shown on figure 3, the central point of cam disc 5 is set to P2, the central point of rotating disk 6 is set to P3, rotating disk 6 so that Distance Ra between center of rotation axis P1 and center point P 2 is equal to the mode of distance Rb between center point P 2 and center point P 3, Eccentric relative to cam disc 5.The internal tooth 6b between 1 group of cam disc 5 it is provided with in receiving hole 6a of rotating disk 6.

Be positioned at the little gear 70 of the position concentric and corresponding with the internal tooth 6b of rotating disk 6 with center of rotation axis P1 with tool The power shaft 2 having cam disc 5 rotate against mode freely be arranged in power shaft 2 run through insertion hole 60 in.Little gear 70 with Pinion shaft 72 forms as one.It addition, little gear 70 can also with pinion shaft 72 split constitute, and combined by spline Little gear 70 is made to connect with pinion shaft 72.In the present embodiment, it is defined as including little gear when being only only called little gear 70 Axle 72.

Little gear 70 engages with the internal tooth 6b of rotating disk 6 through cut hole 5b of cam disc 5.Pinion shaft 72 is provided with little Gear-bearing 74, this pinion bearing 74 is between adjacent little gear 70.Pinion shaft 72 is via this pinion bearing 74 Supporting power shaft 2.Pinion shaft 72 connects and has the differential attachment 8 being made up of planetary gears etc..Driving source is used in regulation The driving force of 14 is passed to little gear 70 via differential attachment 8.

Be fixed with the rotary speed of power shaft 2 of cam disc 5 identical with the rotary speed of pinion shaft 72 in the case of, Rotating disk 6 rotates the most integratedly with cam disc 5.In the feelings that the rotating speed of power shaft 2 and the rotating speed of pinion shaft 72 there are differences Under condition, rotating disk 6 centered by the center point P 2 of cam disc 5 cam disc 5 periphery rotate.

Rotating disk 6 is eccentric relative to cam disc 5, therefore, it is possible to make rotating disk 6 in the way of distance Ra is equal with distance Rb Center point P 3 be positioned on the axis identical with center of rotation axis P1, make between center of rotation axis P1 and center point P 3 away from It is " 0 " from i.e. offset R1.

Connecting rod 15 has the input side annulus 15a of major diameter on side (power shaft 2 side) end, (defeated at opposite side Shaft 3 side) there is the outlet side annulus 15b that the diameter than input side annulus 15a is little on end.The input side of this connecting rod 15 Annulus 15a is by by axially going up 2, side by side and the connecting-rod bearing 16 that the ball bearing of 2 group is constituted is with can be rotatable Mode outside be embedded in the periphery of rotating disk 6.On output shaft 3, via the main one-way clutch stoping mechanism as single direction rotation 17, it is provided with 6 forks 18 accordingly with connecting rod 15.

Main one-way clutch 17 is located between fork 18 and output shaft 3, when fork 18 is intended to relative to output shaft 3 to side phase To when rotating, fork 18 is fixed on (stationary state) on output shaft 3 by main one-way clutch 17, when fork 18 is intended to opposite side phase To when rotating, main one-way clutch 17 makes fork 18 dally (idling conditions) relative to output shaft 3.

Fork 18 is formed as ring-type, is thereunder provided with the swing end that the outlet side annulus 15b with connecting rod 15 connects 18a.Swinging on the 18a of end, to be provided with a pair prominent tab 18b in the way of axially clipping outlet side annulus 15b.? The insertion hole 18c corresponding with the internal diameter of outlet side annulus 15b it is provided through on a pair tab 18b.Inserting hole 18c and defeated Go out and on the annulus 15b of side, be inserted with the coupling pin 19 as swinging axle.Thus, connecting rod 15 connects with fork 18.

Fig. 4 A to Fig. 4 D illustrates the little tooth of the state making the offset R1 (radius of turn) of radius of turn governor motion 4 change Position relationship between wheel shaft 72 and rotating disk 6.Fig. 4 A represents the state making offset R1 be " maximum ", pinion shaft 72 chord Rotating disk 6 is positioned at and makes the center point P 3 of center of rotation axis P1, the center P2 of cam disc 5 and rotating disk 6 be arranged in straight line Position.Gear ratio h now becomes minimum.

Fig. 4 B represent make offset R1 become less than Fig. 4 A " in " state, Fig. 4 C represents makes offset R1 become than figure The state of " little " that 4B is less.In figure 4b, gear ratio h be gear ratio h than Fig. 4 A big " in ", in figure 4 c, gear ratio h For " greatly " that gear ratio h than Fig. 4 B is big.Fig. 3 D represents the state making offset R1 become " 0 ", center of rotation axis P1 and rotation The center point P 3 of rotating disk 6 is positioned at concentric position.Gear ratio h now becomes infinitely great (∞).The power of present embodiment passes Delivery device 1 utilizes radius of turn governor motion 4 to change offset R1, thereby, it is possible to freely regulate radius of turn governor motion 4 Radius of turn (orbital radius of the center delineation of the rotating disk 6 when rotating disk 6 revolves round the sun relative to center of rotation axis P1).

Fig. 5 illustrates the hunting range of the fork 18 in the case of the offset R1 change making radius of turn governor motion 4 Change.Fig. 5 A illustrates the hunting range that offset R1 is the fork 18 during maximum, and Fig. 5 B illustrates fork when offset R1 is middle The hunting range of 18, Fig. 5 C illustrates the hunting range of the fork 18 that offset R1 is hour.According to Fig. 5 A～Fig. 5 D, along with Offset R1 diminishes, and hunting range narrows.Further, when offset R1 is " 0 ", fork 18 no longer swings.

