CN102384234B - Step-less variator structure - Google Patents
Step-less variator structure Download PDFInfo
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- CN102384234B CN102384234B CN201110242898.XA CN201110242898A CN102384234B CN 102384234 B CN102384234 B CN 102384234B CN 201110242898 A CN201110242898 A CN 201110242898A CN 102384234 B CN102384234 B CN 102384234B
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- movable sheave
- actuator
- control mechanism
- power
- stepless speed
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Abstract
The present invention provides a step-less variator structure, wherein when the power for enabling a movable pulley is increased, a V-stripe type automatic variator is uneasily large-scaled. The step-less variator structure used for the V-stripe type automatic variator provided with a fixed pulley (61) and used for moving a movable pulley (62), and provided with a V-strip between two pulleys, is provided with a first control mechanism (CM1) provided with a first actuator (90) for moving the movable pulley (62), and a second control mechanism (CM2) cooperated with the first control mechanism and used for mobbing the movable pulley (62). Under the condition of increasing the power for moving the movable pulley, the load of each actuator can be reduced, the large-scaling of each actuator is inhibited thereby realizing the miniaturization of the V-strip type automatic variator.
Description
Technical field
The present invention relates to the stepless speed variator structure that V belt-type automatic transmission is used.
Background technique
At present, the stepless speed variator structure of using as V belt-type automatic transmission, the known stepless speed variator structure as shown in Figure 37 that has for example patent documentation 1.The symbol of using in the document describes, this stepless speed variator structure is to have fixed pulley (203) and the movable sheave (207) that can move with respect to this fixed pulley (203) and at two pulleys (203,207) between, volume is hung the stepless speed variator structure that V is with the V belt-type automatic transmission of (211) to use, it has single control mechanism (300), and this single control mechanism (300) has the mobile single actuator (100) of movable sheave of making (207).
[patent documentation 1] TOHKEMY 2009-79759 communique
In above-mentioned existing stepless speed variator structure, owing to being configured to the structure that movable sheave is moved by single actuator and single control mechanism, if therefore increase the power for movable sheave is moved, the tendency that exists single actuator and single control mechanism to maximize, consequently, there is the easily such shortcoming of maximization of V belt-type automatic transmission.
Summary of the invention
Even if it is a kind of in the case of increasing for making power that movable sheave moves that problem to be solved by this invention is to provide, V belt-type automatic transmission is also difficult for the stepless speed variator structure maximizing.
In order to solve above-mentioned problem, stepless speed variator structure involved in the present invention is to have fixed pulley and the movable sheave that can move with respect to this fixed pulley and hang with the stepless speed variator structure that the V belt-type automatic transmission of V band is used at two pulley rooms volumes, described stepless speed variator structure is characterised in that to possess:
The first control mechanism, it has the first actuator that described movable sheave is moved;
The second control mechanism, it cooperates with described the first control mechanism, and has the second actuator that described movable sheave is moved.
According to this stepless speed variator structure, first control mechanism due to moving through of movable sheave with the first actuator carries out with the cooperation of second control mechanism with the second actuator, therefore power that movable sheave moves, this power decentralized can be given to first control mechanism with the first actuator and second control mechanism with the second actuator in the case of increasing for making.
Thereby, make compared with existing structure that movable sheave moves with utilizing single actuator and single control mechanism, even in the case of increasing for making power that movable sheave moves, also can reduce to the load to actuator, suppress the maximization of each actuator, thereby can realize on the whole the miniaturization of V belt-type automatic transmission.
And, by suppressing the load of each actuator, can improve the durability of each actuator.
Preferably described the first actuator is the actuator driving by electric power, and described the second actuator is the actuator that the centrifugal force by accompanying with the rotation of described movable sheave drives.
If form like this, the centrifugal force of the rotation of a side actuator by having utilized movable sheave drives, and therefore can suppress the power consumption of stepless speed variator structural entity, thereby can reduce energy loss.
In this case, more preferably described the first actuator is configured in described the second actuator around.
If form like this, two actuators can be configured in around the running shaft of belt wheel compactly, and improve the configuration degrees of freedom of the first actuator simultaneously.
In this case, preferably described the first actuator is configured in interior all positions that described V is with.
If form like this, can effectively utilize and easily become all spaces in the V of wasted space band.
Preferably described the second actuating device is for multiple governor weights and cam member, the plurality of governor weight is configured in around the spin axis of described movable sheave, this cam member remains on this governor weight between itself and movable sheave, under the effect of the centrifugal force accompanying with the rotation of movable sheave, governor weight moves movable sheave.
If form like this, the second actuator makes square increase pro rata of power that movable sheave moves and the angular velocity of movable sheave, therefore can reduce the power that the first actuator moves movable sheave, further suppresses power consumption.
Preferably described the first control mechanism possesses via bearing and is held in the movable sheave support of described movable sheave, transmits the power transfering part of the power of described the first actuator to this movable sheave support, and this power transfering part is configured in described the first actuator side with respect to the rotating center of described movable sheave.
If form like this, can make power transfering part miniaturization, thereby can realize the miniaturization of stepless speed variator structure and V belt-type automatic transmission.
In this case, preferred described bearing is configured in described governor weight around.
If form like this, can utilize the peripheral space configuration bearing of governor weight, although be provided with first control mechanism with the first actuator and second control mechanism with the second actuator, also can suppress the maximization in the axial direction of stepless speed variator structure and V belt-type automatic transmission device.
Preferably described the first actuator is the actuator moving as follows,, at the low rotary area of described movable sheave, produce the equidirectional power of power that will make described movable sheave move with described the second control mechanism, at the high rotary area of described movable sheave, to make the power that described movable sheave moves produce resistance with respect to described the second control mechanism.
If form like this,, at the low rotary area of movable sheave, by the unidirectional power being produced by the first control mechanism and the second control mechanism, movable sheave is moved, therefore can movable sheave be moved swimmingly by two control mechanisms.
On the other hand, at the high rotary area of movable sheave, the mode that the first actuator becomes resistance with the power that will make movable sheave move with respect to the second control mechanism is moved, and therefore can suppress the excessive movement of the movable sheave that the second control mechanism causes, i.e. excessive gear shifting operation.
Brief description of the drawings
Fig. 1 is the two-wheeled side view of small motor cycle type of an example of vehicle of V belt-type automatic transmission representing as possessing a mode of execution that has used the stepless speed variator structure the present invention relates to.
Fig. 2 is the side view of this two-wheeled power unit that possesses V belt-type automatic transmission.
Fig. 3 is that III-III sectional view is omitted in the part of Fig. 2.
Fig. 4 is the figure that represents a mode of execution of the stepless speed variator structure the present invention relates to, and is the partial enlarged drawing of Fig. 3.
Fig. 5 is the figure that represents this mode of execution, is that V is omitted to view in the part of Fig. 3.
