CN105659004B - Power transmission - Google Patents

Abstract

A kind of power transmission is provided, the power transmission returned to from slipping state grab ground state when, can reduce act on single direction rotation prevent mechanism load.In power transmission, gear ratio can be changed by changing offset (R1), according to offset (R1), make the driving force speed change of traveling driving source (50) and be transferred to driving wheel (60), from when detecting that state is transformed to skidding detection state with grabbing, radius control process when the control device (40) of power transmission is controlled the skidding of offset (R1), ground state is grabbed so that having been returned to even in current time, one-way clutch (17) also turns into idling conditions.

Description

Power transmission

Technical field

The present invention relates to the power transmission with crank and rocker mechanism.

Background technology

In the past, it is known that the power transmission of the buncher with quadric chain type, the buncher has： Input unit, it is communicated to the driving force from traveling driving sources such as the engines located at vehicle；Output shaft, it joins with driving wheel Knot, and be configured to parallel with the center of rotation axis of input unit；Multiple crank and rocker mechanisms；And control device, it controls row Sail the action with driving source and crank and rocker mechanism (for example, referring to patent document 1).

The crank and rocker mechanism of patent document 1 is made up of following part：Located at the radius of turn governor motion of input unit；With The mode that can freely swing is supported on the shaft on the swing rod on output shaft；And connecting rod, it has on one end can be with freedom The swing end of the mode of rotation and the outer input side annulus of radius of turn governor motion, another end and swing rod joins Knot.

It is provided between swing rod and output shaft as single direction rotation and prevents the one-way clutch of mechanism, the single direction rotation is prevented Mechanism allow hand over for：When to be rotated against relative to the axial side of output, swing rod is relative to the idling conditions that output shaft dallies (so-called disengaged position)；With when to be rotated against relative to the axial opposite side of output swing rod be fixed on consolidating on output shaft Determine state (so-called engagement).

Prior art literature

Patent document

Patent document 1：Japanese Unexamined Patent Publication 2013-47492 publications

The content of the invention

The invention problem to be solved

In the power transmission described in patent document 1, when the non-slip state of the driving wheel from vehicle (grabs ground (grip) state) when being changed into slipping state, the load for acting on traveling driving source and driving wheel largely reduces, by This traveling increased dramatically with the output rotary speed of driving source and the rotary speed of driving wheel.Also, returned from slipping state To when grabbing ground state, the rotary speed of driving wheel is strongly reduced, and then, the rotary speed for the output shaft being coupled with driving wheel Strongly reduce.Now, when the rotary speed of output shaft is less than the rotation for the swing rod for being communicated to the power from traveling driving source During speed, mechanism is prevented to act on larger load to single direction rotation.

The present invention exactly in view of the above and complete, its object is to there is provided a kind of power transmission, from beating Sliding state has been returned to when grabbing ground state, can be reduced and be acted on the load that single direction rotation prevents mechanism.

Means for solving the problems

The present invention is a kind of power transmission, and it has：Input unit, it is passed the drive of the traveling driving source of vehicle Power；Output shaft, it is configured to parallel with the center of rotation axis of the input unit；Crank and rocker mechanism, it has axle branch Swing rod on the output shaft, by the swing for being converted to the swing rod of the input unit；And single direction rotation is prevented Mechanism, it can switch between idling conditions and stationary state, wherein, the idling conditions refers to will be relative to the output The swing rod is relative to the state that the output shaft dallies when rotating against for axial side, and the stationary state refers to will be relative to The swing rod is fixed on the state on the output shaft, the crank rocker machine when the axial opposite side of output is rotated against Structure has：Regulation driving source；Radius of turn governor motion, it can freely be adjusted by the driving force of the regulation driving source Radius of turn when section is pivoted about with the center of rotation axis；And connecting rod, it is coupled radius of turn regulation Mechanism and the swing rod, the power transmission can be by changing the radius of turn of the radius of turn governor motion To change gear ratio, according to the radius of turn, make the driving force speed change of the traveling driving source and be transferred to the vehicle Driving wheel, the power transmission is characterised by, with control device, in the skidding shape skidded in the driving wheel During state, radius control process when the control device is controlled the skidding of the radius of turn so that even in current time Return to the driving wheel grab (grip) grab ground state, the single direction rotation prevents mechanism from also turning into the idling conditions.

In the present invention, from when grabbing ground state transformation for slipping state, control device is controlled to radius of turn System so that returned to even in current time and grabbed ground state, single direction rotation prevents mechanism from also turning into idling conditions.Therefore, exist From slipping state transformation in order to grab during ground state, single direction rotation prevents mechanism from turning into idling conditions, is acted on therefore, it is possible to reduce Single direction rotation prevents the load of mechanism.

In the present invention, it is preferred that in slipping state, the control device, which is performed, makes the traveling driving source Traveling uses driving source speed reduction process, and the radius control process in the skidding during skidding of output rotary speed reduction In, even in current time returned to grab ground state also by the single direction rotation prevention mechanism maintain the idling conditions In the range of, increase the radius of turn in response to the reduction of the output rotary speed of the traveling driving source, from Slipping state has been returned to when grabbing ground state, and the control device, which is performed, controls the traveling driving source or the radius of turn Skidding at the end of handle so that the single direction rotation prevents mechanism from turning into the stationary state.

If in the case of the rotary speed identical of output shaft, the output rotary speed reduction of traveling driving source, then Compared with before reduction, single direction rotation prevent mechanism from idling conditions be changed into stationary state when radius of turn increase.

Therefore, according to said structure, in slipping state, control device even in current time returned to grab ground shape In the range of single direction rotation prevention mechanism is also maintained idling conditions by state, in response to the output rotary speed of traveling driving source Reduction and increase radius of turn.Thus, control device returned to from slipping state grab ground state and perform skidding and terminate When handling, if control traveling driving source or radius of turn, can prevent single direction rotation within the shorter time Mechanism is set to stationary state.

In the present invention, it is preferred that the control device is in the skidding in radius control process, in the output It is and defined less than described in the case that the reduction amount of the rotary speed of axle or the time variation amount of reduction amount are more than defined measure The situation of amount is compared, and further reduces the radius of turn.

According to the structure, situations below can be prevented in advance：Due to the reduction amount or reduction amount of the rotary speed of output shaft Time variation amount be more than defined amount (this for example produced by operating the brake apparatus of vehicle in that case of slowing down It is raw) so that the rotary speed of output shaft is less than the rotary speed for the swing rod for being communicated to the power from traveling driving source.By This, can prevent from preventing mechanism from acting on larger load to single direction rotation.

In the present invention, it is preferred that the control device is in the skidding in radius control process, based on the row The output rotary speed with driving source and the translational speed of the vehicle are sailed, the radius of turn is controlled.

