CN1199832A - Automatic speed variator for V shape leather belt - Google Patents

Abstract

A V-belt automatic transmission, in which a bearing lying between these cylindrical shafts 61a and 62a of both the pulley half bodies 61 and 62 is composed of a cylindrical sliding member 65 which is supported by an inner circumferential surface of the cylindrical shaft 62a of the movable pulley hald body 62, and it is equipped with a sliding body part provided with self-lubricity consisting of synthetic resins, and the sliding body part makes its wall thickness compensate a dimensional variation due to heat of the cylindrical shaft 62a of the movable pulley half body 62, and thus it is formed into a thin wall so as to make the bearing clearance between these cylindrical shafts come to being nearly constant.

Description

The vee-belt automatic speed variator

The application's invention relates to the middle vee-belt automatic speed variators that adopt such as two-wheeled motor vehicle, particularly relate to a kind of like this vee-belt automatic speed variator, the variation of the bearing play between their each Cylindorical rods that this vee-belt automatic speed variator causes by the thermal distortion of eliminating by the fast pulley halfbody of its slave end and movable half-pulley, improve the durability of bearing, eliminate whirling vibration between two half-pulley etc.

The vee-belt automatic speed variator, be between drive pulley and driven pulley, to set up the ring-type vee-belt that the cross section is the V font, automatically increase and decrease the effective radius of two belt pulleys and the transferring power device according to engine speed, each belt pulley vee-belt is clamped in the fast pulley halfbody and the movable half-pulley that can slide vertically between, change effective radius by the relative axial position of movable half-pulley relative fixed half-pulley.

Usually, by spring movable half-pulley is loaded so that make it near fast pulley halfbody one side, and the effective radius ground effect that strengthens the vee-belt of clamping, give vee-belt with tension force, but when load change is big, the loading force deficiency that spring produced, skid thereby between belt pulley and belt, produce, so proposed a kind of like this example of vee-belt automatic speed variator, wherein had the torque cam mechanism mechanism that utilizes the fast pulley halfbody and the relative rotation of movable half-pulley to become the end thrust of movable belt pulley.

As the example of such scheme, the applicant proposed the special patent application (with reference to Figure 24) of being willing to flat 8-101187 number in the past.In the invention of this application, aforementioned torque cam mechanism mechanism is by the movable side cam part 062c that extends vertically from the end of the Cylindorical rod 062a of movable half-pulley 062 and form, with extend and fixed side cam part 075 formation that forms and engage with aforementioned movable side cam part 062c with being meshed along radial direction in the end periphery of the Cylindorical rod 061a of fast pulley halfbody 061, and these movable side cam part 062c and fixed side cam part 075 are the tendency that diminishes in the gap of sense of rotation, whereby, level and smooth sense of acceleration can be obtained, the good vee-belt automatic speed variator of maintenance of torque cam mechanism mechanism can be obtained.In same figure, the 022nd, gear reduction unit, the 045th, speed reducer input shaft, the 047th, rear axle shaft.

Yet, in this scheme, not the deterioration that the thermal expansion of the bearing 027 between each Cylindorical rod 061a, 062a of two half-pulley 061,062 is caused wear resistance performance with and supporting give sufficient consideration.In other words, when each half-pulley 061,062 is shaped by the aluminium cast inblock, as the bearing material between each Cylindorical rod 061a, 062a of two skins wheel halfbody 061,062, can consider to use and in Japanese patent laid-open 4-258559 communique, also carry out disclosed lubricity synthetic resin, but by the bearing that such material constitutes, compare very softly with metal bearing, and thermal expansion is also big, so abrasion easily under some service condition, so wish to make its durability to improve.

In addition, though also considered on the bearing portion slip surface between each Cylindorical rod 061a, 062a of two half-pulley 061,062 that constitute by aluminium, coating is also opened disclosed hardening oxidation aluminium coating in the clear 53-107780 communique in fact at Japan Patent, but in this scheme, the thermal expansion of each Cylindorical rod 061a, 062a is not considered, thereby caused the whirling vibration of 061,062 of two half-pulley by the variation of bearing play.

