CN104930152A

CN104930152A - Continuously variable transmission

Info

Publication number: CN104930152A
Application number: CN201510125668.3A
Authority: CN
Inventors: 西村优史
Original assignee: Honda Motor Co Ltd
Current assignee: Honda Motor Co Ltd
Priority date: 2014-03-20
Filing date: 2015-03-20
Publication date: 2015-09-23
Anticipated expiration: 2035-03-20
Also published as: CN104930152B; JP2015183728A; JP6163124B2

Abstract

The invention provides a continuously variable transmission provided with a distance detection part (50) fixed on a transmission shell (30) and detecting the distance to a to-be-detected part; and an output shaft torque calculating control part (52) calculating the torque of the output shaft (23) based on the value detected by the distance detection part (50). The output shaft torque calculating control part (52) is provided with a peak value storage part (53) storing a peak value of values detected by the distance detection part (50) successively at a specific sequence; and input side period detecting part detecting one spinning period of the input shaft (2); an output side period detecting part (55) detecting one spinning period of the output shaft (23); an average value calculating part (56) calculating the average value of peak value of the stored specified times; and an output shaft torque calculating part (57) calculating torque of the output shaft (23) according to the average value.

Description

Stepless speed variator

Technical field

The present invention relates to stepless speed variator.

Background technique

Such as, a kind of control gear of stepless speed variator of four joint linkage mechanism types is described in Japanese Unexamined Patent Publication 2012-251608 publication, the rotation of the input shaft be connected with motor is converted to the to-and-fro motion of connecting rod by described stepless speed variator, and utilizes overrunning clutch that the to-and-fro motion of connecting rod is converted to the rotary motion of output shaft.

In the control gear of Japanese Unexamined Patent Publication 2012-251608 publication, disclose following content: the accumulative rotating cycle of input part and the accumulative rotating cycle of pinion shaft are counted, and utilize their difference to calculate the turning radius of turning radius controlling mechanism, based on this turning radius, the moment of torsion being passed to input shaft or output shaft is calculated.

When calculating the method for I/O moment of torsion calculate offset R1 based on the rotating speed of input side as Japanese Unexamined Patent Publication 2012-251608 publication after, due to the gap between the backlash of small gear and eccentric disc internal tooth, input shaft parts, input shaft flexure etc. and correct offset R1 cannot be extrapolated, the precision of the output torque consequently calculated also can reduce.

In addition, when the overrunning clutch engaging of Japanese Unexamined Patent Publication 2012-251608 publication, there is dependency relation between its displacement amount and transmitting torque of overrunning clutch in exterior part expander.Can consider such method: according to this dependency relation, use the equidistant detection unit of gap sensor to detect displacement amount, estimation transmitting torque also feeds back in gear ratio control.

Distance detection unit 50 to be configured near exterior part 18 and the figure of the measurement example of the relation between the time variations of the angle of oscillation of exterior part 18 and detecting distance (clearance) is shown by Fig. 6 A.Fig. 6 B is the figure compared the situation of overrunning clutch to be non-loaded situation and overrunning clutch be engagement.Compared with no-load condition, under engagement, by making roller 25 be fastened between output shaft 23 and exterior part 18, thus, exterior part 18 is pressed by radial direction, and exterior part 18 is shifted in the mode expanded along radial direction.According to such characteristic, show such trend: compared with the displacement (gap) when transmitting low moment of torsion with overrunning clutch, the displacement (gap) when transmitting high moment of torsion becomes large (Fig. 6 A).

In addition, because the roller 25 of overrunning clutch configures discretely along the circumferencial direction of output shaft 23, therefore, even if when transmitting same moment of torsion, the output value of the displacement detected is different according to distance detection unit and the relative position relation of roller.

Fig. 7 A shows the state that roller 25 configures relative to the detection faces of distance detection unit 50 with staggering, and Fig. 7 B shows roller 25 and is configured in apart from the state immediately below detection unit 50.Show such trend: compared with the situation (Fig. 7 A) configured with staggering relative to detection faces with roller 25, roller 25 displacement (gap) be configured in the situation (Fig. 7 B) immediately below detection faces becomes large.

Summary of the invention

The present invention completes in view of above-mentioned problem, its object is to provide a kind of stepless speed variator, its revolution (サイ Network Le number) being averaged the peak value to distance detection unit is consistent with the position relationship of roller by employing and obtaining, can calculate output shaft torque based on the displacement measurement reducing deviation.

The stepless speed variator of the 1st aspect of the present invention possesses: input shaft 2, and it is used driving source transmission of drive force by from traveling; Output shaft 23, it has the rotating center axis with the rotating center axis being parallel of described input shaft 2; Turning radius controlling mechanism 4 ~ 7, it can regulate turning radius freely, can rotate centered by the rotating center axis of described input shaft 2; Crankrocker mechanism 20, it has the exterior part 18 linked with described output shaft 23 and the connecting rod 15 linking described turning radius controlling mechanism 4 ~ 7 and described exterior part 18, and the rotary motion of described turning radius controlling mechanism 4 ~ 7 is converted to the oscillating motion of described exterior part 18; Single direction rotation stops mechanism 17, and described exterior part 18 is fixed on described output shaft 23 when described exterior part 18 is for swinging aside by it, and when described exterior part 18 is for swinging to opposite side, described exterior part 18 is dallied relative to described output shaft 23; And case of transmission 30, it receives described crankrocker mechanism 20 and described single direction rotation stops mechanism 17, described single direction rotation stops mechanism 17 to be following such overrunning clutchs, and this overrunning clutch possesses: described output shaft 23, and it is configured in the inner circumferential of described exterior part 18 coaxially; Multiple roller 25, between its inner peripheral surface being configured in described exterior part 18 and the outer circumferential face of described output shaft 23; And multiple force application part 26, it along the circumferential direction exerts a force to described multiple roller 25 and rotates integratedly with described output shaft 23, this overrunning clutch is by the relative rotation towards described side of described exterior part 18 with described output shaft 23, described roller 25 is fastened between the inner peripheral surface of described exterior part 18 and the outer circumferential face of described output shaft 23 and carrys out transmission of drive force, described exterior part 18 has: swing end 18a, itself and described connecting rod 15 link; With annulus 18d, itself and described output shaft 23 link and possess detected portion, and the feature of described stepless speed variator is, described stepless speed variator possesses: distance detection unit 50, they are fixed on described case of transmission 30, detect the distance to described detected portion; Control device 52 is calculated with output shaft torque, it calculates the moment of torsion of described output shaft 23 based on the value detected by described distance detection unit 50, described output shaft torque calculates control device 52 to be possessed: peak value memory section 53, and it stores the peak value of the value detected by described distance detection unit 50 successively with the number of times of regulation; Input side cycle detection portion 54, it detects 1 period of rotation of described input shaft 2; Outlet side cycle detection portion 55, it detects 1 period of rotation of described output shaft 23; Mean value calculation portion 56, it calculates the mean value of the peak value of the stipulated number of described storage; And output shaft torque calculating part 57, the moment of torsion of its output shaft 23 according to described mean value calculation, the number of times of described regulation is made up of following such number of times: this number of times be using the position relationship of the described distance detection unit 50 during described peak value memory section 53 original stored peak value and described roller 25 as the 1st state time, to when becoming the 2nd state with the described position relationship identical with described 1st state, the number of times that described peak value is stored.

In addition, according to the 2nd aspect of stepless speed variator of the present invention, it is characterized in that, the number of times of described regulation is made up of following such number of times: this number of times be when becoming with described 1st state identical described 2nd state to the roller configured immediately preceding the described roller 25 under described 1st state below, the number of times that described peak value is stored.

In addition, according to the 3rd aspect of stepless speed variator of the present invention, it is characterized in that, the number of times of described regulation is made up of following such number of times: this number of times is before described output shaft 23 rotates 1 circle, when becoming described 2nd state identical with described 1st state to other any roller different from the described roller 25 under described 1st state, the number of times that described peak value is stored.