According to the structure, control device can pass through the output rotary speed based on traveling driving source and the movement of vehicle Speed, accurately controls radius of turn.

Brief description of the drawings

Fig. 1 is the sectional view for the power transmission for showing embodiments of the present invention.

Fig. 2 be from end on observation to present embodiment power transmission radius of turn governor motion, connecting rod, pendulum The figure of bar.

Fig. 3 is the change of the radius of turn of the radius of turn governor motion for the power transmission for illustrating present embodiment Figure.Fig. 3 A show the maximum state of radius of turn, and Fig. 3 B show that radius of turn is medium state, and Fig. 3 C show rotation The less state of radius, Fig. 3 D show the state that radius of turn is 0.

Fig. 4 be the radius of turn of the radius of turn governor motion for the power transmission for showing present embodiment change with The figure of relation between the angle of oscillation θ 2 of the oscillating motion of swing rod, Fig. 4 A show the oscillating motion of swing rod when radius of turn is maximum Angle of oscillation, Fig. 4 B show radius of turn for it is medium when swing rod oscillating motion angle of oscillation, Fig. 4 C show radius of turn compared with The angle of oscillation of the oscillating motion of the swing rod of hour.

Fig. 5 is the change with the radius of turn of radius of turn governor motion for the power transmission for showing present embodiment The curve map of the change of the angular velocity omega of corresponding swing rod.

Fig. 6 is shown in the power transmission of present embodiment, passes through 6 crank rockers for making phase differ 60 degree respectively Mechanism makes the curve map of the state of output shaft rotation.

Fig. 7 be power transmission, swing rod the angular speed and output shaft that show present embodiment angular speed with The figure of relation between idling conditions and stationary state.

Fig. 8 is to show the relation between the output rotary speed of speed, offset and traveling driving source and boundary line Figure.

Fig. 9 is the functional block diagram of the structure of the control device for the power transmission for showing present embodiment.

Figure 10 is the flow chart of the processing of the control device for the power transmission for showing present embodiment.

Figure 11 be show from grab ground state be changed into slipping state after, again return to each information of vehicles when grabbing ground state Time change timing diagram.

Figure 12 A are angular speed, the angular speed of output shaft 3 and the imaginary boundary output for showing the swing rod 18 before moment t1 The figure of relation between axis angular rate, Figure 12 B be the angular speed of the swing rod 18 when showing moment t2, output shaft 3 angular speed with And the figure of the relation between imaginary boundary output axis angular rate, Figure 12 C are the angular speed of the swing rod 18 when showing moment t3, output The figure of relation between angular speed and imaginary boundary the output axis angular rate of axle 3, Figure 12 D are the swing rods 18 when showing moment t5 Angular speed, the angular speed of output shaft 3 and imaginary boundary output axis angular rate between relation figure, Figure 12 E are when showing Angular speed, the angular speed of output shaft 3 and the imaginary boundary of swing rod 18 when carving t7 export the figure of the relation between axis angular rate.

Embodiment

(structures of 1. power transmissions)

Illustrate the embodiment of the power transmission of the present invention below.Power transmission 1A (the ginsengs of present embodiment According to Fig. 9) have gear ratio i (rotary speed of rotary speed/output shaft of i=input shafts) can be set to infinitely great (∞) and The rotary speed of output shaft is set to the buncher of " 0 ", i.e. so-called IVT (Infinity Variable Transmission：Infinite buncher).

Reference picture 1, buncher 1 is installed in vehicle C (reference picture 9), with hollow input shaft 2 (equivalent to " input unit " of the present invention), the input shaft 2 is driven by receiving from travelings such as the engines or motor as internal combustion engine The rotary driving force in source 50 (reference picture 9) and pivoted about with input center axis P1.In addition, buncher 1 has Have：Output shaft 3, its be configured to it is parallel with input shaft 2, and via differential gearing (not shown), power transmission shaft etc. to vehicle C driving Take turns 60 (reference picture 9) transmitting rotary powers；And located at 6 radius of turn governor motions 4 of input shaft 2.

As shown in Fig. 2 each radius of turn governor motion 4 has cam disc 5 and rotating disk 6.Cam disc 5 be it is discoid, It is separately positioned in the way of being rotated integrally from input center axis P1 bias and with input shaft 2 on input shaft 2 two by 1 group. Each group cam disc 5 makes phase differ 60 degree respectively, is configured to by 6 groups of cam discs 5 in input shaft 2 circumferentially around one week.In addition, Discoid rotating disk 6 with the receiving opening 6a for receiving cam disc 5 is in the state of relative to the bias of cam disc 5 with energy Each group cam disc 5 is embedded in outside the mode enough rotated freely.

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 is to cause input center axle The distance between line P1 and center point P 2 Ra are equal to the distance between center point P 2 and center point P 3 Rb mode, relative to cam Disk 5 is eccentric.

The internal tooth 6b being located between 1 group of cam disc 5 is provided with the receiving opening 6a of rotating disk 6.On input shaft 2 (Fig. 1) It is formed between 1 group of cam disc 5 and opposed position on the eccentric direction of cam disc 5 connects inner peripheral surface and outer peripheral face Logical cut hole 2a.

Pinion shaft 7 is configured with the mode concentric with input shaft 2 in hollow input shaft 2.Pinion shaft 7 with rotation The corresponding position of rotating disk 6 has external tooth 7a.In addition, pinion shaft 7 is configured to rotate freely relative to input shaft 2.Small tooth The external tooth 7a of wheel shaft 7 is engaged via the cut hole 2a of input shaft 2 with the internal tooth 6b of rotating disk 6.

Pinion shaft 7 is connected with differential attachment 8.Differential attachment 8 is made up of planetary gears, with sun gear 9, with it is defeated Enter the 1st gear ring 10 of the connection of axle 2, the 2nd gear ring 11 and planet carrier 13 that are coupled with pinion shaft 7, the planet carrier 13 is with can Free rotation and revolution mode axle Zhi Youyu sun gears 9 and the 1st gear ring 10 engagement major diameter portion 12a and with the 2nd gear ring The stepwise little gear 12 that the minor diameter 12b of 11 engagements is constituted.

Be linked with sun gear 9 motor drive mechanism by pinion shaft 7 into regulation driving source 14 rotary shaft 14a. When regulation is set into identical with the rotary speed of input shaft 2 with the rotary speed of driving source 14, the gear ring 10 of sun gear 9 and the 1st Rotated with same speed.Thus, turn into can not for sun gear 9, the 1st gear ring 10, the 2nd gear ring 11 and planet carrier 13 this 4 key elements The lock-out state rotated against, the pinion shaft 7 being coupled with the 2nd gear ring 11 with the same speed of input shaft 2 rotate.