In addition, with regard to the bearing device of the bearing 027 between each Cylindorical rod 061a, 062a of two half-pulley 061,062, always or fully not considering, also is to be provided with to be used for preventing the back-up ring (with reference to Japanese patent laid-open 4-224345 communique) that comes off on the inner peripheral surface of the tip side of the Cylindorical rod 062a of movable half-pulley 062 even perhaps consider.In the former occasion, the danger that has bearing to come off, and in the latter's occasion, the Cylindorical rod 062a tip side of movable half-pulley 062 must increase wall thickness, the degree that this wall thickness increases is suitable with the aequum that is provided with when preventing to come off with back-up ring.

So, if the tip side wall thickness of the Cylindorical rod 062a of movable half-pulley 062 increases, the then invention of applying for as former the applicant, be formed at two half-pulley 061 in torque cam mechanism mechanism, each Cylindorical rod 061a of 062, the occasion of the tip side of 062a, it is big that the radius of movable side cam part 062c becomes, the result, in the constant occasion of the moment of torsion that acts on portion of torque cam mechanism mechanism, because the cam force (movable side cam part 062c pushes away the power of fixed side cam 075 along sense of rotation) that produces in this one diminishes, its axial component also diminishes, so that movable half-pulley 062 diminishes near the pushing force of fast pulley halfbody 061, be necessary to set the spring load of the spring 080 of loading for movable half-pulley 062 more greatly along same direction.If spring load is set more greatly, the durability that then causes often being clamped in the vee-belt 055 of 061,062 of two half-pulley by this spring load reduces.

And, in the invention of former the applicant's application, the drive plate 072 of the clutch 070 that cooperates at the end of the Cylindorical rod 061a of fast pulley halfbody 061 061b upper spline prevent to come off with back-up ring 078, use the baffle ring of common opening ring-type, therefore, when effect centrifugal force, then make enlarged-diameter, thus be necessary to come fastening so that tolerate centrifugal force with excessive fastening force, so the assembling performance variation.In addition, for the material that obtains proof stress is implemented the selection of material and processing etc., in making, it takes time and energy very much.In addition, if prevent to come off, then need special space in this part with nut.

In addition, in the invention of former the applicant's application, the shape of the root 061d of the Cylindorical rod 061a of fast pulley halfbody 061, do not make the shape that to disperse stress effectively in this position generation, therefore, the shape at this position becomes big on the size because will guarantee intensity.

The application's invention is finished in view of above-mentioned all problems, its purpose is the durability of the bearing 027 between each Cylindorical rod 061a, 062a of fixing by improving, movable two half-pulley 061,062, provide the tip side of Cylindorical rod 061a, the 062a of two half-pulley 061,062 not form and also can prevent device that this bearing 027 comes off etc. in heavy wall ground, seek the raising, miniaturization, lightweight of the durability of structures of driven pulley side of vee-belt automatic speed variator and performance etc.

For reaching aforementioned purpose, the invention of the application's claim 1 is a kind of vee-belt automatic speed variator, this vee-belt automatic speed variator has by aluminium and integrally is shaped and axle is bearing in fast pulley halfbody on the running shaft, and integrally be shaped by aluminium, mutually opposed with the aforementioned fixation half-pulley, axle is bearing in movable half-pulley on the Cylindorical rod of this fast pulley halfbody sliding freely for clamping V shape belt, and in the distolateral torque cam mechanism mechanism that has of the Cylindorical rod of aforementioned two half-pulley, this cam mechanism can become aforementioned movable half-pulley the end thrust of this movable half-pulley to relatively rotating of aforementioned fixation half-pulley; It is characterized in that: the bearing between the Cylindorical rod of aforementioned fixation half-pulley and the Cylindorical rod of aforementioned movable half-pulley is made of columnar slide member, this slide member is supported on the inner peripheral surface of Cylindorical rod of aforementioned movable half-pulley, have the slip body that constitutes by synthetic resin with self lubricity, this slip body forms thin-walled, its wall thickness can compensate the dimensional changes that produces because of being heated of the Cylindorical rod of the Cylindorical rod of aforementioned fixation half-pulley and aforementioned movable half-pulley, makes the bearing play between these Cylindorical rods constant substantially.