In addition, according to the 4th aspect of stepless speed variator of the present invention, it is characterized in that, the number of times of described regulation becomes number of times same roller to the roller 25 of described 1st state and the roller 25 of described 2nd state.

In addition, according to the 5th aspect of stepless speed variator of the present invention, it is characterized in that, the number of times of described regulation is the number of times to the rotatable phase of the described input shaft when rotatable phase of described input shaft during described 1st state and described 2nd state becomes identical phase place.

In addition, according to the 6th aspect of stepless speed variator of the present invention, it is characterized in that, the number of times of described regulation calculates according to the quantity of 1 period of rotation/described multiple roller 25 of 1 period of rotation/described input shaft 2 of described output shaft 23.

In addition, according to the 7th aspect of stepless speed variator of the present invention, it is characterized in that, the number of times of described regulation calculates according to 1 period of rotation of 1 period of rotation/described input shaft 2 of described output shaft 23.

In addition, according to the 8th aspect of stepless speed variator of the present invention, it is characterized in that, the number of times of described regulation calculates according to 1 period of rotation of the least common multiple/described input shaft 2 of 1 period of rotation of described input shaft 2 and 1 period of rotation of described output shaft 23.

In addition, according to the 9th aspect of stepless speed variator of the present invention, it is characterized in that, described stepless speed variator also possesses: output shaft speed detection unit 58, and its testing result based on described outlet side cycle detection portion 55 judges the rotating speed of described output shaft 23; With stipulated number configuration part 59, it sets the computational methods of the number of times of described regulation based on described judgement, and described mean value calculation portion 56 calculates the number of times of described regulation according to the computational methods of described setting.

According to the structure of the 1st aspect to the 3rd aspect, by adopting, the peak value to consistent with the position relationship of roller apart from detection unit being averaged and the revolution that obtains, output shaft torque can being calculated based on the displacement measurement reducing deviation.

In addition, according to the structure of the 4th aspect, on the basis of the effect in the 1st, the deviation of the checkout value of the distance detection unit caused by the deviation of the roll shape of each roller can be eliminated, and calculate output shaft torque.

In addition, according to the structure of the 5th aspect, on the basis of the effect in the 4th, the deviation of the checkout value of the distance detection unit caused by the deviation of the outer shape of exterior part can be eliminated, and calculate output shaft torque.

In addition, according to the structure of the 6th aspect, on the basis of the effect in the 3rd in the 1st, the number of times of the regulation to distance detection unit is consistent with the position relationship of roller can be calculated.

In addition, according to the structure of the 7th aspect, on the basis of the effect in the 4th, can calculate about same roller, the number of times of regulation to distance detection unit and the relative position relation between roller become identical state.

In addition, according to the structure of the 8th aspect, on the basis of the effect in the 5th, can calculate about same roller, to the position consistency of roller and the phase place of exterior part consistent the number of times of regulation.

In addition, according to the structure of the 9th aspect, on the basis of the effect in the 6th, according to the computational methods of the stipulated number corresponding with the rotating speed of output shaft, the mean value of the checkout value of distance detection unit can be obtained.

Accompanying drawing explanation

Fig. 1 is the sectional view of the structure of the stepless speed variator that present embodiment is shown.

Fig. 2 is the figure of the offset controlling mechanism of stepless speed variator from end on observation Fig. 1, connecting rod and swing arm.

Fig. 3 A-Fig. 3 D is the figure of the change that the offset determined by the offset controlling mechanism of the stepless speed variator of Fig. 1 is shown.

Fig. 4 A-Fig. 4 C is the figure that the relation between the change of offset and the pendulum angle scope of the oscillating motion of swing arm determined by the offset controlling mechanism of present embodiment is shown.

Fig. 5 A is the figure that the functional structure calculating control device to output shaft torque is described.

Fig. 5 B-A ~ Fig. 5 B-D is the figure be described the detection of the relative position relation between the distance detection unit of the 1st mode of execution and roller and peak value.

Fig. 6 A carries out illustrative figure to the relation between the time variations of the angle of oscillation of exterior part and displacement (gap),

Fig. 6 B is the figure compared the situation of overrunning clutch to be non-loaded situation and overrunning clutch be engagement.

Fig. 7 A is the figure that the state that roller configures relative to distance detection unit with staggering is shown.

Fig. 7 B illustrates that roller is configured in the figure of the state immediately below distance detection unit.

Fig. 8 is the figure be described the structure in input side cycle detection portion and outlet side cycle detection portion.

Fig. 9 is the figure that the process calculating control device to the output shaft torque of the 1st mode of execution is described.

Figure 10 is the figure of the example of the group that the 1st mode of execution is shown.

Figure 11 A is the figure that the flow process of the computing of output torque to output shaft is described.

Figure 11 B is the figure that citing illustrates the dependency relation of gap value and output torque.

Figure 12 A-Figure 12 D is the figure be described the detection of the relative position relation between the distance detection unit of the 2nd mode of execution and roller and peak value.

Figure 13 A-Figure 13 B be citing the deviation of roller and the output of distance detection unit is shown change between the figure of relation.

Figure 14 is the figure that the process calculating control device to the output shaft torque of the 2nd mode of execution is described.

Figure 15 is the figure of the example of the group that the 2nd mode of execution is shown.

Figure 16 A-Figure 16 D is the figure be described the detection of the relative position relation between the distance detection unit of the 3rd mode of execution and roller and peak value.

Figure 17 is the figure of the example of the peak value that the 3rd mode of execution is shown.

Figure 18 is the figure that the process calculating control device to the output shaft torque of the 3rd mode of execution is described.

Figure 19 is the figure that the functional structure calculating control device to the output shaft torque of the 4th mode of execution is described.

Embodiment

Below, the mode illustrated to illustrate is described in detail to embodiments of the present invention.But the constituting component recorded in the present embodiment just illustrates, and technical scope of the present invention is determined by claims, does not limit by following single mode of execution.

The structure > of < stepless speed variator

First, see figures.1.and.2 and the structure of the stepless speed variator of present embodiment is described.The stepless speed variator 1 of present embodiment gear ratio i (rotating speed of the rotating speed/output shaft of i=input shaft) can be made to be infinitely great (∞) thus makes the rotating speed of output shaft be the one of speed changer, the i.e. so-called IVT (Infinity VariableTransmission) of " 0 ".

The stepless speed variator 1 of present embodiment possesses input shaft 2, output shaft 23 and 6 offset controlling mechanisms 4.

Input shaft 2 is made up of the parts of hollow, and it is subject to the driving force from the traveling such as motor or motor driving source and is driven in rotation centered by rotating center axis P1.

Output shaft 23 and input shaft 2 are configured in the position be separated with input shaft 2 in the horizontal direction abreast, and transfer a driving force to the axletree of Motor Vehicle via differential gear etc.

Offset controlling mechanism 4 is driving force input part respectively, and is configured to rotate centered by the rotating center axis P1 of input shaft 2, and offset controlling mechanism 4 has the cam disk 5 as cam part, the eccentric disc 6 as eccentric part and pinion shaft 7.Turning radius controlling mechanism (4 ~ 7) can regulate turning radius freely, and is configured to rotate centered by the rotating center axis of input shaft 2.

Cam disk 5 is disc-shapes, and it is with eccentric and be arranged at input shaft 2 with becoming 1 group with the mode 2 that input shaft 2 rotates integratedly from the rotating center axis P1 of input shaft 2.Every 1 group of cam disk 5 is set to respectively and makes phase shifting 60 °, and be configured to 6 groups of cam disks 5 in the circumference of input shaft 2 around a circle.

Eccentric disc 6 is disc-shapes, is being provided with reception hole 6a from the position of its center P3 bias, and 1 group of cam disk 5 is supported to clip this reception hole 6a in the mode that can rotate.