When regulation is set into slower than the rotary speed of input shaft 2 with the rotary speed of driving source 14, by turning for sun gear 9 Speed is set to the gear ratio (number of teeth of the 1st gear ring 10/too that Ns, the rotating speed of the 1st gear ring 10 are set to NR1, the gear ring 10 of sun gear 9 and the 1st The number of teeth of sun wheel 9) be set to j, then the rotating speed of planet carrier 13 is (jNR1+Ns)/(j+1).

Also, if set the gear ratio ((number of teeth of the number of teeth/sun gear 9 of the 2nd gear ring 11) of the gear ring 11 of sun gear 9 and the 2nd × (the major diameter portion 12a of the stepwise little gear 12 number of teeth/minor diameter 12b number of teeth)) be k, then the rotating speed of the 2nd gear ring 11 is {j(k+1)NR1+(k-j)Ns}/{k(j+1)}。

In the case of the rotating speed identical of the rotating speed of input shaft 2 of cam disc 5 and pinion shaft 7 is fixed with, rotating disk 6 with Cam disc 5 together integratedly rotates.In the case of there is difference between the rotating speed of input shaft 2 and the rotating speed of pinion shaft 7, rotation Disk 6 is rotated centered on the center point P 2 of cam disc 5 in the periphery of cam disc 5.

As shown in Fig. 2 rotating disk 6 is eccentric relative to cam disc 5 with turning into identical mode apart from Rb apart from Ra to cause. Center point P 3 therefore, it is possible to make rotating disk 6 makes input center on the axis for turning into same line with input center axis P1 Axis P1 and the distance of center point P 3, i.e. offset R1 are " 0 ".

There is the large-diameter annual portion 15a of major diameter on one end, have on another end than major diameter ring The large-diameter annual portion 15a of the small minor diameter annulus 15b of shape portion 15a diameter connecting rod 15 ball bearing by being made up of The connecting-rod bearing 16, in the way of it can rotate freely outside be embedded in the periphery of rotating disk 6.On output shaft 3, unidirectionally revolved by being used as Turn the one-way clutch 17 of prevention mechanism, with connecting rod 15 accordingly provided with 6 swing rods 18.

The one-way clutch 17 for preventing mechanism as single direction rotation is located between swing rod 18 and output shaft 3.When will be relative to Output shaft 3 to side rotate against when, swing rod 18 is fixed on output shaft 3 by one-way clutch 17, when relative to opposite side During rotation, one-way clutch 17 makes swing rod 18 be dallied relative to output shaft 3.Swing rod 18 is turning into relative by one-way clutch 17 When the state that output shaft 3 dallies, freely swing relative to output shaft 3.

Swing rod 18 is formed as ring-type, the swing end being coupled above it provided with the minor diameter annulus 15b with connecting rod 15 18a.Swinging on the 18a of end by a pair of tab 18b provided with protrusion in the way of axially minor diameter annulus 15b is sandwiched. Through hole 18c corresponding with minor diameter annulus 15b internal diameter is provided through on a pair of tab 18b.In through hole 18c and small Inserted with coupling pin 19 in diameter annular portion 15b.Thus, connecting rod 15 and swing rod 18 are joined together.

Fig. 3 show to make radius of turn governor motion 4 offset R1 (between input center axis P1 and center point P 3 away from From) in the state of change, position relationship between pinion shaft 7 and rotating disk 6.Fig. 3 A show to make offset R1 turn into " most State greatly ".Now, the position relationship between pinion shaft 7 and rotating disk 6 turns into input center axis P1, cam disc 5 Heart point P2, the center point P 3 of rotating disk 6 arrange position relationship in alignment.Gear ratio i now is minimum.

Fig. 3 B show make offset R1 be " medium " smaller than Fig. 3 A state, Fig. 3 C show make offset R1 be than The state of " small " smaller Fig. 3 B.In figure 3b, gear ratio i is big the gear ratio i than Fig. 3 A " medium ", in fig. 3 c, is become Speed is big the gear ratio i than Fig. 3 B " big " than i.

Fig. 3 D show to make offset R1 to turn into the state of " 0 ", and the center point P 3 of input center axis P1 and rotating disk 6 is located at At concentric position.Gear ratio i now turns into infinitely great (∞).The buncher 1 of present embodiment utilizes radius of turn Governor motion 4 changes offset R1, thereby, it is possible to the radius for the rotary motion for freely adjusting radius of turn governor motion 4.At this In embodiment, radius (that is, of the invention " rotations of the offset R1 substantially with the rotary motion of radius of turn governor motion 4 Radius ") it is identical.

As shown in Fig. 2 the radius of turn governor motion 4 of present embodiment, connecting rod 15, swing rod 18 constitute crank and rocker mechanism 20 (quadric chains).Moreover, the swing that the rotary motion of input shaft 2 is converted to swing rod 18 is transported by crank and rocker mechanism 20 It is dynamic.The buncher 1 of present embodiment, which has, adds up to 6 crank and rocker mechanisms 20.

When offset R1 is not " 0 ", if rotating input shaft 2, and make pinion shaft 7 with identical with input shaft 2 Speed rotation, then each connecting rod 15 change 60 degree of phases every time on one side, while based on offset R1 alternately repeatedly in input shaft 2 It is pushed between output shaft 3 to the side of output shaft 3 or goes out to the layback of input shaft 2 and swung.

The minor diameter annulus 15b of connecting rod 15 is coupled with the swing rod 18 set on output shaft 3 by one-way clutch 17. Therefore, when swing rod 18 is swung by the push-and-pull of connecting rod 15, output shaft 3 only when swing rod 18 towards push away in the side of direction Ce Huola directions appoint The side that anticipates is rotated when rotating.

When swing rod 18 rotates towards the opposing party, the power of the oscillating motion of swing rod 18 output shaft 3 is not delivered to, swing rod 18 enters Row idle running.Due to being configured to each radius of turn governor motion 4 to differ 60 degree of phases respectively, therefore, adjusted by each radius of turn Section mechanism 4 successively rotates output shaft 3.

Fig. 4 A show being adjusted relative to radius of turn (when gear ratio i is minimum) during " maximum " that offset R1 is Fig. 3 A The hunting range θ 2 of the swing rod 18 of the rotary motion of mechanism 4, Fig. 4 B show (gear ratio i during " medium " that offset R1 is Fig. 3 B For it is medium when) the rotary motion relative to radius of turn governor motion 4 swing rod 18 hunting range θ 2, Fig. 4 C show bias The swing rod 18 of the rotary motion relative to radius of turn governor motion 4 when " small " that amount R1 is Fig. 3 C (when gear ratio i is big) Hunting range θ 2.