The invention of claim 1 is owing to constitute as aforementioned, even so be out of shape because of thermal expansion by integrally formed fast pulley halfbody of aluminium and movable half-pulley, bearing play between their each Cylindorical rod broadens, also constitute by slide member with slide part owing to bearing, this slide part has bigger rates of thermal expansion, the synthetic resin that is formed by thin-walled ground constitutes, and has a self lubricity, thereby this bearing is inflatable to remedy broadening of this bearing play, so it is constant substantially that this bearing play can often keep, eliminated the abrasion of bearing, its durability improves.In addition, do not produced whirling vibration between two half-pulley yet.

In addition, by as the invention of claim 2, constituting the invention of claim 1, can obtain the bearing of highly heat-resistant and excellent corrosion resistance.

In addition, by as the invention of claim 3, constituting the invention of claim 1 or 2, there is no need on the distolateral inner peripheral surface of the Cylindorical rod of the movable half-pulley that torque cam mechanism mechanism is set to be provided with the back-up ring that comes off of preventing that is used for supporting the slide member that constitutes bearing, therefore, there is no need the Cylindorical rod that heavy wall ground forms the movable half-pulley in this part, so can reduce its external diameter, thereby can reduce the radius of the movable side cam part of the torque cam mechanism mechanism that on its tip side, forms.The result, it is big that the cam force that produces in this portion of torque cam mechanism mechanism becomes, it is big that its axial component also becomes, so can be making movable half-pulley set smallerly, thereby the durability of the vee-belt of clamping between these two half-pulley be improved near the spring load that fast pulley halfbody side ground loads.

Fig. 1 is the overall side view of the scooter that is suitable for of the application's claim 1 a to embodiment's the vee-belt automatic speed variator of invention described in the claim 3.

Fig. 2 is the power plant sectional view along the intercepting of the II-II line among Fig. 1.

Fig. 3 is the partial sectional view at the power plant rear portion among Fig. 2.

Fig. 4 is among the embodiment of Fig. 1, the side view of movable half-pulley.

Fig. 5 is the sectional view along the intercepting of the V-V line among Fig. 4.

Fig. 6 be movable half-pulley variation, with Fig. 4 in same figure.

Fig. 7 is among the embodiment of Fig. 1, the sectional view of fast pulley halfbody.

Fig. 8 is the enlarged view of the contour shape of the VIII portion among Fig. 7.

Fig. 9 is among the embodiment of Fig. 1, the sectional view of spring guide sleeve.

Figure 10 is among the embodiment of Fig. 1, the bearing sectional view of sleeve.

Figure 11 is the enlarged view of the XI portion among Figure 10.

Figure 12 is among the embodiment of Fig. 1, is used for illustrating the figure of bearing with the effect of sleeve.

Figure 13 is among the embodiment of Fig. 1, the plan view of the back-up ring that prevents to come off.

Figure 14 is its side view.

Figure 15 is among the embodiment of Fig. 1, the side view of drive plate.

Figure 16 is the sectional view along the intercepting of the XVI-XVI line among Figure 15.

Figure 17 is the sectional view along the intercepting of the XVII-XVII line among Figure 15.

Figure 18 is among the embodiment of Fig. 1, the unfolded drawing of the jointing state of expression fixed side cam part and movable side cam part.

Figure 19 is among the embodiment of Fig. 1, the figure of the relation of the expression engine speed and the speed of a motor vehicle.

Figure 20 is the variation of expression fixed side cam part and the unfolded drawing of the engagement of movable side cam part, be with Figure 18 in same figure.

Figure 21 is among the embodiment of Fig. 1, prevents to come off with the plan view of wire type back-up ring.