Fig. 6 is the figure that represents movable sheave 62, (a) be plan view, (b) being the b-b sectional view of figure (a), is (c) the c-c sectional view of figure (a), is (d) the d-d sectional view of figure (a).
Fig. 7 is the figure that represents retainer 65, (a) is plan view, is (b) the b-b sectional view of figure (a).
Fig. 8 is the figure that represents movable sheave support 80, (a) is plan view, is (b) the b-b sectional view of figure (a), is (c) the c-c sectional view of figure (a).
Fig. 9 is the figure that represents cam member 110, (a) be plan view, (b) be the b-b sectional view of figure (a), (c) be the c-c sectional view of figure (a), (d) be the local worm's eye view that omits, (e) be the e-e sectional view of figure (a).
Figure 10 is the figure that represents linking member 130, (a) is plan view, is (b) plan view, is (c) the c-c sectional view of figure (b).
Figure 11 is the figure that represents guide 140, (a) is plan view, is (b) the b-b sectional view of figure (a), is (c) the c-c sectional view of figure (a), (d) is worm's eye view.
Figure 12 is the figure that represents the opposing party's stopper 42s, (a) is plan view, is (b) left side view, is (c) the c-c sectional view of figure (a).
Figure 13 is action specification figure.
Figure 14 (a), (b) are respectively action specification figure.
Symbol description:
40: speed changer case
40L: left box body (speed changer cover)
41s, 42s: stopper
50:V belt-type automatic transmission
51: belt shaft
53:V band
60: driving pulley (stepless speed variator structure)
61: fixed pulley
62: movable sheave
64: bearing
80: movable sheave support
90: the first actuators
CM1: the first control mechanism
CM2 the second control mechanism
T: power transfering part
100: the second actuators
101: governor weight
110: cam member
Embodiment
Below, with reference to accompanying drawing, the mode of execution of stepless speed variator structure involved in the present invention is described.
Shown in Fig. 1 two-wheeled 10 is the vehicles that by pivot 12 and rear buffer cell 13, power unit 20 swung to the rear portion that is suspended at freely vehicle frame 11 with respect to vehicle frame 11 around pivot 12.On head tube 11h, turn to front fork 14 is installed freely, in the lower end of this front fork 14, front-wheel 15F is installed.Steering handle 15 is installed on top at front fork 14.
Vehicle frame 11 has pairing left and right seat frame 11s (only illustrating a side) at rear portion.On this seat frame 11s, be provided with for passenger and straddle the seat 16 of taking one's seat, below this seat 16, be provided with the containing box 17 of opening upward.Dispose fuel tank 18 at the rear of containing box 17.
Power unit 20 has as the motor 30 of driving source, is arranged on the speed changer case 40 at the rear of this motor 30.In speed changer case 40, be built-in with the V belt-type automatic transmission 50 that the driving force of motor 30 is transmitted to trailing wheel 15R.Power unit 20 swings the rear portion that is arranged on freely vehicle frame 11, and the power of motor 30 transmits to trailing wheel 15R via the V belt-type automatic transmission 50 in speed changer case 40.Power unit 20 doubles as rear-swing arm.
As shown in Figure 2 and Figure 3, motor 30 has crankcase 31, cylinder block 32, cylinder head 33 and valve mechanism cover 34.At the front end of crankcase 31 in conjunction with by the cylinder block 32 along general horizontal direction orientation, at the front end of this cylinder block 32 in conjunction with cylinder head 33, at the front end of this cylinder head 33 in conjunction with valve mechanism cover 34.
As shown in Figure 3, by the ball bearing 31b, the 31b that are held in crankcase 31, bent axle 31c is supported as rotating, piston 32p can be slidably arranged in cylinder block 32.Bent axle 31c and piston 32p link by connecting rod 32c, make bent axle 31c rotation by the to-and-fro motion of piston 32p.Bent axle 31c forms main shaft 51 described later.In cylinder head 33, connect the sucking pipe 35 (Fig. 1) and the outlet pipe 36 (Fig. 1) that are communicated with firing chamber 33c.As shown in Figure 2, on sucking pipe 35, connect fuel supplying device 35a and air-strainer 35c.On venting gas appliance 36, connect silencing apparatus (not shown).
In Fig. 3,30p represents spark plug, 30c represents valve camshaft, this valve is arranged in valve mechanism cover 34 with camshaft, drive rotation by bent axle 31c via chain c, 31g represents generator, and this generator has the stator of flexing axle 31c setting and is fixed on the rotor on bent axle 31c in crankcase cover 31e.
As shown in Figure 3, speed changer case (also referred to as casing) 40 as form aforesaid power unit 20 a part casing and form.This casing 40 has right case 40R and the left box body 40L with its combination.Right case 40R and above-mentioned crankcase 31 are made integratedly.At the rear portion of right case 40R, in conjunction with the gearbox cover 40C that forms gear-box (40G), this gear-box (40G) slows down the rotation of countershaft 52 and transmit to rear-wheel spindle 55.
As shown in Figure 3, V belt-type automatic transmission 50 has: the driving pulley 60 being supported by the main shaft 51 as the first belt shaft; The driven pulley 70 being supported by the countershaft 52 as the second belt shaft; The V being erected between above-mentioned driving pulley 60 and driven pulley 70 is with 53.
As shown in Figure 4, Figure 5, the stepless speed variator structure of this mode of execution is as the driving pulley 60 in V belt-type automatic transmission 50.The stepless speed variator structure of this mode of execution is to have fixed pulley 61 and the movable sheave 62 that can move with respect to this fixed pulley 61 and the stepless speed variator structure that volume extension V uses with 53 V belt-type automatic transmission between two pulleys 61,62.
This stepless speed variator structure possesses: the first control mechanism CM1, and it has the first actuator 90 that movable sheave of making 62 moves; The second control mechanism CM2, it cooperates with this first control mechanism CM1, and has the second actuator 100 that movable sheave of making 62 moves.
It should be noted that, in illustrated V belt-type automatic transmission 50, the stepless speed variator structure of this mode of execution is used for to driving pulley 60, but also can be for driven pulley 70 (with reference to Fig. 3).
Below, the structure of V belt-type automatic transmission 50 is described, the stepless speed variator structure of this mode of execution is further described simultaneously.
As shown in Figure 3, Figure 4, in this embodiment, main shaft 51 is made up of an end of aforesaid bent axle 31c.
Bent axle 31c has: by the large-diameter portion 51a of the bearing 31b as bearing components, 31b two supports; On large-diameter portion 51a, arrange and form the minor diameter part 51b of the support of the movable sheave 62 in driving pulley 60 across stepped part 51d.
Main shaft 51 is made up of the minor diameter part 51b of bent axle 31c, and this main shaft 51, the supporting axle of driving pulley 60 is bearing on right case 40R with cantilever position.