As shown in Figure 4, as offset R1 diminishes, the hunting range θ 2 of swing rod 18 narrows.Also, it is in offset R1 When " 0 ", swing rod 18 is not swung.In addition, in the present embodiment, will in the swing end 18a of swing rod 18 hunting range θ 2 Position closest to input shaft 2 is set to inner dead centre, and the position farthest away from input shaft 2 is set to the bottom dead-centre.

Fig. 5 with the anglec of rotation θ 1 of the radius of turn governor motion 4 of buncher 1 for transverse axis and using angular velocity omega as The longitudinal axis, shows the angular velocity omega _ i for the swing rod 18 that the change with the offset R1 of radius of turn governor motion 4 is accompanied change The relation of change.As shown in Figure 5, offset R1 bigger (gear ratio i is smaller), angular velocity omega _ i of swing rod 18 is bigger.

Fig. 6 shows (to make input shaft 2 and small tooth during 6 radius of turn governor motions 4 for making phase differ 60 degree respectively rotation When wheel shaft 7 is rotated with same speed), the angle speed of each swing rod 18 of anglec of rotation θ 1 relative to radius of turn governor motion 4 Spend ω _ i.It will be appreciated from fig. 6 that making output shaft 3 successfully rotate by 6 crank and rocker mechanisms 20.

In addition, as shown in figure 9, buncher 1 has control device 40.Control device 40 is by CPU and memory etc. The electronic unit of composition.

Control device 40 performs the control for keeping traveling driving source 50 and buncher 1 in memory using CPU System program, thus controls the action of traveling driving source 50 and regulation driving source 14.In addition, control device 40 passes through control The action of regulation driving source 14, to realize the function for the offset R1 for controlling radius of turn governor motion 4.

In addition, being provided with the vehicle C of buncher 1 has：Detect the rotary speed of the input shaft 2 of buncher 1 (the example of input side rotary speed test section 41 of (identical with the output rotary speed Ne of driving source 50 with traveling in present embodiment) Such as rotation speed sensor)；Detect the driving wheel rotary speed test section 42 of rotary speed of vehicle C driving wheel 60 (for example Rotation speed sensor)；And (the example of driven pulley rotary speed test section 43 of the rotary speed of detection vehicle C driven pulley 61 Such as rotation speed sensor).

To control device 40 have input input side rotary speed test section 41, driving wheel rotary speed test section 42 and from Each output signal of driving wheel rotary speed test section 43.Control device 40 is believed according to the output of input side rotary speed test section 41 Number, detect output rotary speed Ne of the traveling with driving source 50 (unit is, for example, [rpm]).

In addition, output signal of the control device 40 according to driving wheel rotary speed test section 42, detects the rotation of driving wheel 60 Rotary speed is (hereinafter referred to as " driving wheel rotary speed ".Unit is, for example, [rpm]) Ndrive.Control device 40 is based on detecting " driving wheel rotary speed Ndrive " and " gear ratio between output shaft 3 and driving wheel 60 " detect the rotary speed of output shaft 3 No (unit is, for example, [rpm]).

In addition, output signal of the control device 40 based on driven pulley rotary speed test section 43, detects the rotation of driven pulley 61 Rotary speed (hereinafter referred to as " driven pulley rotary speed ") Ndriven (unit is, for example, [rpm]).Control device 40 is based on detecting Driven pulley rotary speed Ndriven, (unit is, for example, [km/ to V to detection vehicle C travel speed (hereinafter referred to as " speed ") h])。

(states of 2. one-way clutch)

(that is, input shaft 2 can will be come from when swing rod 18 is fixed on output shaft 3 by reference picture 7 for one-way clutch 17 Driving force when being delivered to output shaft 3) and when the swing rod 18 is dallied relative to output shaft 3 (i.e., it is impossible to input shaft 2 will be come from Driving force when being delivered to output shaft 3) situation illustrate.In Fig. 7, transverse axis represents the time, and the longitudinal axis represents angular speed, shows Relation between the angular velocity omega of 1 swing rod 18 (swinging end 18a) and angular velocity omega _ o of output shaft 3.

As shown in hacures in Fig. 7, angular velocity omega _ o of output shaft 3 region is exceeded in angular velocity omega _ i of swing rod 18, And angular velocity omega _ i of swing rod 18 less than output shaft 3 angular velocity omega _ o after, to one-way clutch 17 torsion (several years Reverse) be released untill region in, driving force is transmitted from input shaft 2 to output shaft 3 via crank and rocker mechanism 20.

Hereinafter, the state that the driving force from input shaft 2 can not be delivered into output shaft 3 of one-way clutch 17 is referred to as " idling conditions " (idling conditions is so-called " disengaged position ").In addition, one-way clutch 17 can will be come from into input shaft 2 Driving force be delivered to the state of output shaft 3 and be referred to as " stationary state " (stationary state is so-called " engagement ").

(boundary line of 2-1. switching states)

Fig. 8 shows the offset R1 with radius of turn governor motion 4 and the output rotary speed Ne of traveling driving source 50 The performance plot of the corresponding vehicle velocity V corresponding to boundary line L.Here, Fig. 8 transverse axis represents offset R1, and the longitudinal axis represents that traveling is used The output rotary speed Ne of driving source 50.

One-way clutch 17 is which of idling conditions and stationary state state are according to vehicle velocity V, offset R1 and row Sail and changed with the output rotary speed Ne of driving source 50.

Line La, Lb, Lc shown in Fig. 8 are borders when one-way clutch 17 changes from idling conditions to stationary state Line.In addition, in each boundary line L (La, Lb, Lc), showing that vehicle velocity V different boundary line L, boundary line L are more in Fig. 8 right side Upside position (according to " and La → Lb → Lc " trend), vehicle velocity V is bigger.

Because, i.e. vehicle velocity V is bigger, and angular velocity omega _ o of output shaft 3 is bigger, and therefore, vehicle velocity V is bigger, unidirectionally from Angular velocity omega _ i of swing rod 18 when clutch 17 changes from from idling conditions to stationary state is bigger.

In addition, (that is, in each boundary line La, Lb, Lc), offset R1 is bigger in the state of vehicle velocity V is constant, it is stepless to become The gear ratio i of fast device 1 is smaller, therefore angular velocity omega _ i of swing rod 18 is bigger.Therefore, when one-way clutch 17 from idling conditions to When stationary state changes, offset R1 is bigger, and traveling is smaller with the output rotary speed Ne of driving source 50.

(3. control)

(summary of 3-1. controls)

Fig. 9 shows to control the power transmission 1A of present embodiment control device 40 and power transmission 1A work( Can block diagram.

First, the summary to control device 40 is illustrated.When control device 40 has skidding determination processing unit 71, skidded Processing unit 74 at the end of traveling is used driving source speed reduction process portion 73 and skidded when radius control process portion 72, skidding, as Main processing unit.