Figure 22 is its side view.

Figure 23 is the enlarged view of XXIII portion among Fig. 3.

Figure 24 is the sectional view of the belt sheave structure of expression prior art.

Below, just the claim 1 of the application shown in Fig. 1 to Figure 23 describes to an embodiment of invention described in the claim 3.

Fig. 1 is the overall side view of the small-sized wheel car 1 that rubs that the vee-belt automatic speed variator in the present embodiment is suitable for.

This scooter 1, Vehicular body front 2 is connected through low level tread portion 4 with rear vehicle 3, extend downwards after the rearward horizontally extending vehicle frame 5 of tread portion 4 erects from the tread portion rear end from Vehicular body front 2, and then rearward oblique upper extends to the rear end to inclination.

In the front portion of vehicle frame 5, have bogie car 6 in the upper end, the front fork 8 that supports front-wheel 7 with axle in the lower end with pivot suspension.

At the rear of vehicle frame 5 rising portions, swing up and down pivot suspension freely through connecting rod 10 and in the rear end front end bottom, between the rear upper surface of these power plant 20 and the vehicle frame above it 5, clamping posterior bumper 11 with the oscillating power device 20 of axle supporting wheels 9.

Vehicular body front 2 usefulness legs retaining 15 is covered with, and is laying footrest 16 on tread portion 4, and rear vehicle 3 usefulness car body covers 17 are covered with, and on the top of this car body cover 17 seat 18 are being set.

In power plant 20, forwardly this vee-belt automatic speed variator 23 of Pei Zhi single cylinder 2 circulation engines 21, the gear reduction unit 22 that is equipped with at the rear portion and configuration between internal-combustion engine 21 and gear reduction unit 22 is housed in by unitization in the machine unit shell 25.

The structural diagrams of power plant 20 is in Fig. 2.

Machine unit shell 25 comprises: accommodating vee-belt automatic speed variator 23 and gear reduction unit 22 and double as is left side housing 26 internal-combustion engine 21 crankcase left sides, long extension on fore-and-aft direction, be engaged in the anterior of this left side housing 26 and constitute the right side housing 27 of crankcase right-hand part, cover the transmission case cover 28 of the left side side of aforementioned left side housing 26, and gear-box 29 formations that cover gear reduction unit 22 from the left side.

In the crankcase that forms by left side housing 26 and right side housing 27, bent axle 31 is being supported in right a pair of main bearing 30,30 rotations that keep left freely, above this crankcase, engaging cylinder block 21a, cylinder head 21b successively, the assembly body of being made up of them a little hypsokinesis vertically is built in the top.

The piston 32 that slides in cylinder block 21a is linked to bent axle 31 through connecting rod 33.

At the right-hand member of bent axle 31, alternator 34 and cooling fan 35 are being set, engine hood 36 is covered with internal-combustion engine 21, the periphery of alternator 34 and cooling fan 35.

At the left end of bent axle 31, the drive pulley 40 of vee-belt automatic speed variator 23 is being set.In this drive pulley 40, the fast pulley halfbody 41 and the movable half-pulley 42 that is bearing in sliding freely vertically on the bent axle 31 of left end that is fixed in bent axle 31 is opposed mutually, in movable half-pulley 42 and be fixed between the pitch 43 of bent axle 31 to move along radial direction and accommodating a plurality of centrifugal weights 44 freely.

, make movable half-pulley 42 near fast pulley halfbody 41, thereby can strengthen the effective radius of the vee-belt 55 that is clamped in 41,42 of two half-pulley to the moving of centrifugal direction by centrifugal weight 44.

On the other hand, the rear portion and the gear reduction unit 22 in the gear-box 29 that are configured in left side housing 26 are such as shown in Figure 3, between speed reducer input shaft 45 and rear axle shaft 47, jack shaft 46 is set as speed reducer output shaft, on the input gear 48 of speed reducer input shaft 45, meshing the large diameter intermediate gear 49 of stationary fit in stationary fit in jack shaft 46, on the intermediate gear 50 of the minor diameter of same jack shaft 46, meshing the output gear 51 of stationary fit in stationary fit, constituting reducing gear in rear axle shaft 47.