The center of the reception hole 6a of eccentric disc 6 is formed as: identical to the distance Rb of the center P3 of eccentric disc 6 with the center P2 from cam disk 5 to the distance Ra of the center P2 (center of reception hole 6a) of cam disk 5 from the rotating center axis P1 of input shaft 2.In addition, the inner peripheral surface clipped by 1 group of cam disk 5 of the reception hole 6a of eccentric disc 6 is formed with internal tooth 6b.

Pinion shaft 7 and input shaft 2 are configured in the hollow portion of input shaft 2 with one heart, and are supported on the inner peripheral surface of input shaft 2 in the mode that can relatively rotate via pinion bearing 7b.In addition, the outer circumferential face of pinion shaft 7 is provided with external tooth 7a.And then, pinion shaft 7 is connected with differential attachment 8.

Between 1 group of cam disk 5 on input shaft 2, and be formed with the cut hole 2a making inner peripheral surface be communicated with outer circumferential face at the position opposed with the eccentric direction of cam disk 5, the external tooth 7a of pinion shaft 7 engages with the internal tooth 6b of the reception hole 6a of eccentric disc 6 via this cut hole 2a.

Differential attachment 8 is planetary gears, and it has: sun gear 9; The 1st gear ring 10 linked with input shaft 2; The 2nd gear ring 11 linked with pinion shaft 7; With planet carrier 13, band ladder small gear 12 axle is supported to by it can rotation and revolution, and described band ladder small gear 12 is made up of the large-diameter portion 12a engaged with sun gear 9 and the 1st gear ring 10 and the minor diameter part 12b that engages with the 2nd gear ring 11.In addition, the running shaft 14a in eccentric drive portion 14 (offset adjustment driving source) that the sun gear 9 of differential attachment 8 is formed with the motor driven by pinion shaft 7 links.

And, when making the rotating speed in this eccentric drive portion 14 identical with the rotating speed of input shaft 2, sun gear 9 and the 1st gear ring 10 rotate with same speed, sun gear 9, the 1st gear ring 10, these 4 components of the 2nd gear ring 11 and planet carrier 13 become the lock state that can not relatively rotate, and the pinion shaft 7 and the input shaft 2 that link with the 2nd gear ring 11 rotate with same speed.

In addition, when the rotating speed of the rotating ratio input shaft 2 making eccentric drive portion 14 is slow, if set the rotating speed of sun gear 9 as Ns, if the rotating speed of the 1st gear ring 10 is NR1, if the velocity ratio of sun gear 9 and the 1st gear ring 10 (number of teeth of the number of teeth/sun gear 9 of the 1st gear ring 10) is j, then the rotating speed of planet carrier 13 is (jNR1+Ns)/(j+1).In addition, if set the velocity ratio of sun gear 9 and the 2nd gear ring 11 ((number of teeth of the number of teeth/sun gear 9 of the 2nd gear ring 11) × (being with the number of teeth of the number of teeth/minor diameter part 12b of the large-diameter portion 12a of ladder small gear 12)) as k, then the rotating speed of the 2nd gear ring 11 is { j (k+1) NR1+ (k-j) Ns}/{ k (j+1) }.

Therefore, when make the rotating speed of the rotating ratio input shaft 2 in eccentric drive portion 14 slow and be fixed with the rotating speed of the input shaft 2 of cam disk 5 identical with the rotating speed of pinion shaft 7, eccentric disc 6 and cam disk 5 rotate integrally.On the other hand, when there are differences between the rotating speed and the rotating speed of pinion shaft 7 of input shaft 2, eccentric disc 6 rotates at the periphery of cam disk 5 centered by the center P2 of cam disk 5.

As shown in Figure 2, eccentric disc 6 relative to cam disk 5 bias is: the distance Ra from P1 to P2 is equal with the distance Rb from P2 to P3.Therefore, it is possible to make the rotating center axis P1 of the center P3 of eccentric disc 6 and input shaft 2 be located along the same line, thus distance, i.e. offset R1 between the rotating center axis P1 of the input shaft 2 and center P3 of eccentric disc 6 is made to be " 0 ".

Connecting rod 15 is supported on the outer edge of eccentric disc 6 in the mode that can rotate.Connecting rod 15 has the large footpath annulus 15a in large footpath an end, have the path annulus 15b of path in another end.The large footpath annulus 15a of connecting rod 15 is supported on the outer edge of eccentric disc 6 via connecting rod bearing 16.

< overrunning clutch 17 >

Exterior part 18 stops the overrunning clutch 17 (overrunning clutch) of mechanism and output shaft 23 to link via as single direction rotation.Overrunning clutch 17 when centered by the rotating center axis P4 of output shaft 23 for exterior part 18 being fixed on output shaft 23 to when a sideway swivel, when for rotating to opposite side, exterior part 18 is dallied relative to output shaft 23.

Exterior part 18 is provided with and swings end 18a, swing end 18a is provided with a pair tab 18b, and this pair tab 18b is formed as being sandwiched by path annulus 15b in the axial direction.A pair tab 18b runs through and is provided with the penetration hole 18c corresponding with the internal diameter of path annulus 15b.By connection pin 19 being inserted penetration hole 18c and path annulus 15b, thus connecting rod 15 and exterior part 18 are linked up.In addition, exterior part 18 is provided with annulus 18d.

Overrunning clutch 17 possesses: output shaft 23, and it is configured in the inner circumferential of exterior part 18 coaxially; With multiple roller 25, they are configured between the inner peripheral surface of exterior part 18 and the outer circumferential face of output shaft 23.In addition, overrunning clutch 17 possesses multiple force application part 26, and described multiple force application part 26 along the circumferential direction exerts a force to multiple roller 25, and rotates integratedly with output shaft 23.Overrunning clutch 17 makes roller 25 be fastened between the inner peripheral surface of exterior part 18 and the outer circumferential face of output shaft 23 by exterior part 18 with the relative rotation towards side of output shaft 23 to carry out transmission of drive force.

< crankrocker mechanism 20 >

Next, with reference to Fig. 2 ~ Fig. 4 A-Fig. 4 C, the crankrocker mechanism 20 of the stepless speed variator of present embodiment is described.

As shown in Figure 2, in the stepless speed variator 1 of present embodiment, offset controlling mechanism 4, connecting rod 15 and exterior part 18 constitute crankrocker mechanism 20 (four joint linkage mechanisms).

Crankrocker mechanism 20 is utilized the rotary motion of input shaft 2 to be converted to the oscillating motion of the exterior part 18 centered by the rotating center axis P4 of output shaft 23.As shown in Figure 1, the stepless speed variator 1 of present embodiment possesses 6 crankrocker mechanism 20 altogether.

In crankrocker mechanism 20, if make input shaft 2 and pinion shaft 7 rotate with same speed when the offset R1 of offset controlling mechanism 4 is not " 0 ", then each connecting rod 15 changes phase place every 60 degree, alternately repeatedly to press to output shaft 23 side between input shaft 2 and output shaft 23 or to input shaft 2 side traction simultaneously, thus exterior part 18 is swung.

And, owing to being provided with overrunning clutch 17 between exterior part 18 and output shaft 23, therefore, when exterior part 18 is pressed, exterior part 18 is fixed and the moment of torsion that the oscillating motion because of exterior part 18 produces is passed to output shaft 23, thus output shaft 23 is rotated, in the trailed situation of exterior part 18, exterior part 18 dallies, and the moment of torsion that the oscillating motion because of exterior part 18 produces is not passed to output shaft 23.6 offset controlling mechanisms 4 are configured to change phase place every 60 degree respectively, and therefore, output shaft 23 is by 6 offset controlling mechanism 4 rotary actuations successively.In the stepless speed variator 1 of present embodiment, crankrocker mechanism 20 and overrunning clutch 17 are incorporated in case of transmission 30.

In addition, in the stepless speed variator 1 of present embodiment, as shown in Fig. 3 A-Fig. 3 D, offset R1 can be regulated by offset controlling mechanism 4.