Driving wheel rotary speed Ndrive and the driven pulley rotation that skidding determination processing unit 71 is detected based on control device 40 Rotary speed Ndriven, perform judge be vehicle C the slipping state just skidded of driving wheel 60 or do not skid grab ground state Skidding determination processing.In detail, skidding determination processing unit 71 rotates speed in driving wheel rotary speed Ndrive and driven pulley Degree Ndriven difference is determined as slipping state in the case of more than setting Δ N_threshold, less than setting Δ N_ It is judged to grabbing ground state in the case of threshold.Here, the setting Δ N_threshold passes through the experiment that carries out in advance Deng, be set so as to judge driving wheel 60 be slipping state or grab ground state as value.

In addition, in the present embodiment, control device 40, which by skidding determination processing unit 71 skid, to be judged, but should Control device 40 can not have skidding determination processing unit 71, and be had and skidding determination processing unit 71 by other control device etc. Identical function.In this case or, other control device etc. output represent judgement be slipping state or grab ground state Result signal, control device 40 can the signal based on the output, judgement be slipping state or grab ground state.

Hereinafter, skidding determination processing unit 71 is detected grab ground state state be referred to as " detecting state with grabbing ", detection The state for having arrived slipping state is referred to as " skidding detection state ".

From detect with grabbing state transformation in order to skid detection state when, radius control process portion 72 is controlled during skidding Radius control process during offset R1 skidding so that returned to even in current time and grabbed ground state, one-way clutch 17 Also idling conditions is turned into.

Thus, when from slipping state transformation in order to grab ground state, one-way clutch 17 turns into idling conditions, therefore, it is possible to Reduction acts on the load of one-way clutch 17.

During skidding radius control process portion 72 skid when radius control process in, based on output of the traveling with driving source 50 Rotary speed Ne and vehicle velocity V, control offset R1.Thus, radius control process portion 72 can accurately be controlled partially during skidding Heart amount R1.

Moreover, radius control process portion 72 is more than regulation in the rotary speed No of output shaft 3 reduction amount Δ No when skidding In the case of measuring α, compared with the situation less than ormal weight α, further reduce offset R1.

Thereby, it is possible to prevent situations below in advance：Because the rotary speed No of output shaft 3 reduction amount Δ No compares ormal weight α big (this is for example by operating vehicle C brake apparatus (omit and illustrate) to be produced in that case of slowing down) so that output The rotary speed No of axle 3 is less than the rotary speed for being communicated to the swing rod 18 from the power of traveling driving source 50.Thereby, it is possible to Prevent from acting on larger load to one-way clutch 17.

In addition, traveling is with driving source speed reduction process portion 73 under skidding detection state when skidding, execution uses traveling Traveling uses driving source speed reduction process during the skidding of the output rotary speed Ne reductions of driving source 50.At the same time, as beating Radius control process when sliding, during skidding radius control process portion 72 even in current time returned to grab ground state also will be single In the range of idling conditions being maintained to clutch 17, in response to reduction of the traveling with the output rotary speed Ne of driving source 50, Raise offset R1.

Also, returned to from skidding detection state detect state with grabbing when, processing unit 74 is to cause at the end of skidding One-way clutch 17 turns into the mode of stationary state, performs the skidding knot being controlled to traveling with driving source 50 or offset R1 Handled during beam.

If in the case of the rotary speed No identical of output shaft 3, the output rotary speed Ne of traveling driving source 50 Reduction, then compared with before reduction, one-way clutch 17 from idling conditions be changed into stationary state when offset R1 increase.

That is, skidding when radius control process portion 72 in skidding detection state, grabbed having been returned to even in current time In the range of one-way clutch 17 is also maintained idling conditions by ground state, speed is rotated with the output of driving source 50 in response to traveling Spend Ne reduction, raise offset R1, thus actually returned to grab ground state when, if to traveling with driving source 50 or Offset R1 is controlled, then one-way clutch 17 can be set into stationary state within the shorter time.

(details of 3-2. controls)

10~Figure 12 of reference picture, illustrates the details for the control process that control device 40 is performed.

Figure 10 is the flow chart for showing the control process that control device 40 is performed.

Figure 11 show vehicle C from grab ground state (before moment t1) transformation for slipping state after (time t1~ T4), again return to the time change of each information of vehicles when grabbing ground state (after moment t4) (transverse axis represents the time).In addition, In fig. 11, pay attention to the understandability that is readily appreciated that to be illustrated, therefore schematically show each information of vehicles at each moment Time change.In addition, being changed into grabbing ground state or slipping state rises, to being changed into detecting that state or skidding detection state are with grabbing Only, there are some time differences (such as t1 → moment t2 or moment t4 → moment t6 at the time of Figure 11).

Here, each information of vehicles refers to driving wheel rotary speed Ndrive (solid lines of " vehicle wheel rotational speeds "), driven pulley Rotary speed Ndriven (chain-dotted lines of " vehicle wheel rotational speeds "), traveling driving source 50 output rotary speed Ne, offset R1, swing rod 18 angular velocity omega _ i (solid lines of " angular speed ".Rotary speed to swing rod 18 is multiplied by obtained from " 2 π [rad] " Value), angular velocity omega _ o (chain-dotted lines of " angular speed " of output shaft 3." 2 π [rad] " is multiplied by the rotary speed No of output shaft 3 and Obtained value), the imaginary boundary output shaft angular velocity omega _ bound (dotted lines of " angular speed ".Imaginary boundary output axis angular rate Details will be described later) and vehicle C driving force.

In addition, Figure 12 (each Figure 12 A~12E transverse axis represents that time, the longitudinal axis represent angular speed) is shown shown in Figure 11 " angular velocity omega _ i (solid line) of swing rod 18 ", " angular velocity omega _ o (chain-dotted line) of output shaft 3 " at the time of the regulation of timing diagram And the figure of the relation between " imaginary boundary output shaft angular velocity omega _ bound (dotted line) ".

It is moment t2 in Figure 12 B, when being in fig. 12 c at the time of being before moment t1 in fig. 12 at the time of regulation T3 is carved, is moment t5 in fig. 12d, is moment t7 in fig. 12e.

Here, imaginary boundary output shaft angular velocity omega _ bound, which refers to assume that to have returned at current time, grabs ground state In the case of output shaft 3 angular speed.In addition, imaginary boundary output shaft angular velocity omega _ bound is not deposited when grabbing ground state , therefore (being only time t1~t4, in fig. 12 only 12B and 12C in fig. 11) is only shown in slipping state.