In the present embodiment, radius of turn governor motion 4, connecting rod 15 and fork 18 crank and rocker mechanism is constituted 20 (four joint linkages).And, by crank and rocker mechanism 20, the rotary motion of input unit 2 is converted to the swing of fork 18 Motion.Power transmission 1 total of present embodiment possesses 6 crank and rocker mechanisms 20.When offset R1 is not " 0 ", If making input unit 2 rotate, and making pinion shaft 72 rotate with the speed identical with power shaft 2, the most each connecting rod 15 is every time Change 60 degree of phase places, the most repeatedly push to output shaft 3 side between input unit 2 and output shaft 3 based on offset R1 Or go out to swing end 18a to input unit 2 layback, thus fork 18 swings.

The outlet side annulus 15b of connecting rod 15 and the fork 18 being located at output shaft 3 via one-way clutch 17 connect, because of This, if fork 18 is swung by connecting rod 15 push-and-pull, only the most any one to push in side, direction or draw direction side when fork 18 When side rotates, output shaft 3 rotates, and when fork 18 rotates to opposite side, the power of the oscillating motion of fork 18 will not be passed to Output shaft 3, fork 18 dallies.Owing to being configured to differ 60 degree of phase places respectively by each radius of turn governor motion 4, therefore, pass through Each radius of turn governor motion 4 makes output shaft 3 rotate successively.

It addition, as it is shown in figure 1, the power transmission 1 of present embodiment possesses the control in control and regulation driving source 14 Portion ECU.Control portion ECU is the electronic unit being made up of CPU, memorizer etc., utilizes CPU to perform storage control in memory Program, thus, control and regulation driving source 14, play the function of the offset R1 of regulation radius of turn governor motion 4.

Further, control portion ECU is configured to receive the accelerator open degree from the accelerator open degree test section 71 being located at vehicle Information, carry out the information of the speed in the Bus-Speed Monitoring portion 73 of the travel speed of Autonomous test vehicle, from brake operating test section 75 The information of operation of presence or absence brake pedal and the traveling information etc. of the rotary speed of driving source ENG.

It addition, be made up of radius of turn governor motion 4, connecting rod 15, fork 18, main one-way clutch 17 from power shaft 2 to Output shaft 3 transmits the active force transfer part 79 of power.

With reference to Fig. 1, the power transmission 1 of the 1st embodiment possesses auxiliary power transfer part 80.Auxiliary power transfer part 80 obtain as what is called by power is transferred to traveling driving source ENG from the differential gear 81 of vehicle when being for slowing down The power transfer path of brake force of engine braking.

As it is shown in figure 1, auxiliary power transfer part 80 possesses: the auxiliary one-way clutch being arranged in its power transfer path 82, as friction clutch 83, the control of the disconnecting clutch that this power transfer path is switched to connection status and dissengaged positions The control portion ECU of friction clutch 83 processed and auxiliary train of gears 86.

When the rotary speed of the parts of this ENG side, traveling driving source is bigger than the rotary speed of the parts of differential gear 81 side Time, auxiliary one-way clutch 82 dallies, when the parts of differential gear 81 side apply power to the traveling parts of ENG side, driving source Time, auxiliary one-way clutch 82 engages.Thus, power is only laterally travelled with driving by auxiliary one-way clutch 82 from differential gear 81 The direction transmission of dynamic source ENG.

Output shaft 3 is provided with the outer shaft 84 being positioned at it on same axis.Outer shaft 84 by arranged in series outer shaft 84a～ Outer shaft 84c is constituted.Auxiliary one-way clutch 82 is in the way of only can transmitting power to the direction of outer shaft 84b from outer shaft 84a It is arranged between outer shaft 84a and outer shaft 84b.

Therefore, in the case of the rotary speed of the outer shaft 84a rotary speed than outer shaft 84b is low, assist one-way clutch 82 Idle running, in the opposite case, auxiliary one-way clutch 82 engages, and the power of outer shaft 84a is transferred to outer shaft 84b.Rub from Clutch 83 is to allow hand over into the connection status coupled together with outer shaft 84c by outer shaft 84b and to cut off this dissengaged positions being connected Mode be arranged between outer shaft 84b and outer shaft 84c.

Transmitting driving force from traveling driving source ENG to the input unit 2 of active force transfer part 79 is via with amortisseur Clutch 85 carry out.Outer shaft 84c is via auxiliary train of gears 86 and the amortisseur 87 of the clutch 85 with amortisseur, with row Sail and connect by the drive shaft 88 of driving source ENG.

Auxiliary train of gears 86 is constituted by with lower member: auxiliary input side gear 86a, it is by from traveling driving source ENG warp Power is transmitted by amortisseur 87；Auxiliary idler gear 86b, itself and auxiliary input side gear 86a conjunction, and with rotatable side Formula axle props up in power transmission housing；And auxiliary outlet side gear 86c, itself and auxiliary idler gear 86b conjunction, and with outward Axle 84c rotates integratedly.

On the end of differential gear 81 side of output shaft 3, with output shaft 3 coaxially via output one-way clutch 89 It is provided with transmission axle 90.Output one-way clutch 89 is configured to, only in the rotation of direction of rotation when advancing to vehicle of output shaft 3 In the case of rotary speed is faster than the rotary speed of the direction of rotation when vehicle advances of transmission axle 90, from output shaft 3 to transmission Axle 90 transmits power.Outer shaft 84a there is transmission axle via planetary gears 91 transmission arranged with it on the same axis The power of 90.