Fig. 3 A shows and makes offset R1 be the state of " maximum ", and pinion shaft 7 and eccentric disc 6 are positioned at the position making the rotating center axis P1 of input shaft 2, the center P2 of cam disk 5 and the center P3 of eccentric disc 6 be arranged in straight line.In this case gear ratio i becomes minimum.Fig. 3 B show make offset R1 be less than Fig. 3 A " in " state, Fig. 3 C shows and makes offset R1 be the state of " little " less than Fig. 3 B.Show in figure 3b make gear ratio i become larger than the gear ratio i of Fig. 3 A " in " state, show the state making gear ratio i become " greatly " larger than the gear ratio i of Fig. 3 B in fig. 3 c.Fig. 3 D shows and makes offset R1 be the state of " 0 ", and the rotating center axis P1 of the input shaft 2 and center P3 of eccentric disc 6 is positioned at concentric position.In this case gear ratio i becomes infinity (∞).

Fig. 4 A-Fig. 4 C shows the relation between the pendulum angle scope of the change of the offset R1 determined by the offset controlling mechanism 4 of present embodiment and the oscillating motion of exterior part 18.

Fig. 4 A shows the situation (gear ratio i is minimum situation) that offset R1 is " maximum " of Fig. 3 A.Fig. 4 B show offset R1 be Fig. 3 B " in " situation (gear ratio i be in situation).Fig. 4 C shows the hunting range θ 2 of in the situation (gear ratio i is large situation) that offset R1 is " little " of Fig. 3 C, corresponding with the rotary motion of offset controlling mechanism 4 exterior part 18.At this, from the rotating center axis P4 of output shaft 23 to connecting rod 15 with the length R2 swinging the tie point of end 18a, the distance namely to the center P5 of connection pin 19 is exterior part 18.

Can understand according to Fig. 4 A-Fig. 4 C, along with offset R1 diminishes, the pendulum angle range Theta 2 of exterior part 18 narrows, and when offset R1 becomes " 0 ", exterior part 18 no longer swings.

[the 1st mode of execution]

< output shaft torque calculates the structure > of control device 52

Next, calculate control device 52 to the output shaft torque of the output torque of the output shaft 23 of calculating stepless speed variator 1 to be described.Output shaft torque calculates control device 52 calculates output shaft 23 output torque based on the value detected by distance detection unit 50.

At this, distance detection unit 50 is fixed in case of transmission 30, detects the distance to exterior part 18.Distance detection unit 50 can be made up of gap (GAP) sensor.Exterior part 18 has swing end 18a and annulus 18d, and described swing end 18a and connecting rod 15 link, and described annulus 18d and output shaft 23 link, and possesses by the detected portion of distance detection unit 50 detecting distance.

Fig. 5 A is the figure that the functional structure calculating control device 52 to output shaft torque is described, and output shaft torque calculates control device 52 and possesses peak value memory section 53, input side cycle detection portion 54, outlet side cycle detection portion 55, mean value calculation portion 56 and output shaft torque calculating part 57.The functional structure that output shaft torque calculates control device 52 realizes in the following manner: based on various sensor, storage and storage testing result etc. in memory, under the control of central operation treatment device (CPU), control program performs various calculation process.

Peak value memory section 53 stores the peak value detected by distance detection unit 50 successively with the number of times of regulation.In the present embodiment, the number of times of regulation refers to, using the position relationship of the distance detection unit 50 during peak value memory section 53 original stored peak value and roller 25 as the 1st state time, to becoming the 2nd state of the position relationship identical with the 1st state, store the number of times of peak value.For the number of times of regulation, after be described in detail with reference to Fig. 5 B-A ~ Fig. 5 B-D.

Mean value calculation portion 56 calculates the mean value of the peak value of the stipulated number stored in peak value memory section 53.Output shaft torque calculating part 57 calculates the moment of torsion of output shaft 23 according to the mean value calculated by mean value calculation portion 56.

Figure 11 A is the figure that the flow process of the computing of output torque to output shaft 23 is described, and in step s 51, distance detection unit 50 detects the distance of the detected portion to exterior part 18 respectively.

In step S52, the mean value calculation portion 56 that output shaft torque calculates control device 52 calculates by the mean value of the peak value of the number of times of the regulation detected apart from detection unit 50.Then, output shaft torque calculating part 57 calculates the moment of torsion of output shaft 23 according to the mean value calculated.The displacement amount (gap value) of exterior part 18 has dependency relation with the transmitting torque of the overrunning clutch of stepless speed variator.Figure 11 B is the figure that citing illustrates the dependency relation of gap value and output torque, and the performance data (OWC performance data) of this dependency relation as overrunning clutch is stored in the lookup table of storage by output shaft torque calculating part 57.

Output shaft torque calculating part 57, with reference to lookup table, using the mean value that calculated by mean value calculation portion 56 as gap value (positive gap width), calculates the moment of torsion of the output shaft corresponding with gap value (positive gap width).During the torque feedback of the output shaft calculated by output shaft torque calculating part 57 to gear ratio can control by output shaft torque calculating control device 52.

The explanation > of the number of times that < specifies

Next, in order to the number of times of the regulation of present embodiment is described, detection unit 50 of adjusting the distance is described particularly with the relative position relation of roller 25 and the detection of peak value.In the present embodiment, in the calculating of output torque, employ the mean value of the peak value to distance detection unit 50 and the relative position relation of roller become identical state.The calculating of the output torque in present embodiment can be applied to the situation of the extremely low speed of a motor vehicle.

Fig. 5 B-A ~ Fig. 5 B-D is the figure that detection unit 50 is described with the relative position relation of roller 25 and the detection of peak value that adjusts the distance.As shown in Fig. 5 B-A ~ Fig. 5 B-D, distance detection unit 50 is fixed on case of transmission 30, and is configured to the annulus in the face of exterior part 18.12 rollers 25 are configured with in overrunning clutch 17 (overrunning clutch).When roller is fastened between the inner peripheral surface of exterior part 18 and the outer circumferential face of output shaft 23, as shown in Figure 6B, at the annulus generation expander of exterior part 18, this expander is detected as peak value by distance detection unit 50.In Fig. 5 B-A ~ Fig. 5 B-D, in order to distinguish 12 rollers, the number marked from 1 to 12 illustrates.Below, the statement of roller is identical.

When input shaft 2 revolve turn around time, overrunning clutch 17 (overrunning clutch) swings one back and forth, carries out engaging (engaging) and engagement releasing (engaging is removed) between a shaking peroid back and forth.Fig. 5 B-A shows No. 1 roller and is in apart from the state (the highest) immediately below detection unit 50.In this condition, overrunning clutch 17 engages, and at the annulus generation expander of exterior part 18, this expander is detected as peak value Peak1 (minimum) by distance detection unit 50.

Then, when engaging by releasing, the output of distance detection unit 50 is reduced to the G0 representing that the signal of no-load condition exports from peak value Peak1 (minimum).

Fig. 5 B-B shows state when overrunning clutch 17 being engaged due to next circle rotation of input shaft 2.Rotation due to output shaft 23 makes the position of roller also change, and No. 1 roller be under the state of Fig. 5 B-A immediately below distance detection unit 50 moves to the position that there occurs skew immediately below distance detection unit 50.The state of Fig. 5 B-B becomes the state (transition) not having roller immediately below distance detection unit 50.

Overrunning clutch 17 engages, and at the annulus generation expander of exterior part 18, this expander is detected as peak value Peak2 (minimum) by distance detection unit 50.Further, when engaging by releasing, the output of distance detection unit 50 is reduced to the G0 representing that the signal of no-load condition exports from peak value Peak2 (minimum).

Fig. 5 B-C shows state when overrunning clutch 17 being engaged due to next circle rotation of input shaft 2.Rotation due to output shaft 23 makes the position of roller also there occurs change further, No. 1 roller movement further of the position offset immediately below distance detection unit 50 under the state of Fig. 5 B-B, becomes between No. 1 roller and No. 2 roller immediately below distance detection unit 50.The state of Fig. 5 B-C also becomes the state (transition) not having roller immediately below distance detection unit 50.