As shown in Figure 4, driving pulley 60 has: not along the axially movable fixed pulley of main shaft (belt shaft) 51 (fixing halfbody) 61; Be mounted to respect to main shaft 51 and can move vertically and can not counterrotating movable sheave (movable halves) 62.
The first control mechanism CM1 and the second control mechanism CM2 are for making movable sheave 62 along the support 51b of the belt shaft 51 of the supporting movable sheave 62 of belt shaft 51 to sliding axially, thereby change the well width of belt wheel 60, the i.e. mechanism at fixed pulley 61 and the interval of movable sheave 62.
The first control mechanism CM1 possesses: the movable sheave support 80 that is held in movable sheave 62 via bearing 64; Transmit the power transfering part T of the power of the first actuator 90 to this movable sheave support 80.Power transfering part T is configured in the first actuator 90 sides with respect to the rotating center 62c of movable sheave 62.
Bearing 64 remains in movable sheave 62 via retainer 65 (with reference to Fig. 7), and movable sheave support 80 is supported on movable sheave 62 via bearing 64.66 represent bearing 64 and the snap ring of movable sheave support 80 in conjunction with (engagement).
Power transfering part T possesses the linking member 130 of the front end 91a of the take-off lever 91 that links movable sheave support 80 and the first actuator 90.
The second control mechanism CM2 has the second actuator 100.The second actuator 100 possesses multiple governor weights 101 and cam member 110, wherein, multiple governor weights 101 are configured in around the spin axis of movable sheave 62, this cam member 110 remains on this governor weight 101 between itself and movable sheave 62, and under the effect of the centrifugal force accompanying with the rotation of movable sheave 62, governor weight 101 moves movable sheave 62.Cam member 110 is made up of lamp panel (lamp plate), therefore also cam member 110 is called to lamp panel below.
As shown in Figure 6, movable sheave 62 has lug boss 62b and lip part 62f, between lug boss 62b and lip part 62f, accommodate governor weight 101 (with reference to imaginary line), counterweight accommodation section 62s is and is provided with radially multiple (being illustrated as six).
At counterweight accommodation section 62s, multiple (being illustrated as three) fixing part 62c is set each other, this fixing part 62c has the tapped hole for rigid bearing retainer 65 (Fig. 7).
In addition, be provided with each other multiple (being illustrated as three) directed section 62g at counterweight accommodation section 62s, this directed section 62g is by guide 140 (with reference to imaginary line and Figure 11, Fig. 4 of Fig. 9) guiding being arranged on the guide portion 110g of lamp panel 110 (Fig. 9).
As shown in Figure 7, retainer 65 there is short cylindrical portion 65b, with the lip part 65f of this cylindrical portion 65b one, be arranged on integratedly multiple (being illustrated as three) assembly department 65c of the inner side of lip part 65f.Retainer 65 is by utilizing bolt 65d (with reference to Fig. 4) that assembly department 65c is combined and is fixed in movable sheave 62 with the fixing part 62c of above-mentioned movable sheave 62.Periphery at the cylindrical portion 65b of retainer 65 is installed bearing 64 (Fig. 4).The governor weight 101 that bearing 64 is configured in the second actuator 100 around.
As shown in Figure 8, movable sheave support 80 have ring portion (short cylindrical portion) 81, with the arm 82 of these ring portion 81 one.As shown in Figure 4, ring portion 81 is chimeric with bearing 64, and arm 82 links with linking member 130.To being described later with the connecting arrangement of linking member 130.
As shown in Figure 8, ring portion 81 has: for limiting the lip part 81f with respect to the movement in the axial direction of bearing 64; For the annular slot 81g of snap ring 66 is installed.
As shown in Figure 9, the plate (sheet metal member) that lamp panel (cam member) 110 is overall star, has: the plectane portion 111 of central authorities; Cam part 112, it is radiated entends integratedly from this plectane portion 111, between the counterweight accommodation section 62s of itself and described movable sheave 62, keeps governor weight 101, and this cam part 112 identical with counterweight accommodation section 62s quantity (being illustrated as six); Recess 113, it is for avoiding fixing part 62c, the assembly department 65c of movable sheave 62 and retainer 65; Guide portion 110g, it is provided with described guide 140, guides the directed section 62g (with reference to Fig. 4～Fig. 6) of movable sheave 62 by this guide 140.
The hole 111h that the minor diameter part 51b of feed wheel axle 51 passes is set in plectane portion 111.
Guide portion 110g have the otch 114 of the U-shaped embedding for guide 140, for strengthen this otch 114 periphery guide portion 110g be the rib 115 that U shape erects.
As shown in figure 11, guide 140 is the superior plastic parts of sliding, possess: there is the main body 142 of the cross section U-shaped of the steering channel 141 of cross section U-shaped, the directed section 62g (with reference to Fig. 4～Fig. 6) of this steering channel 141 and movable sheave 62 chimeric become can be to sliding axially; Be arranged on little lip part 143 and the large lip part 144 at the two ends of this main body 142.
As shown in the imaginary line of Fig. 9, this guide 140 embeds main body 142 with the mode of the back side butt of lamp panel 110 with little flange 143 and upper surface butt and the large lip part 144 of the rib 115 of lamp panel 110 to the otch 114 of lamp panel 110, thereby is respectively installed on the guide portion 110g at three positions of lamp panel 110.
The driving pulley 60 with lamp panel 110, movable sheave 62 and movable sheave support 80 etc. as above can be assembled on the minor diameter part 51b of belt shaft 51 as described as follows.
Describe with reference to Fig. 4, first movable sheave support 80 is installed and is utilized snap ring 66 by both engagings in the periphery of bearing 64, at the interior week installation retainer 65 of bearing 64, utilize many (being three (only illustrating one in Fig. 4) in the present embodiment) bolt 65d by retainer 65 and movable sheave 62 combinations, sleeve 67 is inserted to the lug boss 62b of movable sheave 62 via oil sealing 62s and axle collar 62c, each counterweight accommodation section 62s in movable sheave 62 accommodates governor weight 101, each guide portion 110g at lamp panel 110 installs guide 140, the directed section 62g of chimeric movable sheave 62 in the steering channel 141 of above-mentioned guide 140, form in advance thus the assembly body forming in conjunction with movable sheave 62 and lamp panel 110 easily.
Then, first in the hole 111h of the lamp panel 110 in above-mentioned assembly body, pass minor diameter part 51b, then in the sleeve 67 of above-mentioned assembly body, insert minor diameter part 51b, and then at minor diameter part 51b, fixed pulley 61 is installed, and at the front end of minor diameter part 51b, double nut 68 is installed, by this double nut 68 between the stepped part 51d of itself and main shaft 51 by fastening together with lamp panel 110, sleeve 67 and fixed pulley 61, thereby they are fixed on minor diameter part 51b.Thus, driving pulley 60 is assembled on the minor diameter part 51b of belt shaft 51.