Planetary gears 91 is made up of the planetary gears of single pinion type, the planetary gear machine of this list pinion type Structure possesses central gear, gear ring engages with central gear and gear ring little gear and planet carrier, this planet carrier is by little gear Axle Zhi Weineng is relative to central gear rotation freely and revolution.The central gear of planetary gears 91 is located on outer shaft 84a, Gear ring is located on transmission axle 90.

Auxiliary power transfer part 80 is configured to arrive via auxiliary one-way clutch 82, friction clutch 83 from transmission axle 90 The power transfer path of amortisseur 87.Transmission axle 90 via have employed the forward/backward switching mechanism 92 of planetary gears with Differential gear 81 connects.

The planetary gears of forward/backward switching mechanism 92 is made up of the planetary gears of single pinion type, and this is single Little gear that the planetary gears of pinion type is engaged with central gear and gear ring by central gear, gear ring and planet carrier Constitute, this planet carrier by pinion shaft Zhi Weineng relative to central gear rotation freely and revolution.Advance switching mechanism 92 Gear ring connects with differential gear 81.The planet carrier of advance switching mechanism 92 is via the brake being made up of jaw clutch freely It is fixed on power transmission housing.

And, forward/backward switching mechanism 92 possesses the jaw clutch of bang path switching.Forward/backward cut The jaw clutch of the bang path switching of converting mechanism 92 be configured to freely to switch to connection transmission axle 90 and advance/ Retreat the state of the central gear of switching mechanism 92, and the central gear of axle 90 and forward/backward switching mechanism 92 is transmitted in connection And any state in the state of gear ring.

In the case of making vehicle advance, the bang path of forward/backward switching mechanism 92 is switched by control portion ECU Jaw clutch is set to connection transmission axle 90 and the central gear of forward/backward switching mechanism 92 and the state of gear ring.Meanwhile, Make the brake release that the jaw clutch of the planet carrier by advance switching mechanism 92 is constituted, be set to disconnection advance switching machine The state of the connection between planet carrier and the power transmission housing of structure 92.

In the case of making vehicle rollback, the bang path of forward/backward switching mechanism 92 is switched by control portion ECU Jaw clutch is set to the state of connection transmission axle 90 and the central gear of forward/backward switching mechanism 92.Meanwhile, make by front The brake that the jaw clutch of the planet carrier entering switching mechanism 92 is constituted engages, and is set to the row making advance switching mechanism 92 The state that carrier connects with power transmission housing.

The power of output shaft 3 is through output one-way clutch 89, transmission axle 90, forward/backward switching mechanism 92, differential Gear 81 and drive shaft 93 are passed to the wheel of vehicle.Traveling driving source ENG, friction clutch 83, forward/backward cut The control of converting mechanism 92 is carried out by the portion ECU of control.

Fig. 6 illustrates that the driving source rotating speed Ne of the vehicle of the power transmission being provided with present embodiment travels speed with vehicle Relation between degree (vehicle velocity V).And, in fig. 6, it is illustrated that the active force as the 1st gear ratio represented by straight line 95 is transmitted Between gear ratio MR and gear ratio AR as the auxiliary power transfer part 80 of the 2nd gear ratio represented by straight line 94 in portion 79 Relation.2nd gear ratio AR e.g. 3.0 of auxiliary power transfer part 80, is fixing as shown in straight line 94.

Control portion ECU controls above-mentioned regulation driving source 14 and regulates the offset (rotation of radius of turn governor motion 4 Radius) R1, thus enable that the 1st gear ratio MR of active force transfer part 79 is in maximum (infinitely great) and the mistake shown in straight line 95 Carry and change between the minima of side.

As it has been described above, outside rotary speed Nb of auxiliary one-way clutch 82 outer shaft 38b at upstream side is than downstream Dally in the case of rotary speed Na of axle 38a big (Nb > Na).Thus, such as cutting off traveling with driving source ENG's When restarting to supply fuel under the deceleration regime of fuel supply, auxiliary one-way clutch 82 becomes idling conditions, it is to avoid by Auxiliary power transfer part 80 transmits power from traveling driving source ENG to differential gear 81.Otherwise, the rotary speed of outer shaft 38a In the case of Na is intended to rotary speed Nb than outer shaft 38b big (Nb < Na), one-way clutch 82 becomes the state of engagement.

Therefore, the 1st gear ratio MR in active force transfer part 79 is less than the 2nd gear ratio AR of auxiliary power transfer part 80 In the case of, auxiliary one-way clutch 82 becomes engagement.In this case, in order to avoid become auxiliary power transfer part 80 with The interlocking of the state of active force transfer part 79 connection, friction clutch 83 must be turned off state.

On the other hand, in the case of the 1st gear ratio MR is bigger than the 2nd gear ratio AR, Nb > Na, auxiliary one-way clutch 82 becomes For idling conditions.In this case, even if friction clutch 83 is connection status, also will not interlock.

Therefore, control portion ECU is under the 1st state that gear ratio MR (the 1st gear ratio) is bigger than gear ratio AR (the 2nd gear ratio) Friction clutch 83 is set as connection status, gear ratio MR (the 1st gear ratio) less than gear ratio AR (the 2nd gear ratio) Under 2 states, friction clutch 83 is set as dissengaged positions.It addition, the 1st state is corresponding with the region A1 in Fig. 6, the 2nd state with Region A2 is corresponding.

Fig. 7 be vehicle deceleration in traveling is shown, friction clutch when stopping and then start to walk and be transferred to transport condition The sequential chart of the control method of 83.As shown in figs. 7 a and 7b, the 1st gear ratio MR of active force transfer part 79 passes than auxiliary power When under 1st state of the 2nd gear ratio AR big (∞ > MR > AR) passing portion 80, vehicle travels with speed V, as it has been described above, friction clutch Device 83 is set to that connection status, auxiliary one-way clutch 82 are in idling conditions.