Overrunning clutch 17 engages, and at the annulus generation expander of exterior part 18, this expander is detected as peak value Peak3 (minimum) by distance detection unit 50.Further, when engaging by releasing, the output of distance detection unit 50 is reduced to the G0 representing that the signal of no-load condition exports from peak value Peak3 (minimum).

The peak value (Peak1 ~ 3) of Fig. 5 B-A ~ Fig. 5 B-C is illustrated as 1 group.

Fig. 5 B-D shows state when overrunning clutch 17 being engaged due to next circle rotation of input shaft 2.Due to the rotation of output shaft 23, the position of roller also there occurs change further, under the state of Fig. 5 B-C, be between No. 1 roller and No. 2 roller immediately below distance detection unit 50, but, in Fig. 5 B-D, become No. 2 roller and move to apart from the state immediately below detection unit 50.That is, the state roller of Fig. 5 B-D is in the state (the highest) immediately below distance detection unit 50.

Overrunning clutch 17 engages, and at the annulus generation expander of exterior part 18, this expander is detected as peak value Peak4 (minimum) by distance detection unit 50.Further, when engaging by releasing, the output of distance detection unit 50 is reduced to the G0 representing that the signal of no-load condition exports from peak value Peak4 (minimum).

The peak value (minimum) detected by distance detection unit 50 is stored with the number of times of regulation successively by peak value memory section 53.

If output shaft 23 rotates 1 circle, then roller also rotates 1 circle.Because output shaft 23 rotates 1 circle, No. 1 roller be in when detecting peak value Peak1 (minimum) immediately below distance detection unit 50 moves to the position immediately below distance detection unit 50 again.

Be in the highest position from No. 1 roller and to be output shaft rotate time of being in the highest position to No. 2 roller detecting the state of peak value Peak1 (minimum) and detecting peak value Peak4 (minimum) required for 1 circle time/roller number (such as, roller number: 12).

Using the position relationship of the distance detection unit 50 during peak value memory section 53 original stored peak value Peak1 and roller 25 as the 1st state.To when becoming the 2nd state (such as, No. 2 roller for most high state) with the position relationship identical with the 1st state, the number of times storing peak value is the number of times (when Fig. 5 B-A ~ Fig. 5 B-D, times N=3 of regulation) of regulation.The number of times of this regulation becomes 1 group during the mean value asking for displacement.

Figure 10 is the figure of the example of the group that the 1st mode of execution is shown.Figure 10 shows the example of the peak value (minimum) when the number of times of regulation being set to N=3, using 3 peak values (minimum) as 1 group.Peak value (minimum) in group will be averaged to obtained data as the correct gap width (positive gap width) of impact reducing deviation.

The structure > in < input side cycle detection portion 54, outlet side cycle detection portion 55

Next, input side cycle detection portion 54 and outlet side cycle detection portion 55 are described.Fig. 8 is the figure be described the structure in input side cycle detection portion 54 and outlet side cycle detection portion 55.1 period of rotation of input shaft 2 is detected in input side cycle detection portion 54, and 1 period of rotation of output shaft 23 is detected in outlet side cycle detection portion 55.

The rotating pulse generator (CRANK PULSES generator 81) that input side cycle detection portion 54 can utilize the input shaft side such as between stepless speed variator (speed changer) to arrange detects 1 period of rotation (Ti) of input shaft 2.When using rotating pulse generator (CRANK PULSES generator 81), use the checkout value in the number of teeth (Zi) of rotating pulse generator and the cycle (δ i) of output signal.Input side cycle detection portion 54 can calculate 1 period of rotation (Ti) of input shaft 2 according to Ti=Zi × δ i.

Or input side cycle detection portion 54 can utilize the distance detection unit 50 (gap sensor) of the output shaft side being located at speed changer to detect.As the structure in input side cycle detection portion 54, when employing distance detection unit 50 (gap sensor), the time lag that can obtain the peak value (minimum) of the such signal output waveform illustrated in Fig. 5 B-A ~ Fig. 5 B-D is used as 1 period of rotation (Ti) of input shaft 2.1 period of rotation (Ti) of input side cycle detection portion 54 to the input shaft 2 obtained stores.

Outlet side cycle detection portion 55 can use the rotating pulse generator (vehicle speed sensor) be arranged on output shaft 23 to form, and uses the checkout value in the number of teeth (Zo) of rotating pulse generator (vehicle speed sensor 82) and the cycle (δ o) of output signal.Outlet side cycle detection portion 55 can calculate 1 period of rotation (To) of output shaft 23 according to To=Zo × δ o.

< output shaft torque calculates the process > of control device 52

Next, utilize the flow chart of Fig. 9, the handling process output shaft torque of present embodiment being calculated to control device 52 is described.

In step S91, peak value memory section 53 stores with the number of times specified successively to the minimum Peak (N) detected by distance detection unit 50 (gap sensor).The number of times of this regulation is the number of times utilizing Fig. 5 B-A ~ Fig. 5 B-D to illustrate.

In step S92,1 period of rotation (Ti) of the minimizing time lag of the signal output waveform apart from detection unit 50 (gap sensor) as input shaft 2 stores by input side cycle detection portion 54.And, also can be, in step S94, input side cycle detection portion 54 utilizes the checkout value of the rotating pulse generator on input shaft (CRANK PULSES generator 81) calculate 1 period of rotation (Ti) of input shaft 2 and store, and replaces step S92.

In step S93, outlet side cycle detection portion 55 calculates 1 period of rotation (To) of output shaft 23 according to the rotating pulse generator (vehicle speed sensor 82) on output shaft and stores.The concrete process in input side cycle detection portion 54 and outlet side cycle detection portion 55 as illustrated in figure 8.

In step S95, mean value calculation portion 56 obtains 1 period of rotation (Ti) of input shaft 2 from input side cycle detection portion 54, in addition, obtain 1 period of rotation (To) of output shaft 23 from outlet side cycle detection portion 55, and calculate input shaft revolution N (number of times of regulation) according to following formula (1).

N=To/Ti/ roller number (part that fractions omitted point is later) (1)

In step S96, mean value calculation portion 56 obtains the minimum Peak (N) stored in peak value the memory section 53 and input shaft revolution N calculated in step S95, and calculates the shift value (positive gap width) of the deviation reducing output value according to following formula (2).

Positive gap width=Σ Peak (N)/N (2)

Σ Peak (N) represents that N number of minimum is added.This positive gap width be near distance detection unit 50 consistent with the position relationship of roller till minimum Peak (N) average obtained value.

Further, in the example of Fig. 5 B-A ~ Fig. 5 B-D, for the most high state of No. 1 roller and the most high state of No. 2 roller consistent minimum Peak (N) be illustrated, but the structure of present embodiment is not limited thereto.Such as, also can be, by the relation between an arbitrary roller in the scope that roller rotates 1 week of No. 1 roller and No. 3 roller, No. 1 roller and No. 4 roller etc. and another different rollers, obtain the minimum Peak (N) to position relationship is consistent.

In the step s 97, output shaft torque calculating part 57, with reference to the performance data (OWC performance data) of the overrunning clutch of the relation represented between output shaft torque and gap width, calculates the output torque corresponding with the positive gap width calculated.

According to the present embodiment, by adopting, the peak value to consistent with the position relationship of roller apart from detection unit being averaged and the revolution that obtains, output shaft torque can being calculated based on the displacement measurement reducing deviation.