In driving pulley 60 as above, owing to being fixed between double nut 68 and the stepped part 51d of main shaft 51 fastening to lamp panel 110, sleeve 67 and fixed pulley 61, therefore lamp panel 110, sleeve 67 and fixed pulley 61 can not carry out axial relatively move and around the relative rotation of axle with respect to belt shaft 51, and rotation together with belt shaft 51.
Movable sheave 62 can be carried out axial relatively move and around the relative rotation of axle with respect to sleeve 67, but because the steering channel 141 of the guide 140 of directed section 62g on the guide portion 110g that is arranged on lamp panel 110 fastening together with above-mentioned is chimeric, therefore can not carry out around the relative rotation of the axle of lamp panel 110, can not carrying out the relative rotation with respect to belt shaft 51.
Thereby movable sheave 62 is rotated together with belt shaft 51, and can moving axially to belt shaft 51.
Movable sheave support 80 can rotate with respect to movable sheave 62 relatively via bearing 64.Thereby movable sheave support 80 may become the state that strip winding wheel shaft 51 does not rotate.
On the other hand, due to stepped part 62h (with reference to Fig. 6) butt in distolateral and a snap ring 66 of bearing 64 and the lip part 62f of movable sheave 62, another distolateral and the lip part 81f of movable sheave support 80 and lip part 65f butt of retainer 65 of bearing 64, movable sheave support 80 can not carry out to axial relatively moving with respect to movable sheave 62 thus.
Thereby, by making movable sheave support 80 to moving axially, can similarly make thus movable sheave 62 to moving axially.
The arm 82 of movable sheave support 80 links by the take-off lever 91 of linking member 130 and the first actuator 90, and under the driving of the first actuator 90, movable sheave support 80 can be to moving axially.
As shown in Figure 4, Figure 5, the first actuator 90 possesses and contains the motor part M1 (Fig. 4) of the motor as driving source (servomotor) M (Fig. 5), the take-off lever 91 as carry-out part moving by the power of motor M, and this take-off lever 91 configures abreast with described main shaft 51.As shown in Figure 5, the first actuator 90 is configured to motor M and is positioned at than linking main shaft 51 position with the top side of line L1 of countershaft 52.
The first actuator 90 possesses the reduction gear row 92 that the power of motor M is transmitted to take-off lever 91.On the gear 92e of the final level of reduction gear row 92 with one heart shape in conjunction with ball screw (outside thread) 93.The base portion side of take-off lever 91 is formed as cylindric, upper ball screw (internal thread) 91b that forms in surface therein, and this internal thread 91b and ball screw (outside thread) 93 screws togather.Thereby while ball screw 93 being rotated via reduction gear row 92 under the driving of motor M, take-off lever 91 moves to axial direction (the arrow X1 in Fig. 4, X2 direction) advance and retreat according to the sense of rotation of ball screw 93.
By screw 95, the gear-box 94 that contains reduction gear row 92 is fastened on to the assembly department (not shown) of being located in casing 40, thereby the first actuator 90 is fixed on to casing.The first actuator 90 both can be arranged on the inner side of casing 40 and be housed in casing 40, also can be arranged on the outside of casing 40.
The first actuator 90 is configured in the second actuator 100 around.
As shown in Figure 4, the front end 91a of take-off lever 91 is more with 53 side-prominent to V than the motor part M1 of the first actuator 90, and from observing with the orthogonal direction of take-off lever 91, at least a portion 91c of this take-off lever 91 is configured in V with in 53 bandwidth W.Motor part M1 is configured in outside bandwidth W.As shown in Fig. 2, Fig. 5, observe from the axial direction of take-off lever 91, take-off lever 91 V with 53 rotating locus in 53i be configured on the line L1 that links main shaft 51 and countershaft 52.As shown in Figure 4, reduction gear row 92 are configured in V with outside 53 bandwidth W, as shown in Figure 5, observe from the axial direction of take-off lever 91, and reduction gear row 92 are configured to be with 53 overlapping with V.
As shown in Figure 4, the first actuator 90 is configured in fixed pulley side, and take-off lever 91 and linking member 130 crosscut V are with 53 line of travel and link with movable sheave support 80.
As shown in Figure 4, Figure 5, power transfering part T, for the power of the first actuator 90 is transmitted to described movable sheave support 80, has above-mentioned linking member 130.
As shown in Fig. 4, Fig. 8, the arm 82 of movable sheave support 80 extends to the first actuator 90 sides (right side Fig. 4) integratedly from a circumferential end of ring portion 81.On arm 82, be provided with a pair of protuberance 83,83 towards take-off lever 91 sides of the first actuator 90.
On the other hand, as shown in Fig. 4, Fig. 5, Figure 10, linking member 130 has: the hook portion with U groove 131 (hook structure) 133 by pin 132 with the front end 91a link of take-off lever 91; The linking department 134 extending towards arm 82 sides of movable sheave support 80 from this hook portion 133.This linking department 134 enters between a pair of protuberance 83,83 in described movable sheave support 80, by pin 84, the linking department of linking member 130 134 and a pair of protuberance 83,83 is linked.Thus, movable sheave support 80 and linking member 130 are linked.U groove 131 is the U grooves to the direction opening intersecting with the advance and retreat direction of take-off lever 91.
If form like this, when linking the front end 91a of hook portion 133 and take-off lever 91 in the time of assembling, or remove both links in the time decomposing when, by utilizing the first actuator 90 and the gap 41c of casing 40 to make the first actuator 90 rotate to make hook portion 133 engage or depart from pin 132 to arrow a, b direction, can easily carry out thus link/releasing of the front end 91a of hook portion 133 and take-off lever 91.
The gap 41c that actuator 90 can be moved that the assembly department of the actuator 90 in casing 40 is provided for that hook portion 133 is engaged or departs from.
The take-off lever 91 of movable sheave support 80 and the first actuator 90 links by linking member 130, thereby in the time that take-off lever 91 advance and retreat of the first actuator 90 are mobile, movable sheave support 80 is also to equidirectional movement, thus by movable sheave 62 also to equidirectional handover.
Linking member 130 can link with movable sheave support 80 rotationally by pin 84, but on movable sheave support 80, the limiting unit 85,86 (with reference to Fig. 8) that limits the rotation of linking member 130 with abutting part 135,136 butts of linking member 130 is set.
By movable sheave support 80 and take-off lever 91 are linked via linking member 130, improve thus the degrees of freedom of the first actuator 90 with respect to the allocation position of movable sheave support 80, but example as shown in Figure 4, exist because of the first actuator 90 is with respect to the allocation position of movable sheave support 80, and movable sheave support 80 and the coupling position of linking member 130 sold 84 position, with respect to the axis of take-off lever 91, situation about being offset occurred.