In this condition, if accelerator open degree becomes 0 at moment t1, then stop fuel supply, therefore travel with driving source ENG Rotary speed Ne decline.Correspondingly, speed V of vehicle is gradually slowed down, rotary speed Nc of outer shaft 84c, outer shaft 84a Rotary speed Ns of rotary speed Na and drive shaft 93 also reduces.

It is accompanied by this, the offset R1 of control portion ECU regulation radius of turn governor motion 4, makes active force transfer part 79 Gear ratio MR reduces.Thus, the 1st gear ratio MR of active force transfer part 79 is close to the 2nd gear ratio of auxiliary power transfer part 80 AR, therefore rotary speed Nc (=Nb) of outer shaft 84c is close to rotary speed Na of outer shaft 84a.

Further, when the difference of MR=AR, rotary speed Nc and rotary speed Na converges on 0, as illustrated in fig. 7d, control portion ECU becomes the moment t2 of the setting close to 0 in this difference, makes to be applied to the friction clutch 83 so far for connection status Clutch plate crimping load M reduce so that friction clutch 83 is between dissengaged positions or dissengaged positions and connection status State.Afterwards, control portion ECU makes crimping load M recover former state, at the moment t3 that difference is 0 of above-mentioned rotary speed, makes friction Clutch 83 reverts to be fully connected state.Afterwards, the 1st gear ratio MR of active force transfer part 79 is set as by control portion ECU Infinitely great (∞).

Thus, time below the value that the difference of rotary speed Nc Yu rotary speed Na is regulation, friction clutch 83 temporarily sets Being set to the state between dissengaged positions or dissengaged positions and connection status, therefore rotary speed Nc becomes with the difference of rotary speed Na 0, thus relax impact when auxiliary one-way clutch 82 becomes engagement.

When one-way clutch 82 becomes conjunction state, it is applied to the driving force of drive shaft 93 from road surface through wheel and passes through Auxiliary power transfer part 80, drives traveling driving source ENG according to the 2nd gear ratio AR.Thus, engine brake plays merit Can, vehicle slows down effectively.

Afterwards, at moment t4 vehicle deceleration to speed v a corresponding with idling rotary speed, then control portion ECU is to operate system Dynamic pedal is condition, makes traveling driving source ENG stop, friction clutch 83 is set as dissengaged positions.Afterwards, vehicle and system The operation of dynamic pedal is correspondingly stopped at moment t5.

Afterwards, when at moment t6, when replacing brake pedal to operate throttle, control portion ECU makes traveling driving source ENG rise Dynamic, friction clutch 83 is switched to connection status.Further, control portion ECU is meanwhile according to rotary speed Nc of outer shaft 84c The offset R1 of regulation radius of turn governor motion 4, proceeds by control, make the 1st gear ratio MR of active force transfer part 79 from Infinitely great reduction.

Afterwards, when rotary speed Nc of outer shaft 84c rises along with throttle operation, vehicle velocity V, the rotation speed of drive shaft 93 Rotary speed Na of degree Ns and outer shaft 38a correspondingly rises, and the 1st gear ratio MR of active force transfer part 79 reduces.And And, reach corresponding with throttle operation at moment t7 and stablize transport condition.

Fig. 8 be vehicle deceleration in traveling is shown, friction clutch when stopping and then start to walk and be transferred to transport condition Other sequential charts of the control method of 83.As shown in Figure 8, the 1st gear ratio MR in active force transfer part 79 passes than auxiliary power Pass under the 2nd state of the 2nd gear ratio AR little (MR < AR < ∞) in portion 80, in the case of vehicle is advanced, assist one-way clutch 82 It is in conjunction state.Now, in order to avoid interlocking, friction clutch 83 is set to dissengaged positions.

When in this condition, accelerator open degree, when the moment, t11 became 0, stops supply fuel, therefore travels and use driving source Rotary speed Ne of ENG declines.Correspondingly, vehicle gradually slows down, rotary speed Na of outer shaft 84a, the rotation of outer shaft 84c Rotary speed Ns of speed Nc and drive shaft 93 also reduces.

Further, while stopping supply fuel, control portion ECU proceeds by the inclined of regulation radius of turn governor motion 4 Heart amount R1 and make the control that the 1st gear ratio MR of active force transfer part 79 is big, and start to increase to friction clutch 83 The control of the crimping load M that clutch plate applies.Further, in the 1st gear ratio MR more than the moment t12 of the 2nd gear ratio AR, rub Clutch 83 is opened to connection status transfer.

When this transfer starts, it is transferred to the power of outer shaft 84b via friction clutch 83 and outer shaft 84c from drive shaft 93 Start to be transferred to traveling driving source ENG.Thus, rotary speed Nc of outer shaft 84c begins to ramp up.During this period, continue to increase The crimping load M that the clutch plate of friction clutch 83 is applied.

Further, at moment t13, friction clutch 83 is entirely connection status, rotary speed Nc of outer shaft 84c and outer shaft Rotary speed Na of 84a is consistent.Thus, from the power of drive shaft 93 by totally tansitive to traveling driving source ENG, the best Carry out well the deceleration of vehicle.Further, as moment t14 later, the 1st gear ratio MR of active force transfer part 79 becomes nothing Time the biggest, slowed down more well.

As moment t15 later, during vehicle deceleration to the most corresponding with idling rotary speed speed v a, control portion ECU with Operation brake pedal is condition, makes traveling driving source ENG stop, friction clutch 83 is set to dissengaged positions.Afterwards, vehicle Stop at moment t16 in response to the operation of brake pedal.