[the 2nd mode of execution]

Next, the structure of the output shaft torque for calculating present embodiment is described.Figure 13 A-Figure 13 B is the figure of the relation between citing outer shape deviation that roller is shown and the change of the output apart from detection unit 50 (gap sensor), due to the deviation etc. of dimensional accuracy, the diameter of the roller 25a of Figure 13 A is less than the diameter of the roller 25b of Figure 13 B.Roller 25a, 25b are in immediately below distance detection unit 50 (gap sensor), are all in the highest state, but due to roller footpath difference, therefore, the maximum displacement detected by distance detection unit 50 in Figure 13 B is larger.

The explanation > of the number of times that < specifies

Next, in order to the number of times of the regulation of present embodiment is described, detection unit 50 of adjusting the distance is described particularly with the relative position relation of roller 25 and the detection of peak value.In the present embodiment, in the calculating of output torque, employ about identical roller, the mean value of peak value to distance detection unit 50 and the relative position relation between roller become identical state, in order to avoid be subject to the impact of the deviation of such roller.In the situation of the medium/high speed of a motor vehicle that calculating can be applied in such as acceleration and deceleration or speed change is medium, driving conditions changes of the output torque in present embodiment.

In the present embodiment, stepless speed variator 1 possesses distance detection unit 50 and output shaft torque calculates control device 52, in the following description, for the structure identical with the 1st mode of execution, mark identical reference number, and the repetitive description thereof will be omitted.

Figure 12 A-Figure 12 D is the figure that detection unit 50 is described with the relative position relation of roller 25 and the detection of peak value that adjusts the distance.Compared with the situation of Fig. 5 B-A ~ Fig. 5 B-D, because Figure 12 A-Figure 12 D shows the different state of the speed of a motor vehicle, therefore, the output waveform of the distance detection unit 50 (gap sensor) in Figure 12 A-Figure 12 D is different from the output waveform of Fig. 5 B-A ~ Fig. 5 B-D.

When input shaft 2 revolve turn around time, overrunning clutch 17 swings one back and forth, carries out engaging (engaging) and engagement releasing (engaging is removed) between a shaking peroid back and forth.Figure 12 A shows No. 1 roller and is in apart from the state (the highest) immediately below detection unit 50.In this condition, overrunning clutch 17 engages, and at the annulus generation expander of exterior part 18, this expander is detected as peak value Peak1 (minimum) by distance detection unit 50.The peak value Peak1 (minimum) detected by distance detection unit 50 is stored in peak value memory section 53.

Identical below, the detection of peak value (minimum) is carried out in the rotation corresponding to input shaft 2, is stored in peak value memory section 53 by the peak value (minimum) that detects of distance detection unit 50 by phase adduction successively.

When output shaft 23 rotates 1 circle, roller also rotates 1 circle, because output shaft 23 rotates 1 circle, No. 1 roller be such as in when detecting peak value Peak1 (minimum) immediately below distance detection unit 50 moves to the position immediately below distance detection unit 50 again.

Figure 12 B becomes and to make because output shaft 23 rotates 1 circle No. 1 roller move to state immediately below distance detection unit 50.That is, the state of Figure 12 B become No. 1 roller be in distance detection unit 50 immediately below state (the highest).

By the position relationship of the distance detection unit 50 during peak value memory section 53 original stored peak value Peak1 and roller (such as, No. 1 roller) as the 1st state.To become there is the position relationship identical with the 1st state the 2nd state (such as, No. 1 roller rotates 1 circle, No. 1 roller moves to the state immediately below distance detection unit 50) time till store peak value number of times be the number of times (when Figure 12 A-Figure 12 D, times N=4 of regulation) of regulation.

Further, in the relation between the rotation and the rotation of output shaft of input shaft, relative phase is inconsistent, can produce phase difference PH.Therefore, as shown in Figure 12 C, Figure 12 D, No. 1 roller is not in immediately below distance detection unit 50, and roller position is different from the position immediately below distance detection unit 50.In each group, although roller position is not quite identical, but the peak value (minimum) of the output waveform apart from detection unit 50 (gap sensor) can be divided into the group that the pattern of the magnitude relationship of roller is roughly consistent, try to achieve the average of the data in this 1 group.

Figure 15 is the figure of the example of the group that the 2nd mode of execution is shown.Figure 15 shows the example of the peak value (minimum) when the number of times of regulation being set to N=4, using 4 peak values (minimum) as 1 group.Peak value (minimum) in group will be averaged to obtained data as the correct gap width (positive gap width) of impact reducing deviation.

< output shaft torque calculates the process > of control device 52

Next, utilize the flow chart of Figure 14, the handling process output shaft torque of present embodiment being calculated to control device 52 is described.

In step s 141, peak value memory section 53 stores with the number of times specified successively to the minimum Peak (N) detected by distance detection unit 50 (gap sensor).The number of times of this regulation is the number of times utilizing Figure 12 A-Figure 12 D to illustrate.

In step S142,1 period of rotation (Ti) of the minimizing time lag of the signal output waveform apart from detection unit 50 (gap sensor) as input shaft 2 stores by input side cycle detection portion 54.And, also can be, in step S144, input side cycle detection portion 54 utilizes the checkout value of the rotating pulse generator on input shaft (CRANK PULSES generator 81) calculate 1 period of rotation (Ti) of input shaft 2 and store, and replaces step S142.

In step S143, outlet side cycle detection portion 55 calculates 1 period of rotation (To) of output shaft 23 according to the rotating pulse generator (vehicle speed sensor 82) on output shaft and stores.The concrete process in input side cycle detection portion 54 and outlet side cycle detection portion 55 as illustrated in figure 8.

In step S145, mean value calculation portion 56 obtains 1 period of rotation (Ti) of input shaft 2 from input side cycle detection portion 54, in addition, obtain 1 period of rotation (To) of output shaft 23 from outlet side cycle detection portion 55, and calculate input shaft revolution N (number of times of regulation) according to following formula (3).

N=To/Ti (part that fractions omitted point is later) (3)

In step S146, mean value calculation portion 56 obtains the minimum Peak (N) stored in peak value the memory section 53 and input shaft revolution N calculated in step S95, and calculates the shift value (positive gap width) of the deviation reducing output value according to following formula (4).

Positive gap width=Σ Peak (N)/N (4)

Σ Peak (N) represents that N number of minimum is added.This positive gap width is that the minimum Peak (N) become till identical state about same roller near distance detection unit 50 and the relative position relation between roller averages obtained value.

In step S147, output shaft torque calculating part 57, with reference to the performance data (OWC performance data) of the overrunning clutch of the relation represented between output shaft torque and gap width, calculates the output torque corresponding with the positive gap width calculated.

In addition, the deviation of the checkout value of the distance detection unit caused by the deviation of roll shape can be eliminated, and calculate output shaft torque.

[the 3rd mode of execution]

Next, the structure of the output shaft torque for calculating present embodiment is described.In the 2nd mode of execution above, as shown in Figure 12 A-Figure 12 D, in the relation between the rotation and the rotation of output shaft of input shaft, relative phase is inconsistent, can produce phase difference PH.

When the outer shape of exterior part 18 exists deviation, such as, when exterior part 18 is situation and the expander midway of maximum expander, the checkout value of distance detection unit 50 also can produce deviation.Due to phase difference PH, when distance detection unit 50 measures different detected portion (detected portion when detected portion during maximum expander and expander midway) of exterior part 18, the deviation of outer shape is overlapping with the testing result of distance detection unit 50, and testing precision can be caused to reduce.

In the present embodiment, in the calculating of output torque, employ about same roller, to the position consistency of roller and the phase place of exterior part consistent the mean value of peak value.The calculating of the output torque in present embodiment can be applied to the situation that the driving conditions such as such as constant speed state change the less speed of a motor vehicle or the high speed of a motor vehicle.

In the following description, for the structure identical with the 2nd mode of execution with the 1st mode of execution, also the repetitive description thereof will be omitted to mark identical reference number.