Such skew can make linking member 130 rotate around pin 84 in the time that take-off lever 91 advance and retreat move, in order to prevent this rotation, the limiting unit 85,86 that limits the rotation of linking member 130 with abutting part 135,136 butts of linking member 130 is set on movable sheave support 80.
By such limiting unit 85,86 is set, transmission of power position between linking member 130 and the movable sheave support 80 that take-off lever 91 can be advanced and retreat when mobile is distributed to position (84) and the limiting unit 85,86 that keying is closed, and therefore can suppress to make the power in direction that movable sheave support 80 tilts.
On casing 40 (being illustrated as right case 40R), be provided with stopper 41s, the 42s of the moving range of regulation movable sheave support 80.Observe from the rotating center (62c) of movable sheave 62, above-mentioned stopper 41s, 42s are arranged near of the linking department (84) of movable sheave support 80 and linking member 130.
One side's stopper 41s is arranged on the internal surface of casing 40 integratedly, be formed as parallel with belt shaft 51 and from the internal surface of casing 40 towards the outstanding column of the arm 82 of movable sheave support 80.One side 80b butt of this stopper 41s and movable sheave support 80, stops the excessive movement of movable sheave support 80 to arrow X1 direction thus.
The opposing party's stopper 42s is for stoping the excessive movement of movable sheave support 80 to arrow X2 direction, and therefore having can be with the abutting part 42t (with reference to Figure 12) of the portion that is limited 87 butts of the convex that arranges on arm 82 at movable sheave support 80, to the assembly department 42c of casing 40.This stopper 42s is by utilizing bolt 42b that assembly department 42c is fixed on cylindric assembly department 42 and is installed on casing 40, and wherein, cylindric assembly department 42 is from internal surface and belt shaft 51 outstanding formation abreast of casing 40.
The scope that the moving range (being the sliding scale that points to X1, X2 direction in this case) of movable sheave support 80 is moved by the advance and retreat of the take-off lever 91 in the first actuator 90 taking servomotor M as driving source specifies, therefore common movable sheave support 80 and not butt of stopper 41s, 42s.
But, owing to existing movable sheave support 80 for example, because some reason (fault of the control system of the first actuator 90) is necessary with Shangdi (exceedingly) mobile situation, therefore in order to prevent this situation, stopper 41s, 42s are set.
The second actuator 100 is formed as foregoing structure, moves as follows.
Driving pulley 60 rotates, when the rotating speed of driving pulley 60 reaches certain when above, with the corresponding centrifugal action of its rotating speed in governor weight 101.Thereby governor weight 101 is according to the rotating speed of driving pulley 60 and to move (maybe will move) away from the direction of belt shaft 51.Here,, owing to accommodating the counterweight accommodation section 62s by movable sheave 62 of governor weight 101 and space S (with reference to Fig. 4) that lamp panel 110 forms along with narrowing away from belt shaft 51, therefore governor weight 101 works in the mode of widening this space S.Because lamp panel 110 can not be to moving axially, on the other hand and movable sheave 62 can be to moving axially, therefore consequently, movable sheave 62 moves under the effect of governor weight 101.
The advance and retreat that the movement of this movable sheave 62 is the take-off lever 91 in the first actuator 90 by the first control mechanism CM1 move to limit.
As shown in Figure 3, the driven shaft of V belt-type automatic transmission 50 is that countershaft 52 rotates on the left box body 40L and gearbox cover 40C that is bearing in freely above-mentioned casing 40.On this countershaft 52, via centrifugal clutch 54, driven pulley 70 is set.
Driven pulley 70 possesses fixed pulley (fixing halfbody) 71 and movable sheave (movable halves) 72.
Be with 53 at aforesaid driving pulley 60 with the added ring-type V that is provided with of driven pulley 70, the rotation of driving pulley 60 is transmitted to driven pulley 70.In the time that the rotating speed of driven pulley 70 exceedes regulation rotating speed, the centrifugal clutch 54 being arranged between driven pulley 70 and countershaft 52 becomes coupled condition, and countershaft 52 starts rotation.
Gear row (gear-box) 40G rotation of countershaft 52 being slowed down and transmit to rear-wheel spindle 55 has the gear 52g being arranged on countershaft 52, the small gear 142 rotating with the gear 141 in the large footpath that this gear 52g engages, than these gearwheel 141 paths and together with gearwheel 141, the gearwheel 143 engaging with this small gear 142.Gearwheel 143 is arranged on rear-wheel spindle 55 and is mounted to and can not relatively rotate.
Thereby, the rotation of countershaft 52 is slowed down and transmits the trailing wheel 15R (Fig. 1) of drive installation on rear-wheel spindle 55 to rear-wheel spindle 55.
Movable sheave 72 in driven pulley 70 is mounted to respect to countershaft 52 and moves freely vertically.Movable sheave 72 by helical spring 73 to the direction application of force that approaches fixed pulley 71, according to acting on V with the tension force on 53 and moving vertically.; when the movable sheave 62 of driving pulley 60 is to the direction displacement of constriction well width and V when hanging diameters and increase with 53 volumes to driving pulley 60 (with reference to Figure 13); correspondingly being wound around V on driven pulley 70 is pulled to driving pulley 60 sides with 53 and acts on V and become large with the tension force on 53; because of the increase at this tension force; the movable sheave 72 of driven pulley 70 is to the direction displacement of widening well width; V hangs diameter with 53 volumes to driven pulley 70 and diminishes, and countershaft 52 is with High Rotation Speed.To widening the direction displacement of well width, carry out contrary action in the movable sheave 62 of driving pulley 60, make countershaft 52 with low speed rotation.
Under the control of not shown control device, make the first actuator 90 move, in Fig. 4, take-off lever 91 is outstanding and when movable sheave 62 is slided to X1 direction to arrow X1 direction, fixed pulley 61 broadens with the interval of movable sheave 62, V hangs with 53 volumes to driving pulley 60 that diameters diminish and V hangs diameter with 53 to the volume that drives driven pulley 70 and becomes large (with 53 velocity ratio step-down), and trailing wheel 15R is rotated with driven at low speed and resists high load.Otherwise, in the time that take-off lever 91 makes movable sheave 62 slide to X2 direction to the slip of arrow X2 direction (with reference to Figure 13), fixed pulley 61 narrows with the interval of movable sheave 62, V hangs diameter change greatly with 53 volumes to driving pulley 60 and V diminishes to the volume extension diameter that drives driven pulley 70 with 53, and trailing wheel 15R is rotated with high-speed driving.