Afterwards, when when moment t17 operation throttle is to replace brake pedal, in the same manner as the situation of Fig. 7, at moment t18 Reach corresponding with throttle operation and stablize transport condition.

According to the 1st embodiment, as it is shown in fig. 7, the 1st gear ratio MR in active force transfer part 79 is transmitted than auxiliary power Under the 1st state that 2nd gear ratio AR in portion 80 is big, the input side of auxiliary one-way clutch 82 and the difference of the rotary speed of outlet side When converging on 0, friction clutch 83 is temporarily set to the state between dissengaged positions or dissengaged positions and connection status.Thus, The impact when engine braking of auxiliary power transfer part 80 starts effective can be relaxed when vehicle deceleration.

Further, according to the 1st embodiment, along with the change of the 1st gear ratio MR of active force transfer part 79, as shown in Figure 8, From the 1st gear ratio MR of active force transfer part 79 2nd status transition less than the 2nd gear ratio AR of auxiliary power transfer part 80 to During described 1 state, friction clutch 83 is gradually transferred to connection status from dissengaged positions.Thus, from the 2nd state to the 1st State transfer and in the case of slowing down, it is possible to make the rotary speed of traveling driving source ENG increase rapidly and rapid Produce fruit of slowing down, gently slow down.

And, according to present embodiment, when vehicle is slowed down by auxiliary power transfer part 80, satisfied operation brake pedal, In the case of being decelerated to the conditions such as the speed corresponding with idling speed, travelling and stop with driving source ENG, friction clutch 83 is cut It is changed to dissengaged positions.Thereby, it is possible to prevent from passing through auxiliary power when further accelerating or reset in implementing idling and stopping Transfer part 80 is accelerated.

Above, although the 1st embodiment of the present invention is illustrated, but the invention is not restricted to the 1st embodiment. Such as, in the 1st embodiment, following situation is illustrated: constituted input by input unit end 2a and multiple cam disc 5 Axle 2, power shaft 2 possess run through insertion hole 60, this run through insertion hole 60 constitute by being connected with the through hole 5a of cam disc 5. But, the input unit of the present invention is not limited to this.

As input unit component parts such as can also: arrange the one end open other end close shape, have and pass through Intert the input unit core of hollow of hand-hole, make to run through insert hole formed than present embodiment to run through insertion hole big so that Input unit core can be run through and be inserted in discoid cam disc, and make each cam disc spline be incorporated into outside input unit core Side face, constitutes the input unit possessing multiple cam disc.

In this case, by the input unit core of hollow, it is arranged in correspondence with cut hole with the cut hole of cam disc.Further, The little gear inserted in input unit engages with the internal tooth of rotating disk through the cut hole of input unit core and the cut hole of cam disc.

Furthermore it is possible to using the input unit of the present invention as the pinion shaft 72 of the 1st embodiment.In this case, utilize Regulation driving source 14 makes the power shaft 2 of the 1st embodiment drive, thus regulates radius of turn.

Additionally, in the above-described embodiment, employ main one-way clutch 17 and stop mechanism as single direction rotation, but, The single direction rotation of the present invention stops mechanism to be not limited to this, it is also possible to be to be configured to following bidirectional clutch: can be from fork to defeated Shaft transmission moment of torsion, and can freely switch the fork direction of rotation relative to output shaft.

Additionally, anglec of rotation θ that offset R1 is the rotating disk 6 during maximum can not be 180 °.Such as merely with arriving In the case of anglec of rotation θ is the gear ratio till gear ratio when 150 °, can be set as rotating by maximum offset R1 Angle, θ is value when 150 °.

Further, as disconnecting clutch, the state between the connection status and the dissengaged positions that produce other can be used also The clutch of this state, such as fluid clutch, centrifugal clutch etc. can be controlled, replace friction clutch 83.

Further, in the power transmission 1 of the 1st embodiment, the power possessing auxiliary one-way clutch 82 is illustrated Transfer device, but the power transmission of the present invention can omit auxiliary one-way clutch.

[the 2nd embodiment]

It follows that with reference to Fig. 9 to Figure 11, the power transmission 1 of the 2nd embodiment of the present invention is illustrated.2nd The power transmission 1 of embodiment, in addition to the action difference of control portion ECU, is configured to identical with the 1st embodiment.? In 2nd embodiment, the label identical to the structure tag identical with the 1st embodiment, and omit the description.

As it is shown in figure 9, the control portion ECU of the 2nd embodiment the most in step 1 based on vehicle velocity V and offset R1 according to The mapping data that control portion ECU is previously stored obtain main joint driving source rotating speed Ne_main.Further, dynamic based on vehicle velocity V and auxiliary 2nd gear ratio (the gear ratio of auxiliary train of gears 86) of power transfer part 80 is obtained auxiliary in step 2 and is engaged driving source rotating speed Ne_ sub。

Additionally, in the 2nd embodiment, the 2nd gear ratio can not speed change, be therefore configured to make auxiliary engage in advance Driving source rotating speed Ne_sub is stored in control portion ECU, reads in step 2.Then, enter step 3, confirm not operate throttle.

In step 3, in the case of control portion ECU confirms that driver does not operates throttle, step 4 is entered, based on speed, system The information of vehicles of the regulations such as the stampede operation amount of dynamic pedal, is confirmed whether that there are auxiliary engages request, and this auxiliary engages request It it is the request when becoming the state needing engine braking.

In the case of confirming auxiliary joint request in step 4, enter step 5, confirm main joint driving source rotating speed Ne_ Main is bigger than auxiliary engages driving source rotating speed Ne_sub.Driving is engaged than auxiliary at main joint driving source rotating speed Ne_main In the case of source rotating speed Ne_sub is big, enter step 6, confirm making on the present actual Ne driving source rotating speed plus described later Obtained by β, value (actual Ne+ β) is bigger than Ne_sub.