Such as illustrated in Figure 3, on left side speed reducer input shaft 45, perforation gear-box 29 of this gear reduction unit 22, driven pulley 60 and clutch 70 are being set.

Driven pulley 60 is made of mutual opposed a pair of fast pulley halfbody 61 that is all aluminum and movable belt pulley 62.

Such as illustrated in Figure 7, in fast pulley halfbody 61, the interior perimembranous of main body is extended vertically, form the 61a of inner sleeve portion cylindraceous (Cylindorical rod), the end of the 61a of this inner sleeve portion forms slightly undergauge and process zigzag assembly department 61b on periphery, and is provided for preventing the circlip groove 61c that wire type back-up ring that the drive plate 72 of following clutch 70 comes off is 78 that cooperated, the cross section is the semicircle arcuation substantially in the end of this assembly department 61b.This fast pulley halfbody 61, from main body to assembly department 61b, by aluminium die casting cast form integrally.

In addition, at the root 61d of the 61a of inner sleeve portion of this fast pulley halfbody 61, the tension force of vee-belt 55 produces very big stress, so always, this part forms large scale in order to ensure intensity, thereby makes weight become heavy.But in the present embodiment, be to form such shape, promptly among the curve of a plurality of curvature of the cross section contour that constitutes this part, with the apex angle (α of the tangent line of the contact of a curve of curvature maximum ₁, α ₂Deng) be predetermined angle above (with reference to Fig. 7, Fig. 8).

So, can under the situation of the basic shape of the fast pulley halfbody 61 that does not change prior art, be dispersed in the stress that root 61d produces effectively, keep the intensity of this one, so can obtain the intensity of this one by littler size shape, can seek miniaturization, the lightweight of fast pulley halfbody 61.

In the present embodiment, in the outer diameter D of the 61a of inner sleeve portion of fast pulley halfbody 61 ₁=34mm, the outer diameter D of the main part of fast pulley halfbody 61 ₂=118mm, the maximum dimension D of root 61d ₃=45mm, the thickest t=5mm of the main part of fast pulley halfbody 61, main part angle of inclination beta=15 °, the maximum curvature R of the profile line of root 61d ₃During=5.5mm, as make α 〉=90 °, then can be dispersed in the stress that root 61d produces most effectively.At this moment, with the maximum curvature R of root 61d ₃The profile curvature of a curve R of the profile line adjacency of=5.5mm ₁, R ₂Be R ₁=2.2mm, R ₂=2.0mm.

On the other hand, in movable half-pulley 62, as illustrated among Fig. 4 and Fig. 5, the interior perimembranous of main body is extended vertically, form internal diameter cylindraceous outer sleeve portion (Cylindorical rod) 62a more bigger than the 61a of inner sleeve portion of aforementioned fixation half-pulley 61, in the end of the 62a of this outer sleeve portion, equally spaced outstanding vertically formation cross section is circular-arc projection 62b to circumferencial direction in 3 places, the front end of this projection 62b is crooked along clockwise direction in Fig. 4, forms movable side cam part 62c.On this movable side cam part 62c, form export-oriented camming surface 62co that the front/rear end of circumferencial direction tilts and interior to camming surface 62ci,

In the present embodiment, though with rotation opposite direction (clockwise direction in Fig. 4) leg-of-mutton bulge is set respectively 3 movable side cam part 62c upper edges, form interior to camming surface 62ci, but since should in be the relative rotation that is used to limit with following fixed side cam part 75 to camming surface 62ci, do not acting on heavy load, even, form interior to camming surface 62ci also enough (with reference to Fig. 6) so only on the movable side cam part 62c of in 3 bulge is set.

Aforementioned movable half-pulley 62, from main body to movable side cam part 62c, by aluminium die casting cast form integrally.