And then in this embodiment, under the control of above-mentioned control device, the first actuator 90 moves as follows.; the first actuator 90 moves as follows; in the low rotary area of the movable sheave 62 of driving pulley 60; produce the equidirectional power of power that will make movable sheave 62 move with the second control mechanism CM2; in the high rotary area of movable sheave 62, to make the power that movable sheave 62 moves produce resistance with respect to the second control mechanism CM2.
Figure 14 is the chart that represents the control example of the first actuator 90, is also the action specification figure of the first control mechanism CM1 and the second control mechanism CM2.(a) chart while being normal mode, the chart while (b) being motor pattern (sports mode).The selection of pattern is undertaken by the mode selection switch or the model selection bar that are arranged on the maneuverable position of driver that rides on vehicle.
In above-mentioned chart, the longitudinal axis in left side adopts the power (thrust (N)) that movable sheave 62 is moved, the longitudinal axis on right side adopts the rotating speed (rpm) of bent axle 31c (motor), and transverse axis adopts the speed of a motor vehicle (km/h).Thrust is made to the direction that movable sheave 62 moves to fixed pulley 61, and (direction (acceleration side) at the interval of constriction two pulleys, the arrow X2 direction setting of Fig. 4 is being for just.
In above-mentioned chart, single-point line (CM1) represents the first control mechanism CM1 thrust that the first actuator 90 produces, dotted line (CM2) represents the second control mechanism CM2 thrust that the second actuator 100 based on governor weight 101 produces, and solid line (CM1+CM2) represents making a concerted effort of above-mentioned thrust.
Under normal mode, as shown in Figure 14 (a), the moment that reaches about S1 (for example about 20km/h) in the speed of a motor vehicle is moved the first actuator 90, for example, above add the thrust (intermediate value (for example about 500N) of P2 and P3) of the first control mechanism CM1 generation and produce the large total thrust (intermediate value (for example about 1100N) of P5 and P6 in the thrust (about P3 (about 600N)) of the second control mechanism CM2 generation, accelerate fast thus (shift up) (band velocity ratio is set in to high side) and realize the raising of fuel availability.
For example, in the time that the speed of a motor vehicle exceedes about S3 (about 60km/h), thrust corresponding with engine speed and that the second control mechanism CM2 produces increases gradually, therefore in order to add up to thrust (CM1+CM2) to be maintained necessarily, and the thrust that the first control mechanism CM1 is produced little by little reduces.
For example, in the time that the speed of a motor vehicle exceedes about S4 (about 80km/h), thrust corresponding with engine speed and that the second control mechanism CM2 produces becomes excessive, therefore will add up to thrust (CM1+CM2) to be maintained necessarily in order to offset this thrust, the thrust that the first control mechanism CM1 (the first actuator 90) is produced is moved to minus side.
Under motor pattern, as shown in Figure 14 (b), the speed of a motor vehicle reach about S4 (for example approximately 80km/h) before the first actuator 90 be failure to actuate.Thereby before the speed of a motor vehicle reaches about S4, the first control mechanism CM1 can not produce thrust (CM1+CM2=CM2).Therefore, accelerate suppressed (band velocity ratio maintains downside), can carry out alert and resourceful travelling.
In the time that the speed of a motor vehicle exceedes about S4, thrust corresponding with engine speed and that the second control mechanism CM2 produces becomes excessive, therefore need to offset this thrust and will add up to thrust (CM1+CM2) to be maintained in necessarily, the thrust that the first control mechanism CM1 (the first actuator 90) is produced is moved to minus side.
According to stepless speed variator structure as above, can play following action effect.
(a) owing to possessing the first control mechanism CM1 and the second control mechanism CM2, the first actuator 90 that the movable sheave of making 62 that has this first control mechanism CM1 moves, the second control mechanism CM2 cooperates with this first control mechanism CM1, and there is the second actuator 100 that movable sheave of making 62 moves, therefore movable sheave 62 move through the first control mechanism CM1 with the first actuator 90 with have the second actuator 100 the second control mechanism CM2 cooperate carry out.
Therefore, increasing when making power that movable sheave 62 moves, this power decentralized can be given to the first control mechanism CM1 with the first actuator 90 and the second control mechanism CM2 (reference example is as Figure 14 (a)) with the second actuator 100.
Thereby, make compared with existing structure that movable sheave moves with utilizing single actuator and single control mechanism, even in the case of increasing for making power that movable sheave 62 moves, also can reduce the load to each actuator 90,100, suppress the maximization of each actuator 90,100, thereby realize on the whole the miniaturization of V belt-type automatic transmission 50.
And, by suppressing the load of each actuator 90,100, can improve thus the durability of each actuator.
And then, the weight of the governor weight of the second actuator 100 101 is set as under normal mode and these two kinds of patterns of motor pattern (with reference to Figure 14 (a), (b)), the necessary maximum thrust roughly equal (approximately-P2～P2) of the first actuator 90, therefore can make respectively the first actuator 90 and the second actuator 100 miniaturizations.
(b) because the first actuator 90 drives by electric power, the second actuator 100 drives by the centrifugal force accompanying with the rotation of movable sheave 62,, the centrifugal force of the rotation of one side's actuator 100 by having utilized movable sheave 62 drives, and therefore can suppress the power consumption of stepless speed variator structural entity and reduce energy loss.
(c) because the first actuator 90 is configured in the second actuator 100 around, therefore two actuators 90,100 can be configured in around the running shaft 51 of driving pulley 60 compactly, improve the configuration degrees of freedom of the first actuator 90.
(d), because the first actuator 90 is configured in V with interior all positions of 53, therefore can effectively utilize and easily become the V of wasted space with interior all space 53i of 53.
(e) because the second actuator 100 possesses multiple governor weights 101 and cam member 110, wherein, multiple governor weights 101 are configured in around the spin axis 62c of movable sheave 62, this cam member 110 remains on this governor weight 101 between cam member 110 and movable sheave 62, under the effect of the centrifugal force accompanying with the rotation of movable sheave 62, governor weight 101 moves movable sheave 62, therefore the second actuator 100 makes square the increasing pro rata of angular velocity of power that movable sheave 62 moves and movable sheave 62
Thereby, can reduce the power that the first actuator 90 moves movable sheave 62, can further suppress power consumption (reference example is as the scope of the speed of a motor vehicle S3～S4km/h in Figure 14 (a)).
In addition, in the time that V belt-type automatic transmission 50 is dismantled, utilize cam member 110 can prevent that governor weight 101 from coming off from the counterweight accommodation section 62s of movable sheave 62, can improve maintenance.
(f) be held in the movable sheave support 80 of movable sheave 62, transmit the power transfering part T of the power of the first actuator 90 to this movable sheave support 80 because the first control mechanism CM1 possesses via bearing 64, this power transfering part T is configured in the first actuator 90 sides with respect to the rotating center 62c of movable sheave 62, therefore power transfering part T miniaturization can be made, thereby the miniaturization of stepless speed variator structure and V belt-type automatic transmission can be realized.