Herein, β is to suppress impact when engaging and the fixed value that determines for every kind of vehicle (car type).

In the case of actual Ne+ β is bigger than Ne_sub, enter step 7, switch to from friction clutch connection illegal state The state connect as the friction clutch 83 (disconnecting clutch) of assisted clutch, i.e. friction clutch connection is allowed to allow shape State, terminates current process.Control portion ECU performs the process of the flow chart of Fig. 9 according to the circulation time (controlling the cycle) of regulation.

In step 3, in the case of control portion ECU has confirmed by operator throttle, it is shunted to step 8, controls Portion ECU, based on throttle operation and the information of vehicles of regulation, controls offset R1 so that become the speed change that target drive force is suitable Ratio, terminates current process.

In step 4, in the case of auxiliary unconfirmed engages request, being shunted to step 9, control portion ECU will not make to start Mechanism is dynamic to come into force, and the coast performing to control the moment of torsion (or rotating speed) of R1 and driving source ENG controls so that drive source ENG Driving force be not passed to driving wheel, terminate current process.

In steps of 5, main joint driving source rotating speed Ne_main engages the big situation of driving source rotating speed Ne_sub unlike auxiliary Under, it is shunted to step 10, controls offset R1 so that it is big (to low speed side) that main joint gear ratio engages gear ratio than auxiliary, returns Return step 5.

In step 6, in the case of actual Ne+ β is big unlike Ne_sub, it is shunted to step 11, controls the moment of torsion in driving source And make actual Ne increase, return step 6.

In case of Figure 10 stops after having auxiliary to engage request in low speed travels after vehicle start and slowing down, The action of the power transmission 1 of the 2nd embodiment is shown.The horizontal axis representing time of Figure 10.And, the 3rd counted from above The double dot dash line shown in curve chart of the driving source rotating speed Ne of part represents auxiliary engaging rotating speed Ne_sub.

Vehicle stops, until the t101 moment.Further, in the t101 moment, gas pedal is trampled by driver, vehicle start. And, the t103 moment of more than 10km/h is reached in speed, friction clutch 83 is engaged.It addition, as friction clutch 83 On engaged opportunity, can suitably change between 0km/h～15km/h and set.

Further, in the t105 moment, gas pedal goes off (OFF).Driving source rotating speed (actual Ne) because of gas pedal Disconnect and when naturally declining, in the t107 moment that auxiliary joint Ne_sub is consistent with rotating speed, engine braking comes into force, speed due to Engine braking and decline.When the t109 moment is trampled gas pedal again by driver, vehicle again speeds up.Further, exist In the t111 moment, before main engaging rotating speed Ne_main < auxiliary engaging rotating speed Ne_sub, discharge friction clutch 83.

Further, in the t115 moment, throttle goes off again, it is thus identified that after the deceleration request of vehicle, in the t117 moment Drop to actual Ne at rotating speed become auxiliary and engage before Ne_sub, it is considered to the generation of impact and make friction clutch 83 engage.

Further, if drive source rotating speed, the actual Ne of reality drop to the idling speed of driving source ENG, then the driving of reality Dynamic source rotating speed, actual Ne are controlled so as to maintain idling speed.Further, in the t119 moment, the travel speed (speed) of vehicle is no During foot 10km/h, discharge friction clutch 83.Further, at t121 moment vehicle parking.

In case of Figure 11 stops after having auxiliary to engage request in travelling by high speed after vehicle start and slowing down, The action of the power transmission 1 of the 2nd embodiment is shown.The horizontal line express time of Figure 11.And, the 3rd counted from above The chain-dotted line of the curve chart of the driving source rotating speed Ne of part represents main engaging rotating speed Ne_main, and double dot dash line represents that auxiliary engages Rotating speed Ne_sub.

Vehicle parking, until the t201 moment.Further, in the t201 moment, gas pedal is trampled by driver, vehicle start. And, the t203 moment of more than 10km/h is reached in speed, friction clutch 83 is engaged.Further, in the t205 moment, main joint Friction clutch 83 is discharged before rotating speed Ne_main < auxiliary engaging rotating speed Ne_sub.

Further, in the t207 moment, the tread-on quantity of the gas pedal of driver is 0.Now, offset r1 is made to turn to low speed side Move and as standby offset r1, improve main engaging rotating speed Ne_main.

Further, in the t209 moment, control portion ECU confirms main engaging rotating speed Ne_main > auxiliary engaging rotating speed Ne_sub time, Control portion ECU makes friction clutch 83 engage.Further, in the t211 moment, improved by the joint (half engages) of friction clutch 83 Actual Ne reach assist engaging rotating speed Ne time, then be transferred to the deceleration regime making engine braking come into force.

Further, in the t213 moment, driver when again trampling gas pedal, in order to release engine braking, and make to rub Wipe clutch 83 to discharge.Further, while release friction clutch 83, it is possible to make offset R1 shift to high-speed side, reduce Main engaging rotating speed Ne_main, transfers a driving force to rapidly tire.

Further, in the t219 moment, the tread-on quantity (aperture) of gas pedal becomes 0, when the t207 moment in the same manner as, make standby Offset R1 shifts to low speed side, improves main engaging rotating speed Ne_main to the rotating speed exceeding auxiliary engaging rotating speed Ne_sub.