Here, imaginary boundary output shaft angular velocity omega _ bound is to " assume that to have returned at current time and grab ground shape The rotary speed No " of output shaft 3 in the case of state is multiplied by value obtained from " 2 π [rad] ", wherein, " it assume that current It is by " driven pulley rotary speed that moment, which has returned to the rotary speed No " of output shaft 3 grabbed in the case of ground state, Ndriven (represents actual vehicle C translational speed V rotary speed.That is, returned at current time grab ground state when Driving wheel rotary speed Ndrive) " and " gear ratio between output shaft 3 and driving wheel 60 " obtained from.That is, imaginary boundary The maximum angular speed that output shaft angular velocity omega _ bound is expressed as follows：Under skidding detection state, returned even in current time Return to and grabbed ground state, one-way clutch 17 is turned into idling conditions.

Therefore, control device 40 is under skidding detection state, as long as defeated in imaginary boundary with angular velocity omega _ i of swing rod 18 Shaft angular velocity omega _ below bound mode controls offset R1, then has been returned to even in current time and grabbed ground state, One-way clutch 17 can be set to idling conditions.

In addition, strictly speaking, although generate driving wheel rotary speed within moment t4 to moment t5 extremely short period Ndrive change, but when state " returned at current time grab ground " is to represent moment t5 (that is, at the end of transition state Carve).

In addition, strictly speaking, after angular velocity omega _ os of the angular velocity omega _ i less than output shaft 3 of swing rod 18, to unidirectionally from The torsion (torsions in several years) of clutch 17 be released untill in a period of, one-way clutch 17 be stationary state.Therefore, although When one-way clutch 17 changes from stationary state to idling conditions, once with cause swing rod 18 angular velocity omega _ i be in than imagination The low modes for being used to discharge the region of the angular speed of above-mentioned torsion of border output shaft angular velocity omega _ bound, are carried out to offset R1 Control, but " in the way of angular velocity omega _ i of swing rod 18 is in imaginary boundary output shaft angular velocity omega _ below bound, to offset R is controlled " also comprising such control.In addition, when one-way clutch 17 is in idling conditions, above-mentioned torsion is not produced Turn, therefore in the way of causing angular velocity omega _ i of swing rod 18 in imaginary boundary output shaft angular velocity omega _ below bound, to inclined Heart amount R1 is controlled.

Control device 40 controls offset R1 equivalent in the present invention " being skidding shape from being not detected by as described above When to detect state transformation with grabbing in order to detect be that the skidding of slipping state detects state of state, controls the radius of turn, makes Even in current time return to the driving wheel it is non-slip grab ground state, the single direction rotation prevents mechanism from also turning into The idling conditions ".

Hereinafter, reference picture 10, illustrate the control process that control device 40 is performed.Control device 40 every the defined cycle, Perform the flow chart shown in Figure 10.First, control device 40 performs in initial step ST1 and is based on driving wheel rotary speed Ndrive and driven pulley rotary speed Ndriven skidding determination processing, judgement are slipping state or grab ground state.Here, The processing performed in step ST1 is equivalent to the skidding determination processing performed by skidding determination processing unit 71.

(such as t2 is such at the time of Figure 11, in driving wheel when control device 40 is judged in step ST1 for slipping state When rotary speed Ndrive and driven pulley rotary speed Ndriven difference are larger), into step ST2, perform fuel-cut and (beat Traveling uses driving source speed reduction process when sliding), and forbid upshift (that is, the processing for increasing offset R1).By so Fuel-cut is carried out, after the time t 2, the output rotary speed Ne of traveling driving source 50 can be reduced.

Control device 40 is in following step ST3, by the way that traveling is removed with the output rotary speed Ne of driving source 50 With driven pulley rotary speed Ndriven, effective rate R_act is calculated.Effective rate R_act is represented under slipping state, by row Sail with the output rotary speed Ne of driving source 50 divided by " assuming that having returned to the drive grabbed in the case of ground state at current time Ratio (gear ratio) obtained from driving wheel rotary speed Ndrive ".

Control device 40 in following step ST4, based on traveling with the output rotary speed Ne of driving source 50 and from Driving wheel rotary speed Ndriven, determines border ratio R _ bound.Here, border ratio R _ bound refers under slipping state, Assuming that returned at current time grab ground state in the case of, switching stationary state and idling conditions border ratio. That is, border ratio R _ bound refers to the (reference on boundary line L corresponding with driven pulley rotary speed Ndriven (or vehicle velocity V) Fig. 8), offset R1 corresponding with the output rotary speed Ne of traveling driving source 50 gear ratio is corresponded to.

Here, in the case of effective rate R_act and border ratio R _ bound identicals, be swing rod 18 angular velocity omega _ I and imaginary boundary output shaft angular velocity omega _ bound identical situations.That is, when in slipping state, if border ratio R _ Bound be more than effective rate R_act, then returned at current time grab ground state when, angular velocity omega _ i of swing rod 18 exceedes Imaginary boundary output shaft angular velocity omega _ bound, one-way clutch 17 turns into stationary state.It is thereby possible to be hindered to single direction rotation Locking mechanism drastically acts on larger load.

Therefore, when in slipping state, with border ratio R _ bound by way of below effective rate R_act, Control offset R1 (and then, control border ratio R _ bound), thus returned to even in current time and grabbed ground state, One-way clutch 17 can be set to idling conditions.

Control device 40 in following step ST5, judge effective rate R_act whether be less than border ratio R _ bound。

Control device 40 be determined as in step ST5 " in the case of effective rate R_act ＜ borders ratio R _ bound ", Into step ST6, according to rule when skidding, the target offset R1_cmd of offset R1 desired value is determined as.In detail Ground says, control device 40 will have been returned to even in current time grabs ground state, one-way clutch 17 and be also able to maintain that idle running shape Offset R1 as state is defined as target offset R1_cmd.That is, control device 40 will cause angular velocity omega _ i of swing rod 18 It is defined as target offset R1_cmd in imaginary boundary output shaft angular velocity omega _ below bound offset R1.

In the present embodiment, it is fast in order to export shaft angle with imaginary boundary substantially by the angular velocity omega of swing rod 18 _ i settings Spend ω _ bound identical values.Therefore, the situation that control device 40 is reduced in traveling with the output rotary speed Ne of driving source 50 Under, grab in the range of one-way clutch 17 also to maintain to ground state idling conditions, ring having been returned to even in current time Increase in the output rotary speed Ne of traveling driving source 50 reduction offset R1.In addition, in above-mentioned steps ST2 Prohibit upshift (that is, offset R1 increase), but the increase of the offset R1 caused by the processing is not object that this is forbidden.

Control device 40 is in following step ST7, and whether the rotary speed No of judgement output shaft 3 reduction amount Δ No Ormal weight α is exceeded.Control device 40 is determined as in step ST7 " in the case of reduction amount Δ No ＞ ormal weights α ", into step Rapid ST8, according to reduction amount Δ No, reduces the target offset R1_cmd determined in step ST6.