(g) because bearing 64 is configured in governor weight 101 around, therefore can utilize the peripheral space of governor weight 101 to configure bearing 64, although be provided with the first control mechanism CM1 with the first actuator 90 and the second control mechanism CM2 with the second actuator 100, but still can suppress the maximization in the axial direction of stepless speed variator structure and V belt-type automatic transmission device.
(h) the first actuator 90 moves as follows,, at the low rotary area (reference example is as the region of the N3～N7rpm in Figure 14 (a)) of movable sheave 62, produce the equidirectional power of power that will make movable sheave 62 move with the second control mechanism CM2, at the high rotary area (reference example is as the region more than N7rpm in Figure 14 (a)) of movable sheave 62, to make the power that movable sheave moves produce resistance with respect to the second control mechanism CM2.
Thereby at the low rotary area of movable sheave 62, what produce by the first control mechanism CM1 and the second control mechanism CM2 moves movable sheave 62 to unidirectional power, therefore can movable sheave 62 be moved swimmingly by two control mechanisms.
On the other hand, at the high rotary area of movable sheave 62, the mode that the first actuator 90 becomes resistance with the power that will make movable sheave 62 move with respect to the second control mechanism CM2 is moved, and therefore can suppress the excessive movement of the movable sheave 62 that the second control mechanism CM2 causes, i.e. excessive gear shifting operation.
(i) because more than 101 decentralized configuration of governor weight is around the rotating center 62c of movable sheave 62, therefore can reduce with respect to the distortion of the movable sheave 62 of the inclination of movable sheave 62 or to the load of the first actuator 90, the counter-force of the band that wherein inclination of movable sheave 62 is born due to half circumferential portion of movable sheave 62 produces.
(j) owing to utilizing the linking member 130 with the U groove 131 linking with this front end 91a to link by be held in the movable sheave support 80 of movable sheave 62 and the front end 91a of take-off lever 91 via bearing 64, therefore, can form the power transfer member that the power of take-off lever 91 is transmitted to movable sheave 62 by movable sheave support 80 and linking member 130.
This power transfer member 80,130 is different from aforesaid fork member of the prior art (300), does not need to be bearing on engine case, therefore can improve assembling performance and assembling space.
And linking member 130 carries out via the U groove 131 of linking member 130 with the link of the front end of take-off lever 91, therefore can further improve assembling performance.
(k) because actuator 90 is configured in fixed pulley 61 sides, take-off lever 91 and linking member 130 crosscut V are with 53 line of travel and link with movable sheave support 80, therefore can effectively utilize and easily become the inner space 53i of the V of wasted space with 53 line of travel.Thereby, can make stepless speed variator miniaturized structure.
(l) linking member 130 links with respect to movable sheave support 80 and the circumferential end (arm 82) in this movable sheave support 80, and there is the hook structure that forms U groove 131, therefore can easily carry out by the opening of the U groove 131 of hook structure the assembling/dismounting of linking member 130 and take-off lever 91.
(m) because the U groove 131 of linking member 130 is to the U groove of the direction opening intersecting with the advance and retreat direction of take-off lever 91, therefore the power of the advance and retreat of take-off lever 91 two directions can be transmitted to movable sheave 80 via linking member 130.Therefore, can carry out swimmingly mobile control the in two directions of movable sheave 80.
(n) because V belt-type automatic transmission 50 possesses the left box body 40L as speed changer cover that covers crankcase 31, on this speed changer cover 40L, actuator 90 is installed, actuator 90 can be configured in thus to the opposition side of crankcase 31 with respect to movable sheave 62.Therefore, the degrees of freedom of configuration is improved, and actuator 90 can be approached to the rotating center 62c configuration of driving pulley 62.Thereby, can realize the further miniaturization of stepless speed variator structure.
(o) by actuator 90 being approached to the rotating center 62c configuration of driving pulley 62, actuator 90 can be approached thus to pivot 12 configuration around, therefore can reduce load under spring.
(p) because linking member 130 is connected to and can be rotated by pin 84 and movable sheave support 80, the limiting unit 85,86 that limits the rotation of linking member 130 with linking member 130 butts is set on movable sheave support 80, therefore can close the link of easily carrying out linking member 130 and movable sheave support 80 by pin joint, and the transmission of power position between linking member 130 and movable sheave support 80 can be disperseed to position and the limiting unit 85,86 of closing to keying, therefore can suppress to make the power in direction that movable sheave support 80 tilts.
(q) observe from the rotating center (62c) of movable sheave support 80, stopper 41s, the 42s of the movement in the axial direction of restriction movable sheave support 80 is arranged near of the linking department of movable sheave support 80 and linking member 130, therefore can reduce movable sheave support 80 with stopper 41s, 42s butt time, act on the warping force on movable sheave support 80, and can centralized configuration stopper funtion part, thereby make speed change gear miniaturization.
Above, embodiments of the present invention are illustrated, but the present invention is not limited to above-mentioned mode of execution, can in the scope of purport of the present invention, be suitably out of shape enforcement.
Claims (6)
1. a stepless speed variator structure, it is to have fixed pulley and the movable sheave that can move with respect to this fixed pulley and hang with the stepless speed variator structure that the V belt-type automatic transmission that is equipped on small size motorcycle of V band is used at two pulley rooms volumes, wherein, described fixed pulley is supported by the belt shaft that points to overall width direction, described stepless speed variator structure is characterised in that to possess:
The first control mechanism, it has the first actuator that described movable sheave is moved;
The second control mechanism, it cooperates with described the first control mechanism, and has the second actuator that described movable sheave is moved,
Described the first actuator is to have by the advance and retreat actuator of mobile take-off lever of electric power, and described take-off lever and described belt shaft configure abreast, and described the first control mechanism possesses: the movable sheave support that is held in described movable sheave via bearing; Transmit the power transfering part of the power of described the first actuator to this movable sheave support,
Described the second actuator drives by the centrifugal force accompanying with the rotation of described movable sheave, and described the second actuating device is for multiple governor weights and cam member, the plurality of governor weight is configured in around the spin axis of described movable sheave, this cam member remains on this governor weight between itself and described movable sheave, under the effect of the centrifugal force accompanying with the rotation of described movable sheave, described governor weight is moved, make thus described movable sheave move up in described spin axis side
Described bearing is disposed at the peripheral of the described governor weight around described spin axis, and is held in described movable sheave via retainer,
Described movable sheave has lug boss and lip part, the counterweight accommodation section of accommodating described governor weight between this lug boss and lip part is and is provided with radially multiplely, is provided with each other the fixing part for fixing described retainer in multiple described counterweights accommodation section.
2. stepless speed variator structure according to claim 1, is characterized in that,
Described the first actuator is configured in described the second actuator around.