And in the t221 moment, control portion ECU confirms that main engaging rotating speed Ne_main has exceeded auxiliary engaging rotating speed Ne_sub Time, control portion ECU makes friction clutch 83 engage, and improves actual Ne.Further, it is increased to auxiliary at t223 moment actual Ne connect When closing rotating speed Ne_sub, engine braking based on auxiliary power transfer part 80 comes into force.

Further, in the t225 moment, actual Ne is the rotating speed lower than idling speed, when becoming necessary to maintenance idling speed When the i.e. idling of the rotating speed of minimum recovers rotating speed, actual Ne is improved to idling speed and becomes idling conditions, and utilize auxiliary The state helping the engine braking of power transfering part 80 to come into force terminates.Further, when speed drops to the speed using idling parking (t227 moment), make driving source ENG stop, and make friction clutch 83 discharge, offset R1 is set as 0, will active force 1st gear ratio of transfer part 79 is set as infinity.

According to the power transmission 1 of the 2nd embodiment, when for actual driving source rotating speed (actual Ne) than main engaging rotating speed During low for Ne_main state, in the case of main engaging rotating speed Ne_main is higher than auxiliary engaging rotating speed Ne_sub, it is allowed to disconnecting from Clutch engages.Thus, the present invention is it can be avoided that may carry out from both active force transfer part 79 and auxiliary power transfer part 80 The state (interlocking state) of power transmission.

And, according to the power transmission 1 of the 2nd embodiment, drive source rotating speed (actual Ne) ratio if not reality Main state low for engaging rotating speed Ne_main, does not the most allow to engage as the friction clutch 83 of disconnecting clutch.Therefore, rubbing Wipe under the state that clutch 83 is released, have auxiliary to engage request and control portion ECU must be based on driving source moment of torsion and controls to drive During dynamic source rotating speed, only control into actual driving source rotating speed (actual Ne) and be just prevented from defeated less than main engaging rotating speed Ne_main Go out the driving force of waste, therefore need not adjust driving source moment of torsion accurately and just can stably control driving source rotating speed.

Additionally, in the power transmission 1 of the 2nd embodiment, about the rotation half of the rotating disk 6 as rotating part Footpath, when being transferred to deceleration regime from acceleration mode, controls radius of turn R1 of rotating disk 6 so that main engaging rotating speed Ne_main Higher than the auxiliary engaging rotating speed Ne_sub when auxiliary power transfer part side transmission power.

Thus, by radius of turn R1 of rotating disk 6 is controlled less, it is possible to make main engaging rotating speed Ne_main rapid To the rotating speed transfer higher than auxiliary engaging rotating speed Ne_sub such that it is able to gently make the power via auxiliary power transfer part 80 Transmit, i.e. come into force via the engine braking of auxiliary power transfer part 80 (auxiliary train of gears 86).

Additionally, in the 2nd embodiment, following situation is illustrated: in a same manner as in the first embodiment, by inputting End, portion 2a and multiple cam disc 5 constitute power shaft 2, power shaft 2 possess run through insertion hole 60, this run through insertion hole 60 by with The through hole 5a of cam disc 5 connects and constitutes.But, the input unit of the present invention is not limited to this.

As input unit component parts such as can also: arrange the one end open other end close shape, have and pass through The input unit core of the hollow of interspersed hand-hole, makes through hole be formed bigger than present embodiment, enabling by input unit core Portion runs through and is inserted in discoid cam disc, and makes each cam disc spline be incorporated into the outer peripheral face of input unit core, and composition possesses The input unit of multiple cam discs.

In this case, cut hole with cam disc on the input unit core of hollow it is being arranged in correspondence with cut hole.Further, The little gear inserted in input unit core engages with the internal tooth of rotating disk via the cut hole of input unit core and the cut hole of cam disc.

Furthermore it is possible to using the input unit of the present invention as the pinion shaft 72 of the 2nd embodiment.In this case, utilize Regulation driving source 14 makes the power shaft 2 of the 2nd embodiment drive, thus regulates radius of turn.

Additionally, in the 2nd embodiment, employ main one-way clutch 17 and stop mechanism as single direction rotation, but, this Invention single direction rotation stop mechanism be not limited to this, can be such as following bidirectional clutch: be configured to from fork to Output shaft transmission moment of torsion freely switch the fork direction of rotation relative to output shaft.

Additionally, anglec of rotation θ that offset R1 is the rotating disk 6 during maximum can not be 180 °.Such as merely with arriving In the case of anglec of rotation θ is the gear ratio till gear ratio when 150 °, maximum offset R1 can be set to rotation Angle, θ is value when 150 °.

Further, as disconnecting clutch, the state between the connection status and the dissengaged positions that produce other can be used also The clutch of this state, such as fluid clutch, centrifugal clutch etc. can be controlled, replace friction clutch 83.

Further, the power transmission 1 of the 2nd embodiment is in a same manner as in the first embodiment, it is also possible to omit the 2nd unidirectional Clutch 82.

Label declaration

1: power transmission；2: power shaft；2a: power shaft end (input unit)；3: output shaft；4: radius of turn regulates Mechanism；5: cam disc (cam part)；6: rotating disk (rotating part)；17: main one-way clutch (single direction rotation stops mechanism)；18: Fork；20: crank and rocker mechanism (four joint linkages)；79: active force transfer part；80: auxiliary power transfer part；81: differential Gear；82: auxiliary one-way clutch；83: friction clutch (disconnecting clutch)；84: outer shaft；84a: outer shaft；84b: outer shaft； 84c: outer shaft；86: auxiliary train of gears；86a: auxiliary input side gear；86b: auxiliary idler gear；86c: auxiliary outlet side tooth Wheel；89: output one-way clutch；ECU: control portion；ENG: travel and use driving source；R1: offset (radius of turn).