Moreover the outer part of the root of the 62a of outer sleeve portion in the main body of movable half-pulley 62 forms annular groove 62d.And, in the main body of movable half-pulley 62 perimembranous, with the end of the opposite side of the 62a of outer sleeve portion, the setting circlip groove 62e that back-up ring 66 (with reference to Figure 13, Figure 14) can be packed into that prevents to come off, this back-up ring 66 is used for preventing the bearing hereinafter addressed with the coming off of sleeve 65, and this bearing is installed between the 61a of inner sleeve portion of the 62a of outer sleeve portion of this movable half-pulley 62 and fast pulley halfbody 61 with sleeve 65.

Because this back-up ring 66 that prevents to come off uses the wire type back-up ring as illustrated among Figure 13 and Figure 14, so with the drive plate 72 of the clutch of hereinafter addressing 70 prevent come off same with wire type back-up ring 78, when it is engaged among the circlip groove 62e, by its elastic recovering force, the pushing bearing shoulder of the right-hand member of sleeve 65, end direction along the 62a of outer sleeve portion loads to it, so can prevent positively that it from coming off.

As the above driven pulley that constitutes 60 in, such as illustrated in Figure 3, the 61a of inner sleeve portion of fast pulley halfbody 61 is decelerated machine input shaft 45 and connects, and is bearing in freely on this speed reducer input shaft 45 through needle bearing 63 and ball bearing 64 rotations; And the 62a of outer sleeve portion of movable half-pulley 62 is bearing in sleeve 65 sliding freely through bearing on the periphery of the 61a of inner sleeve portion of aforementioned fixation half-pulley 61, and supports thereon with the pivot form.

Movable half-pulley 62 is in the opposed to each other position of main body with respect to fast pulley halfbody 61, and can slide relatively vertically and along the circumferential direction be supported rotationally.

In the present embodiment, aforementioned bearings is with illustrating among the detailed structure of sleeve (slide member) 65 such as Figure 10 and Figure 11, on steel surface, implement the back of the body metal part 65a that copper facing forms, the fixing slip body 65b layer with self lubricity that is made of synthetic resin (teflon) forms thin walled structures thus on the inner peripheral surface of this back of the body metal part 65a layer.This by the two-layer bearing that constitutes sleeve 65, be pressed into aforementioned movable half-pulley 62 the 62a of outer sleeve portion inner peripheral surface and remain in wherein, the surface layer of its slip body 65b leans on the outer circumferential face sliding contact smoothly of the 61a of inner sleeve portion of its self lubricity and aforementioned fixation half-pulley 61, thereby movable half-pulley 62 is bearing on the fast pulley halfbody 61 smoothly.In Figure 11,65c is used to make slip body 65b to be easy to be fixed on the sinter layer of carrying on the back on the metal part 65a.

And, since aforementioned bearings with the rates of thermal expansion of the slip body 65b layer of sleeve 65 greater than as two half-pulley 61, the aluminium of 62 constituent materials, and form the thin-walled of predetermined thickness, even so the dimensional changes b that the internal diameter of the 62a of outer sleeve portion of dimensional changes a that the external diameter of the 61a of inner sleeve portion of fast pulley halfbody 61 produces because of being heated and movable half-pulley 62 causes because of being heated (a＜b) the bearing play c between these interior external diameters is enlarged, also can just compensate the expansion of this extensive magnitude d, this bearing play c is remained in originally constant substantially size (with reference to Figure 12).

Thereby, bearing can prevent that with sleeve 65 extensive magnitude that surpasses the bearing play c that the hole enlargement of each sleeve part 61a, 62a of two half- pulley 61,62 causes because of hole enlargement from making their slip surface be subjected to fierce slip abrasion, and 61,62 of two half-pulley at driven pulley 60 produce whirling vibration by the expansion of this bearing play c.