3. stepless speed variator structure according to claim 2, is characterized in that,
Described the first actuator is configured in interior all positions of described V band.
4. according to the stepless speed variator structure described in any one in claim 1～3, it is characterized in that,
Described the first control mechanism possesses via bearing and is held in the movable sheave support of described movable sheave, transmits the power transfering part of the power of described the first actuator to this movable sheave support, and this power transfering part is configured in described the first actuator side with respect to the rotating center of described movable sheave.
5. according to the stepless speed variator structure described in any one in claim 1～3, it is characterized in that,
Described the first actuator is the actuator moving as follows,, at the low rotary area of described movable sheave, produce the equidirectional power of power that will make described movable sheave move with described the second control mechanism, at the high rotary area of described movable sheave, to make the power that described movable sheave moves produce resistance with respect to described the second control mechanism.
6. stepless speed variator structure according to claim 4, is characterized in that,
Described the first actuator is the actuator moving as follows,, at the low rotary area of described movable sheave, produce the equidirectional power of power that will make described movable sheave move with described the second control mechanism, at the high rotary area of described movable sheave, to make the power that described movable sheave moves produce resistance with respect to described the second control mechanism.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2010-190831 | 2010-08-27 | ||
| JP2010190831A JP5506601B2 (en) | 2010-08-27 | 2010-08-27 | Continuously variable transmission structure |
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| Publication Number | Publication Date |
|---|---|
| CN102384234A CN102384234A (en) | 2012-03-21 |
| CN102384234B true CN102384234B (en) | 2014-12-10 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201110242898.XA Expired - Fee Related CN102384234B (en) | 2010-08-27 | 2011-08-23 | Step-less variator structure |
Country Status (3)
| Country | Link |
|---|---|
| JP (1) | JP5506601B2 (en) |
| CN (1) | CN102384234B (en) |
| IT (1) | ITTO20110771A1 (en) |
Families Citing this family (16)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US9101377B2 (en) | 2007-01-25 | 2015-08-11 | Biolase, Inc. | Electromagnetic energy output system |
| JP5852915B2 (en) * | 2012-03-30 | 2016-02-03 | 武蔵精密工業株式会社 | V belt type continuously variable transmission |
| JP5960474B2 (en) * | 2012-03-30 | 2016-08-02 | 武蔵精密工業株式会社 | V belt type continuously variable transmission |
| JP2014196780A (en) * | 2013-03-29 | 2014-10-16 | 武蔵精密工業株式会社 | V-belt type stepless transmission |
| EP2784357B1 (en) | 2013-03-29 | 2016-02-17 | Musashi Seimitsu Industry Co., Ltd. | V-belt continuously variable transmission |
| JP6144517B2 (en) * | 2013-03-29 | 2017-06-07 | 武蔵精密工業株式会社 | V belt type continuously variable transmission |
| CN106461035B (en) * | 2014-03-31 | 2019-05-28 | 庞巴迪动力产品公司 | The driving pulley of stepless transmission |
| JP6120334B2 (en) * | 2014-08-06 | 2017-04-26 | 本田技研工業株式会社 | V-belt continuously variable transmission for vehicles |
| JP6108314B2 (en) | 2014-08-18 | 2017-04-05 | 本田技研工業株式会社 | V-belt continuously variable transmission for vehicles |
| DE102015203901A1 (en) * | 2015-03-05 | 2016-09-08 | Robert Bosch Gmbh | CVT transmission with improved controllability |
| TWI567317B (en) * | 2015-03-31 | 2017-01-21 | 三陽工業股份有限公司 | Multi-mode continuously variable transmission mechanism |
| ITUB20156895A1 (en) * | 2015-12-10 | 2017-06-10 | Piaggio & C Spa | TRANSMISSION DEVICE WITH CONTINUOUS CHANGE WITH CHANGE ADJUSTMENT DEVICE |
| JP6470723B2 (en) * | 2016-10-06 | 2019-02-13 | 株式会社エフ・シー・シー | Continuously variable transmission |
| WO2018073882A1 (en) * | 2016-10-18 | 2018-04-26 | 本田技研工業株式会社 | Manufacturing method for drive pulley and manufacturing system therefor, roller assembly device, piece attachment device and boss insertion device |
| JP6706381B2 (en) * | 2017-03-16 | 2020-06-03 | 本田技研工業株式会社 | Belt type continuously variable transmission |
| JP6657274B2 (en) * | 2018-02-07 | 2020-03-04 | バンドー化学株式会社 | Weight roller, method for manufacturing the same, and mold used for manufacturing the weight roller |
Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1900554A (en) * | 2005-07-20 | 2007-01-24 | 本田技研工业株式会社 | V-belt type continuous speed changing transmission |
| CN1977121A (en) * | 2004-06-28 | 2007-06-06 | 雅马哈发动机株式会社 | Belt type continuously variable transmission for saddle-riding type vehicle and saddle-riding type vehicle |
| CN101796326A (en) * | 2007-09-05 | 2010-08-04 | 日本精工株式会社 | Continuously variable transmission, actuator, and intermediate terminal |
Family Cites Families (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS601453A (en) * | 1983-06-14 | 1985-01-07 | Mitsuboshi Belting Ltd | Control of revolution by v-belt type speed change system |
| JPH1151133A (en) * | 1997-08-06 | 1999-02-23 | Tochigi Fuji Ind Co Ltd | Shift device |
| JP2004278725A (en) * | 2003-03-18 | 2004-10-07 | Honda Motor Co Ltd | Continuously variable transmission for vehicle |
-
2010
- 2010-08-27 JP JP2010190831A patent/JP5506601B2/en not_active Expired - Fee Related
-
2011
- 2011-08-19 IT ITTO20110771 patent/ITTO20110771A1/en unknown
- 2011-08-23 CN CN201110242898.XA patent/CN102384234B/en not_active Expired - Fee Related
Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1977121A (en) * | 2004-06-28 | 2007-06-06 | 雅马哈发动机株式会社 | Belt type continuously variable transmission for saddle-riding type vehicle and saddle-riding type vehicle |
| CN1900554A (en) * | 2005-07-20 | 2007-01-24 | 本田技研工业株式会社 | V-belt type continuous speed changing transmission |
| CN101796326A (en) * | 2007-09-05 | 2010-08-04 | 日本精工株式会社 | Continuously variable transmission, actuator, and intermediate terminal |
Non-Patent Citations (2)
| Title |
|---|
| JP特开2004-278725A 2004.10.07 * |
| JP特开平11-51133A 1999.02.23 * |
Also Published As
| Publication number | Publication date |
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| JP2012047292A (en) | 2012-03-08 |
| CN102384234A (en) | 2012-03-21 |
| ITTO20110771A1 (en) | 2012-02-28 |
| JP5506601B2 (en) | 2014-05-28 |
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