Control device 40 is determined as in step ST7 " in the case of reduction amount Δ No≤ormal weight α ", or step ST8 Processing terminated in the case of, into step ST9, the target determined in step ST6 or step ST8 is turned into offset R1 Offset R1_cmd mode, controls to adjust and uses driving source 14.

So, offset R1 is controlled in step ST9 in the way of as target offset R1_cmd, therefore from skidding shape State transformation is in order to grab during ground state, and one-way clutch 17 turns into idling conditions, wherein, the target offset R1_cmd is with i.e. Make to have returned at current time grab ground state, one-way clutch 17 be also able to maintain that the mode of idling conditions and in step ST6 Middle setting.Therefore, it is possible to reduce the load for acting on one-way clutch 17.

Here, " (that is, to be returned to as the target offset R1_cmd determined in step ST6 even in current time Grab ground state, it is also possible that one-way clutch 17 maintains offset R1 as idling conditions) mode come in step ST9 Middle control offset R1 " equivalent to by above-mentioned skidding when radius control process portion 72 perform skidding when radius control process.

In addition, be determined as in step ST7 " in the case of reduction amount Δ No ＞ ormal weights α ", in step ST8, according to Reduction amount Δ No, reduces the target offset R1_cmd determined in step ST6.Thus, in step ST9, to subtract as this The mode of target offset R1_cmd after small, controls offset R1 in step ST9.

Thus, for example in that case of slowing down, also can even in operation vehicle C brake apparatus (omitting diagram) The rotary speed No of output shaft 3 is prevented to be less than the rotation speed for being communicated to the swing rod 18 from the power of traveling driving source 50 in advance The situation of degree.Thereby, it is possible to prevent from acting on larger load to one-way clutch 17.

Here, when step ST8 is performed after step ST7 judgement and step ST9 processing is performed equivalent to above-mentioned skidding It is radius control process portion 72, " and small in the case where the rotary speed No of output shaft 3 reduction amount Δ No is more than ormal weight α Compared in ormal weight α situation, further reduce offset R1 " processing.

Control device 40 be determined as in step ST5 " in the case of effective rate R_act≤border ratio R _ bound ", Or after step ST9 processing terminates, into step ST10.Control device 40 is in step ST10, in the same manner as step ST1 Determine whether slipping state.Here, the processing performed in step ST10 is performed equivalent to by skidding determination processing unit 71 Skidding determination processing.

In the case that control device 40 is judged to being slipping state in step ST10, return to step ST3.

Control device 40 is determined as it being that when grabbing ground state, (such as t6 like that, is driving at the time of Figure 11 in step ST10 When wheel rotary speed Ndrive and driven pulley rotary speed Ndriven difference is smaller), into step ST11, fuel-cut is released, And release and forbid upshift.

Control device 40 is in following step ST12, for target offset R1_cmd, with one-way clutch 17 into For the mode of stationary state, target offset R1_cmd is determined.In detail, control device 40 is at least at one-way clutch 17 During idling conditions, in the way of the offset R1 more than current time, target offset R1_cmd is determined.

Control device 40 turns into the target determined in step ST12 with offset R1 inclined in following step ST13 Heart amount R1_cmd mode, controls to adjust and uses driving source 14.

In step ST6, control device 40 in the case where traveling is with the output rotary speed Ne of driving source 50 reduction, Return to and grabbed in the range of one-way clutch 17 also to maintain to ground state idling conditions even in current time, in response to row The reduction of the output rotary speed Ne with driving source 50 is sailed, increases offset R1.Thus, so that offset in step ST13 When the mode of R1 increases is controlled to adjust with driving source 14, (for example in fig. 11, it can be and then moment in shorter time After t6) in, one-way clutch 17 is set to stationary state.

Here, to " one-way clutch 17 is from idling conditions " when in order to grab detecting state from the transformation of skidding detection state " When transformation is for stationary state " untill in a period of, step ST12~ST13 processing equivalent to skidding at the end of handle.

In addition, in step ST12, ST13 handled at the end of as skidding, being controlled offset R1, but beat Processing can also be following processing at the end of cunning：The output rotary speed Ne of traveling driving source 50 is controlled, by one-way clutch 17 are set to stationary state from idling conditions.

In the case that control device 40 is judged to being slipping state in step ST1, or in step ST13 processing knot Shu Hou, terminates this flow chart.

Then, reference picture 11, caused by the control process as illustrating above shown in the execution of control device 40 Figure 10, The time change of each information of vehicles.

When moment t1 becomes for slipping state, due to reasons such as load reductions, traveling is rotated with the output of driving source 50 Speed Ne and driving wheel rotary speed Ndrive increases.And now, due to being skidded, vehicle C driving force is 0.

Then, in moment t2, control device 40 turn into skidding detection state, by performing step ST2, moment t2 it Afterwards, traveling is gradually reduced with the output rotary speed Ne of driving source 50.And now, for driving wheel rotary speed Ndrive, In step ST6~ST9, offset R1 is controlled by way of turning into idling conditions with one-way clutch 17, as not from row Sail and be passed driving force with driving source 50 and leaned on inertia state of rotation.Therefore, driving wheel rotary speed Ndrive when It is gradually reduced after quarter t2.

In moment t3, the output rotary speed Ne of traveling driving source 50 reduces, thus with the reduction, even if Return to and grabbed in the range of one-way clutch 17 also maintains idling conditions by ground state at current time, used in response to traveling The output rotary speed Ne of driving source 50 reduction, offset R1 increases.

Then, it is short-term interior untill moment t5 after moment t4 is changed into grabbing ground state, driving wheel rotary speed Ndrive is strongly reduced untill driven pulley rotary speed Ndriven.

Then, turn into moment t6 and detect state with grabbing, in the way of one-way clutch 17 turns into stationary state, make bias Measure R1 increases.In addition, even in current time returned to grab ground state one-way clutch 17 is also maintained into idling conditions In the range of, in response to reduction of the traveling with the output rotary speed Ne of driving source 50, increase offset R1, thus and then After moment t6, one-way clutch 17 turns into stationary state, and vehicle C driving force gradually increases from 0, untill moment t7, The transport condition that can smoothly return to before being changed into slipping state.

(4. variation)

In the present embodiment, radius control process portion 72 (step ST7, ST8) is being exported during the skidding of control device 40 In the case that the rotary speed No of axle 3 reduction amount Δ No is more than ormal weight α, compared with the situation less than ormal weight α, further Reduce offset R1, but not limited to this.For example, it is also possible to control device is configured to, in the rotary speed No of output shaft 3 Reduction amount Δ No time variation amount d Δs No/dt be more than ormal weight α 2 in the case of, with the situation phase less than ormal weight α 2 Than further reducing offset R1.And at this time it is also possible to without using the rotary speed No of output shaft 3, and revolved using driven pulley Rotary speed Ndriven (that is, the time variation amount of its reduction amount or the reduction amount).