In the present embodiment, when the outer diameter D of the 61a of inner sleeve portion of fast pulley halfbody 61 ₁=34mm, the inside diameter D of the 62a of outer sleeve portion of movable half-pulley 62 ₄=37mm is when bearing is used the wall thickness h=2mm of sleeve 65, by the thickness h with slip body 65b ₁Set the thin-walled of 0.75mm for, can be held in originally constant substantially size to aforementioned bearings gap c.The thickness h of slip body 65b ₁Such size is set, and can for example realize by the surface layer of slip body 65b is implemented machining at an easy rate.

When between each sleeve part 61a, 62a of aforementioned bearings being installed in two half- pulley 61,62 with sleeve 65, the one end in contact is at the end difference 62f of the projection 62b root that is formed at movable half-pulley 62 62a of outer sleeve portion inner peripheral surfaces, its the other end, as mentioned above, the back-up ring 66 that comes off of preventing among the circlip groove 62e that is formed by an opposite side end with the 62a of outer sleeve portion that is encased in perimembranous in movable half-pulley 62 main bodys supports, and limits its axial motion thus.

Thereby, because bearing prevents to come off and is not configured on the projection 62b one side inner peripheral surface of the 62a of outer sleeve portion of movable half-pulley 62 with back-up ring 66 with sleeve 65, so there is no need to strengthen the wall thickness of this part 62a of outer sleeve portion, its external diameter can form smallerly, so in the constant occasion of the moment of torsion that acts on portion of torque cam mechanism mechanism, can strengthen the cam force that produces in this portion of torque cam mechanism mechanism, it is axial, the component that movable half-pulley 62 is pushed to fast pulley halfbody 61 1 sides also can strengthen, so can be clamped in two half-pulley 61 thereby can make setting smallerly along the equidirectional spring load of the spring 80 of movable half-pulley 62 loadings of giving, the durability of 62 vee-belts 55 improves.

Next, describe with regard to clutch 70 and torque cam mechanism mechanism.

Left end assembly department 61b at the 61a of inner sleeve portion of the left end of speed reducer input shaft 45 and fast pulley halfbody 61 is provided with clutch 70.

The flat outer clutch drum 71 that the round-ended cylinder shape arranged that is of clutch 70 is matched with the left end screw section of speed reducer input shaft 45 with its diapire 71a center hole through sleeve pipe 79, and by nut 74 screw threads for fastening, and its perisporium 71b is to right-hand opening.

In the inside of aforementioned clutch external drum 71, such as illustrated in Figure 3 on the left end assembly department 61b of the 61a of inner sleeve portion of fast pulley halfbody 61, cooperate the drive plate 72 that is installed with as drum in the clutch by zigzag fashion.

In order to prevent this zigzag fashion matching loose, with wire type back-up ring 78 be matched be located at assembly department 61b end, the cross section is substantially among the circlip groove 61c of semicircle arcuation, make the chamfered section 72e of its Elastic Contact in the zigzag fashion auxiliary section of the drive plate of hereinafter addressing 72 72a, whereby, load (with reference to Figure 21 to Figure 23) for drive plate 72 along the main body side direction of fast pulley halfbody 61 all the time.

As shown in the figure, this wire type back-up ring 78 for circular arc part by the cut-out ring-type of cutting away a bit a little, under nature for making its two end part shape very in a small amount of regulation that staggers, so when it is loaded among the circlip groove 61c, depend on elastic recovering force F ₁(the main body side direction of fast pulley halfbody 61) pushes the chamfered section 72e of drive plate 72 powerfully vertically, so even the driven pulley high speed rotating is acting on centrifugal force F on wire type back-up ring 78 ₂, the F that makes a concerted effort of these power also acts on counter-force from chamfered section 72e with point of contact wire type back-up ring 78 effectively relatively, prevents the hole enlargement of this back-up ring 78, can not throw off.And, such wire type back-up ring 78, simple in structure, cheapness also can easily be arranged even the space is narrow and small.

As illustrated among Figure 15 and Figure 16, drive plate 72 forms flat zigzag fashion cylindraceous auxiliary section 72a on inner circumference edge, core 72b extends along radiation direction from the outer circumferential face of this zigzag fashion auxiliary section 72a, connects the periphery dish 72c of portion that has some steps by this core 72b.