Claims (8)

1. a power transmission, it is characterised in that

Described power transmission possesses:

Active force transfer part, the driving force in the traveling driving source of vehicle is transferred to this with the 1st gear ratio that can regulate by it The differential gear of vehicle；And

Auxiliary power transfer part, power is transferred to described traveling with driving from described differential gear with the 2nd gear ratio of regulation by it Dynamic source,

Described active force transfer part possesses:

Input unit, it is transfused to the driving force in described traveling driving source and rotates；

Output shaft, it is configured to parallel with the center of rotation axis of described input unit, is connected with described differential gear；

Crank and rocker mechanism, it has by the fork of output shaft described in axle Zhi Yu, the rotary motion of described input unit is converted to The oscillating motion of described fork；

Radius of turn governor motion, it is for including the described 2nd by adjusting the radius of turn of described crank and rocker mechanism Described 1st gear ratio is controlled in the range of gear ratio；And

Single direction rotation stops mechanism, when described fork is intended to relatively rotate, this unidirectional rotation relative to the axial side of described output Turn and stop mechanism to be fixed on this output shaft by this fork, when this fork is intended to relatively rotate relative to the axial opposite side of this output Time, this single direction rotation stops mechanism to make this fork dally relative to this output shaft,

Described auxiliary power transfer part possesses:

Disconnecting clutch, it for switching to connection status and cutting off shape by the power transfer path of this auxiliary power transfer part State；And

Control portion, it controls described disconnecting clutch,

Described disconnecting clutch is set under the 1st state that described 1st gear ratio is bigger than described 2nd gear ratio by described control portion For connection status, under the 2nd state that described 1st gear ratio is less than described 2nd gear ratio, described disconnecting clutch is set as Dissengaged positions.

Power transmission the most according to claim 1, it is characterised in that

The gear ratio along with described active force transfer part change and from described 2nd status transition to described 1 state time, institute State control portion to be controlled so that described disconnecting clutch is gradually transferred to connection status from dissengaged positions, this disconnecting clutch The rotary speed of both sides consistent time or consistent after become being fully connected state.

Power transmission the most according to claim 1 and 2, it is characterised in that

Under described 1st state, it is passed to described travel with drive through described auxiliary power transfer part because of power at described vehicle Dynamic source and when slowing down, described control portion becomes below the value of regulation along with the speed of described vehicle and makes described traveling driving source Stop, and described disconnecting clutch is set as dissengaged positions.

Power transmission the most according to claim 3, it is characterised in that

Described auxiliary power transfer part possesses auxiliary one-way clutch, when described traveling drives source and described differential gear side Compare rotary speed big time, described auxiliary one-way clutch dally, when described travelings driving source from described differential gear side When accepting power, described auxiliary one-way clutch engages.

Power transmission the most according to claim 1, it is characterised in that

Described auxiliary power transfer part possesses auxiliary one-way clutch, when described traveling drives source and described differential gear side Compare rotary speed big time, described auxiliary one-way clutch dally, when described travelings driving source from described differential gear side When accepting power, described auxiliary one-way clutch engages.

6. a power transmission, it is characterised in that

Described power transmission possesses:

Active force transfer part, it is with the 1st gear ratio the driving the traveling driving source can being equipped in vehicle that can regulate Power is transferred to the differential gear of this vehicle；And

Auxiliary power transfer part, power is transferred to described traveling with driving from described differential gear with the 2nd gear ratio of regulation by it Dynamic source,

Described active force transfer part possesses:

Input unit, it is transfused to the driving force in described traveling driving source and rotates；

Output shaft, it is configured to parallel with the center of rotation axis of described input unit, exports driving force to described differential gear；

Crank and rocker mechanism, it has by the fork of output shaft described in axle Zhi Yu, the rotary motion of described input unit is converted to The oscillating motion of described fork；

Radius of turn governor motion, it is for including the described 2nd by regulating the radius of turn of described crank and rocker mechanism Described 1st gear ratio is controlled in the range of gear ratio；And

Single direction rotation stops mechanism, when described fork is intended to relatively rotate, this unidirectional rotation relative to the axial side of described output Turn and stop mechanism to be fixed on described output shaft by described fork, when described fork is intended to relative to described output axial opposite side phase When rotating over the ground, this single direction rotation stops mechanism to make described fork dally relative to described output shaft,

Described auxiliary power transfer part possesses:

Disconnecting clutch, it for switching to connection status and cutting off shape by the power transfer path of described auxiliary power transfer part State；And

Control portion, it controls described disconnecting clutch,

The engaging condition of described disconnecting clutch includes:

Relative to main engaging rotating speed, the actual driving source rotating speed as present driving source rotating speed is relatively low, wherein, and described main joint Rotating speed be the radius of turn by described radius of turn governor motion and car speed determine can carry out described single direction rotation resistance The driving source rotating speed of the power transmission of locking mechanism；And

I.e. assist engaging rotating speed relatively low relative to described main engaging rotating speed at the driving source rotating speed driven according to described 2nd gear ratio In the case of, it is allowed to the joint of described disconnecting clutch.

Power transmission the most according to claim 6, it is characterised in that

About the radius of turn of described radius of turn governor motion, from acceleration mode to deceleration regime transition time, half will be rotated Footpath controls less, described main engaging rotating speed controls into the rotating speed than driving according to described 2nd gear ratio high.

8. according to the power transmission described in claim 6 or 7, it is characterised in that

Described auxiliary power transfer part possesses auxiliary one-way clutch, when described traveling drives source and described differential gear side Compare rotary speed big time, described auxiliary one-way clutch dally, when described travelings driving source from described differential gear side When accepting power, described auxiliary one-way clutch engages.