In this case, for example even in by operating vehicle C brake apparatus (omit and illustrate) come such situation of slowing down Under, it can also prevent the rotary speed No of output shaft 3 to be less than the swing rod for being communicated to the power from traveling driving source 50 in advance The situation of 18 rotary speed, and then obtain effect from larger load to one-way clutch 17 that can prevent from acting on.

In addition, in the present embodiment, the angular velocity omega of swing rod 18 _ i settings is fast in order to export shaft angle with imaginary boundary Angular velocity omega _ i of swing rod 18, can also be set as more defeated than imaginary boundary by degree ω _ bound identical values, but not limited to this The value of shaft angular velocity omega _ low bound.In this case, in Figure 11 and Figure 12, angular velocity omega _ i of swing rod 18 is located at imaginary side Under boundary's output shaft angular velocity omega _ bound.

In addition it is also possible to control device is configured to, not according to the rotary speed No of output shaft 3 reduction amount Δ No or Relation between reduction amount Δ No time variation amount d Δs No/dt and ormal weight α controls offset R1.In this case, omitting The processing of Figure 10 step ST7, ST8.

In addition, in the present embodiment, control device 40 is constituted in skidding detection state, to perform row when skidding Sail and use driving source speed reduction process, and grabbed when skidding in radius control process having been returned to even in current time In the range of one-way clutch 17 is also maintained idling conditions by ground state, speed is rotated with the output of driving source 50 in response to traveling Ne reduction is spent, offset R1 is increased (step ST6), but it is also possible to which control device is configured to when skidding at radius control In reason, the control without the corresponding offset R1 of the reduction of the output rotary speed Ne with traveling driving source 50 (makes above-mentioned The control of offset R1 increases).

In addition, in the present embodiment, control device 40 is when skidding in radius control process, based on traveling driving source 50 output rotary speed Ne and vehicle velocity V, control offset R1.But, vehicle velocity V now can be not based on driven pulley rotation speed Degree Ndriven is obtained, and uses value obtained from the actual translational speed of estimation vehicle.For example, as vehicle velocity V, can be based on GPS (the Global Positioning System installed by vehicle：Global positioning system) the obtained shifting of vehicle of receiver The acceleration of dynamic information and the vehicle obtained by the acceleration transducer that vehicle is installed, estimates the translational speed of vehicle and obtains Arrive.

In addition, in the present embodiment, having used one-way clutch 17 as single direction rotation and having prevented mechanism, still, this hair Bright single direction rotation prevents mechanism not limited to this, can also be from being configured to transmit moment of torsion and energy from swing rod 18 to output shaft 3 Enough free switching swing rods 18 are constituted relative to the bidirectional clutch (Two-way clutch) of the direction of rotation of output shaft 3.

In addition, in the present embodiment, illustrating with the cam disc 5, the rotation of rotating disk 6 rotated integrally with input shaft 2 Turn radius governor motion 4, still, the not limited to this of radius of turn governor motion 4 of the invention.For example, it is also possible to by following part Constitute radius of turn governor motion：With the discoid rotating disk for prejudicially running through the through hole set from center；It is disposed through The gear ring of the inner peripheral surface in hole；The 1st little gear for being fixed on input shaft and being engaged with gear ring；Transmit the drive to be self-regulated with driving source The planet carrier of power；Two the 2nd little gears, they respectively by can free rotation and revolution in the way of be supported on the shaft on planet carrier, And engaged respectively with gear ring.

Label declaration

1A：Power transmission；C：Vehicle；2：Input shaft (input unit)；3：Output shaft；4：Radius of turn governor motion； 14：Regulation driving source；15：Connecting rod；17：One-way clutch (single direction rotation prevention mechanism)；18：Swing rod；20：Crank rocker machine Structure；40：Control device；50：Traveling driving source；60：Driving wheel；61：Driven pulley；i：Gear ratio；No：The rotation of output shaft 3 Speed；Ne：The output rotary speed of traveling driving source 50；V：Speed (translational speed of vehicle)；ΔNo：Reduction amount；dΔ No/dt：Reduction amount Δ No time variation amount；α：Ormal weight.

Claims (4)

1. a kind of power transmission, it has：

Input unit, it is passed the driving force of the traveling driving source of vehicle；

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

Crank and rocker mechanism, it has the swing rod being supported on the shaft on the output shaft, the rotation of the input unit is converted to described The swing of swing rod；And

Single direction rotation prevents mechanism, and it can switch between idling conditions and stationary state, wherein, the idling conditions refers to The swing rod is relative to the state that the output shaft dallies, the fixation when being rotated against relative to the axial side of the output The swing rod is fixed on the shape on the output shaft when state refers to rotate against relative to the axial opposite side of the output State,

The crank and rocker mechanism has：Regulation driving source；Radius of turn governor motion, it can be driven by the regulation The driving force in dynamic source freely adjusts radius of turn when being pivoted about with the center of rotation axis；And connecting rod, its It is coupled the radius of turn governor motion and the swing rod,

The power transmission can change speed change by changing the radius of turn of the radius of turn governor motion Than, according to the radius of turn, make the driving force speed change of the traveling driving source and be transferred to the driving wheel of the vehicle,

The power transmission is characterised by,

With control device, in the slipping state skidded in the driving wheel, the control device is controlled the rotation Turn radius control process during the skidding of radius so that even in current time return to the driving wheel grab ground grab ground state, The single direction rotation prevents mechanism from also turning into the idling conditions.

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

In slipping state, the control device is performed when making the skidding that the output rotary speed of the traveling driving source is reduced Traveling uses driving source speed reduction process, and is returned in the skidding in radius control process even in current time To grabbing in the range of single direction rotation prevention mechanism also maintains the idling conditions by ground state, in response to the traveling Increase the radius of turn with the reduction of the output rotary speed of driving source,

Returned to from slipping state grab ground state when, the control device performs the control traveling driving source or described Handled at the end of the skidding of radius of turn so that the single direction rotation prevents mechanism from turning into the stationary state.

3. power transmission according to claim 1, it is characterised in that

The control device in the skidding in radius control process, the rotary speed of the output shaft reduction amount or subtract In the case that a small amount of time variation amounts is more than defined measure, compared with less than the situation of the defined amount, further reduce The radius of turn.

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

The control device is in the skidding in radius control process, the output rotary speed based on the traveling driving source With the translational speed of the vehicle, the radius of turn is controlled.