The explanation > of the number of times that < specifies

Figure 16 A-Figure 16 D is the figure that detection unit 50 is described with the relative position relation of roller 25 and the detection of peak value that adjusts the distance.Compared with the situation of Fig. 5 B-A ~ Fig. 5 B-D, because Figure 16 A-Figure 16 D shows the different state of the speed of a motor vehicle, therefore, the output waveform of the distance detection unit 50 (gap sensor) in Figure 16 A-Figure 16 D is different from the output waveform of Fig. 5 B-A ~ Fig. 5 B-D.

When input shaft 2 revolve turn around time, overrunning clutch 17 swings one back and forth, carries out engaging (engaging) and engagement releasing (engaging is removed) between a shaking peroid back and forth.Figure 16 A shows No. 1 roller and is in apart from the state (the highest) immediately below detection unit 50.In this condition, overrunning clutch 17 engages, and at the annulus generation expander of exterior part 18, this expander is detected as peak value Peak1 (minimum) by distance detection unit 50.The expander that this state shows exterior part 18 becomes maximum state (maximum expander).

Figure 16 B becomes and to make because output shaft 23 rotates 1 circle No. 1 roller move to state immediately below distance detection unit 50.That is, the state of Figure 16 B become No. 1 roller be in distance detection unit 50 immediately below state (the highest).

Now, the state of exterior part 18 is the states of the expander midway reached before maximum expander, different from the state of the maximum expander of the exterior part 18 of Figure 16 A.

Figure 16 C shows the state that exterior part 18 is maximum expander, but the position of No. 1 roller is moved to the position different from immediately below distance detection unit 50.In Figure 16 C, No. 3 roller is in apart from the state immediately below detection unit 50.

Figure 16 D shows the state that exterior part 18 is maximum expander, and roller shows No. 1 roller and rotates 1 circle along with output shaft 23 and be in the state of the position immediately below distance detection unit 50.

By the distance detection unit 50 during peak value memory section 53 original stored peak value Peak1 with roller (such as, No. 1 roller) as the 1st state.To become there is the position relationship identical with the 1st state the 2nd state (such as, No. 1 roller is positioned at the state immediately below distance detection unit 50) and the 1st state time the rotatable phase of input shaft 2 and the 2nd state time rotatable phase become identical till store peak value number of times be the number of times (when Figure 16 A-Figure 16 D, times N=12 of regulation) of regulation.

About the relation of the rotatable phase of input shaft and the rotatable phase of output shaft, relative phase is consistent at Peak12 place.Figure 17 is the figure of the example of the peak value (minimum) illustrated when the number of times of regulation being set to N=12, using 12 peak values (minimum) as 1 group, and using the data making the peak value of this scope (minimum) equalization obtain as the correct gap width (positive gap width) of impact reducing deviation.

< output shaft torque calculates the process > of control device 52

Next, utilize the flow chart of Figure 18, the handling process output shaft torque of present embodiment being calculated to control device 52 is described.

In step S181, peak value memory section 53 stores with the number of times specified successively to the minimum Peak (N) detected by distance detection unit 50 (gap sensor).The number of times of this regulation is the number of times utilizing Figure 16 A-Figure 16 D to illustrate.When N=16, peak value memory section 53 stores 16 minimums.

In step S182,1 period of rotation (Ti) of the minimizing time lag of the signal output waveform apart from detection unit 50 (gap sensor) as input shaft 2 stores by input side cycle detection portion 54.And, also can be, in step S184, input side cycle detection portion 54 utilizes the checkout value of the rotating pulse generator on input shaft (CRANK PULSES generator 81) calculate 1 period of rotation (Ti) of input shaft 2 and store, and replaces step S182.

In step S183, outlet side cycle detection portion 55 calculates 1 period of rotation (To) of output shaft 23 according to the rotating pulse generator (vehicle speed sensor 82) on output shaft and stores.The concrete process in input side cycle detection portion 54 and outlet side cycle detection portion 55 as illustrated in figure 8.

In step S185, mean value calculation portion 56 obtains 1 period of rotation (Ti) of input shaft 2 from input side cycle detection portion 54, in addition, obtain 1 period of rotation (To) of output shaft 23 from outlet side cycle detection portion 55, and calculate input shaft revolution N (number of times of regulation) according to following formula (5).

Least common multiple/the Ti (5) of N=Ti and To

In step S186, mean value calculation portion 56 obtains the minimum Peak (N) stored in peak value the memory section 53 and input shaft revolution N calculated in step S95, and calculates the shift value (positive gap width) of the deviation reducing output value according to following formula (6).

Positive gap width=Σ Peak (N)/N (6)

Σ Peak (N) represents that N number of minimum is added.This positive gap width be position consistency about the near roller of same roller and the swaying phase of exterior part 18 consistent till minimum Peak (N) average obtained value.

In step S187, output shaft torque calculating part 57, with reference to the performance data (OWC performance data) of the overrunning clutch of the relation represented between output shaft torque and gap width, calculates the output torque corresponding with the positive gap width calculated.

In addition, the deviation of the checkout value because of the distance detection unit caused by the deviation of roll shape can be eliminated, and the deviation of the checkout value because of the distance detection unit caused by the deviation of the outer shape of exterior part can be eliminated, and calculate output shaft torque.

[the 4th mode of execution]

In the 1st mode of execution illustrated above, the situation of the extremely low speed of a motor vehicle can be applied to, in the 2nd mode of execution, the situation of the medium/high speed of a motor vehicle can be applied to, in the 3rd mode of execution, can be applied to the situation of the high speed of a motor vehicle, the computational methods of the number of times (input shaft revolution N) of the regulation in each implementation methods are different.This is because, different according to the speed of a motor vehicle for the detection frequency calculating the peak value of positive gap width, therefore to adopt the computational methods being suitable for various situation respectively.

If be only conceived to the precision of positive gap width, then in the 3rd mode of execution, asked for position consistency to roller and the phase place of exterior part consistent the mean value of peak value, therefore, precision positive gap width can be superlatively calculated in the 1st to the 3rd mode of execution, but, to consistent, the more time be spent.Therefore, the situation of the high speed of a motor vehicle can carrying out the detection of a fairly large number of peak value is preferably applied to.

On the other hand, when the 1st mode of execution, the mean value of the peak value to distance detection unit 50 and the relative position relation between roller become identical state is employed in the calculating of output torque, therefore, if be conceived to the precision of positive gap width, then the situation of ratio of precision the 3rd mode of execution is low, but, compare with the 3rd mode of execution with the 2nd mode of execution, the calculating of positive gap width can be carried out by the detection of less peak value., when the extremely low speed of a motor vehicle, if adopt the computational methods illustrated in the 3rd mode of execution, then the detection of peak value needs the longer time, cannot calculate positive gap width efficiently.

In the present embodiment, such structure is described: corresponding to the rotating speed (change of driving conditions) of output shaft 23, changes the setting of the computational methods of the number of times (input shaft revolution N) of regulation, try to achieve the mean value of peak value.Figure 19 is the figure that the structure calculating control device 52 to the output shaft torque of the 4th mode of execution is described.Output shaft torque calculates control device 52 and possesses peak value memory section 53, input side cycle detection portion 54, outlet side cycle detection portion 55, mean value calculation portion 56, output shaft torque calculating part 57, output shaft speed detection unit 58 and stipulated number configuration part 59.

The functional structure that output shaft torque calculates control device 52 realizes in the following manner: based on various sensor, storage and storage testing result etc. in memory, under the control of central operation treatment device (CPU), control program performs various calculation process.Further, in the structure of Figure 19, for the structure identical with the 1st mode of execution, also the repetitive description thereof will be omitted to mark identical reference number.

Output shaft speed detection unit 58 judges the rotating speed (change of driving conditions) of output shaft 23 based on the testing result in outlet side cycle detection portion 55.

It is any that output shaft speed detection unit 58 judges to belong in such as following situation: the rotating speed of (1) output shaft 23 is as the situation of the extremely low speed of a motor vehicle; (2) in acceleration and deceleration or the situation of the medium/high speed of a motor vehicle that speed change is medium, driving conditions changes; Or (3) driving conditions changes the situation of the less speed of a motor vehicle or the high speed of a motor vehicle.

Stipulated number configuration part 59 sets the computational methods of the stipulated number of the mean value of the checkout value for calculating distance detection unit 50 based on the result of determination of output shaft speed detection unit 58.Such as, when the rotating speed of output shaft 23 be extremely the low speed of a motor vehicle, stipulated number configuration part 59 is set in the computational methods of the stipulated number illustrated in the 1st mode of execution.

In acceleration and deceleration or speed change is medium, driving conditions changes the medium/high speed of a motor vehicle, stipulated number configuration part 59 is set in the computational methods of the stipulated number illustrated in the 2nd mode of execution.

When driving conditions changes the less speed of a motor vehicle or the high speed of a motor vehicle, stipulated number configuration part 59 is set in the computational methods of the stipulated number illustrated in the 3rd mode of execution.

The computational methods of the stipulated number set by stipulated number configuration part 59 are imported into mean value calculation portion 56.Mean value calculation portion 56 calculates input shaft revolution according to the computational methods of the stipulated number of setting.

When setting the computational methods of the stipulated number illustrated in the 1st mode of execution, mean value calculation portion 56 calculates input shaft revolution N according to the formula (1) of the 1st mode of execution.

When setting the computational methods of the stipulated number illustrated in the 2nd mode of execution, mean value calculation portion 56 calculates input shaft revolution N according to the formula (3) of the 2nd mode of execution.

When setting the computational methods of the stipulated number illustrated in the 3rd mode of execution, mean value calculation portion 56 calculates input shaft revolution N according to the formula (5) of the 3rd mode of execution.

And, mean value calculation portion 56 obtains the minimum Peak (N) stored in peak value the memory section 53 and input shaft revolution N calculated, and calculates the shift value (positive gap width) of the deviation reducing output value according to following formula (7).

Positive gap width=Σ Peak (N)/N (7)

Σ Peak (N) represents that N number of minimum is added.Output shaft torque calculating part 57, with reference to the performance data (OWC performance data) of the overrunning clutch of the relation represented between output shaft torque and gap width, calculates the output torque corresponding with the positive gap width calculated.

According to the present embodiment, the computational methods of stipulated number (revolution) that can be corresponding according to the rotating speed (change of driving conditions) with output shaft 23, try to achieve the mean value of the checkout value of distance detection unit.

In addition, flexible Application the 1st is to the 3rd mode of execution characteristic separately, for respective travelling state, select the computational methods of optimum positive gap width, can calculate positive gap width efficiently thus, and the positive gap width that the computational methods according to optimum can be calculated feeds back to during the calculating of output shaft torque and gear ratio control.

Although invention has been described for the embodiment of reference example, should be understood that the present invention is not limited to disclosed exemplary embodiment.The scope of following claim should be given the widest explanation to comprise all such modified examples and equivalent structure and fuction.

Claims

1. a stepless speed variator, it possesses:

Input shaft (2), it is used driving source transmission of drive force by from traveling;

Output shaft (23), it has the rotating center axis with the rotating center axis being parallel of described input shaft (2);

Turning radius controlling mechanism (4 ~ 7), it can regulate turning radius freely, can rotate centered by the rotating center axis of described input shaft (2);

Crankrocker mechanism (20), it has the exterior part (18) linked with described output shaft (23) and the connecting rod (15) linking described turning radius controlling mechanism (4 ~ 7) and described exterior part (18), and the rotary motion of described turning radius controlling mechanism (4 ~ 7) is converted to the oscillating motion of described exterior part (18);

Single direction rotation stops mechanism (17), described exterior part (18) is fixed on described output shaft (23) when described exterior part (18) is for swinging aside by it, and makes described exterior part (18) dally relative to described output shaft (23) when described exterior part (18) is for swinging to opposite side; And

Case of transmission (30), it receives described crankrocker mechanism (20) and described single direction rotation stops mechanism (17),

Described single direction rotation stops mechanism (17) to be following such overrunning clutch, and this overrunning clutch possesses: described output shaft (23), and it is configured in the inner circumferential of described exterior part (18) coaxially; Multiple roller (25), it is configured between the inner peripheral surface of described exterior part (18) and the outer circumferential face of described output shaft (23); And multiple force application part (26), it along the circumferential direction exerts a force to described multiple roller (25) and rotates integratedly with described output shaft (23), this overrunning clutch is by the relative rotation towards described side of described exterior part (18) with described output shaft (23), described roller (25) is fastened between the inner peripheral surface of described exterior part (18) and the outer circumferential face of described output shaft (23) and carrys out transmission of drive force

Described exterior part (18) has: swing end (18a), itself and described connecting rod (15) link; With annulus (18d), itself and described output shaft (23) link and possess detected portion,

The feature of described stepless speed variator is,

Described stepless speed variator possesses:

Distance detection unit (50), they are fixed on described case of transmission (30), detect the distance to described detected portion; With

Output shaft torque calculates control device (52), and it calculates the moment of torsion of described output shaft (23) based on the value detected by described distance detection unit (50),

Described output shaft torque calculates control device (52) to be possessed:

Peak value memory section (53), it stores the peak value of the value detected by described distance detection unit (50) successively with the number of times of regulation;

Input side cycle detection portion (54), it detects 1 period of rotation of described input shaft (2);

Outlet side cycle detection portion (55), it detects 1 period of rotation of described output shaft (23);

Mean value calculation portion (56), it calculates the mean value of the peak value of the stipulated number of described storage; And

Output shaft torque calculating part (57), the moment of torsion of its output shaft (23) according to described mean value calculation,

The number of times of described regulation is made up of following such number of times: this number of times be using described distance detection unit (50) during described peak value memory section (53) original stored peak value with the position relationship of described roller (25) as the 1st state time, to when becoming the 2nd state with the described position relationship identical with described 1st state, the number of times that described peak value is stored.

2. stepless speed variator according to claim 1, is characterized in that,

The number of times of described regulation is made up of following such number of times: this number of times be when becoming with described 1st state identical described 2nd state to the roller configured immediately preceding the described roller (25) under described 1st state below, the number of times that described peak value is stored.

3. stepless speed variator according to claim 1, is characterized in that,

The number of times of described regulation is made up of following such number of times: this number of times is before described output shaft (23) rotates 1 circle, when becoming described 2nd state identical with described 1st state to other any roller different from the described roller (25) under described 1st state, the number of times that described peak value is stored.

4. stepless speed variator according to claim 1, is characterized in that,

The number of times of described regulation becomes number of times same roller to the roller (25) of described 1st state and the roller (25) of described 2nd state.

5. stepless speed variator according to claim 4, is characterized in that,

The number of times of described regulation is the number of times to the rotatable phase of the described input shaft when rotatable phase of described input shaft during described 1st state and described 2nd state becomes identical phase place.

6. the stepless speed variator according to any one in claims 1 to 3, is characterized in that,

The number of times of described regulation calculates according to the quantity of 1 period of rotation/described multiple roller (25) of 1 period of rotation/described input shaft (2) of described output shaft (23).

7. stepless speed variator according to claim 4, is characterized in that,

The number of times of described regulation calculates according to 1 period of rotation of 1 period of rotation/described input shaft (2) of described output shaft (23).

8. stepless speed variator according to claim 5, is characterized in that,

The number of times of described regulation calculates according to 1 period of rotation of the least common multiple/described input shaft (2) of 1 period of rotation of described input shaft (2) and 1 period of rotation of described output shaft (23).

9. stepless speed variator according to claim 6, is characterized in that,

Described stepless speed variator also possesses:

Output shaft speed detection unit (58), its testing result based on described outlet side cycle detection portion (55) judges the rotating speed of described output shaft (23); With

Stipulated number configuration part (59), it sets the computational methods of the number of times of described regulation based on described judgement,

Described mean value calculation portion (56) calculates the number of times of described regulation according to the computational methods of described setting.