On the periphery dish 72c of portion, 3 places pin 73 along the circumferential direction equally spaced is set, on this pin 73, support clutch shoe 74 (with reference to Fig. 3) with axle.

On aforementioned core 72b, mold pressing integrally has the resinous fixed side cam part 75 of self lubricity, and 3 places along the circumferential direction equally spaced are set.

In each fixed side cam part 75 each other, form space 72d, 3 movable side cam part 62c of aforementioned movable half-pulley 62 make resinous fixed side cam part 75 engage to engagement with movable side cam part 62c facing to these 3 space 72d.

Such as illustrated in Figure 17, resin system fixed side cam part 75 is fixed on the crooked core 72b, the cross section approximate trapezoid, and what have the circumferencial direction front/rear end and be a clinoplain is interior to camming surface 75i be the export-oriented camming surface 75o of curved surface.

Such drive plate 72 is configured in the outer clutch drum 71, the clutch shoe 74 that is supported on pin 73 with axle is resisted clutch spring 76 and is outwards swung along radial direction under centrifugal action, be arranged on the inner peripheral surface that friction member 74a on the periphery of clutch shoe 74 is contacted with the perisporium side 71b of outer clutch drum 71, become jointing state.

Because drive plate 72 is matched with the left end assembly department 61b of the 61a of inner sleeve portion of fast pulley halfbody 61 and goes up the ground integral installation with sawtooth, so this drive plate 72 rotates with fast pulley halfbody 61 with being integral.

Such as illustrated in Figure 3, be bearing in the movable half-pulley 62 between the main body of this drive plate 72 and fast pulley halfbody 61 sliding freely, in periphery near the 62a of its outer sleeve portion, the spring 80 of spring steel is set, this spring 80 is installed between drive plate 72 and the movable half-pulley 62, along loading near the direction of fast pulley halfbody 61 movable half-pulley 62.

In the gap of the periphery of interior week of this spring 80 and the 62a of outer sleeve portion, clamping resinous spring guide sleeve 81.

This spring guide sleeve 81 is made cylindric as diagram among Fig. 9, at one end forms flange 81a, and its internal diameter is bigger slightly than the external diameter of the 62a of outer sleeve portion, the internal diameter hole enlargement to some extent of flange 81a side.

This spring guide sleeve 81 is arranged on the periphery of the 62a of outer sleeve portion, when drive plate 72 is installed on the left end assembly department 61b of the 61a of inner sleeve portion, resinous fixed side cam part 75 embeds the inside diameter of the hole enlargement of spring guide sleeve 81, support spring guide sleeve 81, the flange 81a of spring guide sleeve 81 are contacted with the stepped part 72f in interior week of the periphery dish 72c of portion of drive plate 72.

On the other hand, in the annular groove 62d of the root peripheral part of the 62a of outer sleeve portion that is located at movable half-pulley 62, equipped be the spring seat 82 of iron ring-type iron plate, the flange 81a ground that makes spring 80 two ends be contacted with this spring seat 82 and aforementioned spring guide sleeve 81 clamps it (with reference to Fig. 1, Fig. 4, Fig. 5).

So, leaning on spring 80 between movable half-pulley 62 and this fast pulley halfbody 61 that fast pulley halfbody 61 sides load, clamping and around hanging anterior rear portion around the vee-belt 55 that is hung on drive pulley 40, the trend ground around hanging vee-belt 55 effective radiuses that is increasing acts on, and can make vee-belt 55 tensionings whereby.

In addition, 3 movable side cam part 62c of left end of the 62a of outer sleeve portion of movable half-pulley 62 face 3 space 72d of the drive plate 72 that integrally rotates with fast pulley halfbody 61 respectively, engage with resinous 3 fixed side cam part 75 engagement ground.The jointing state of these 3 movable side cam part 62c and 3 fixed side cam part 75 is illustrated in Figure 18.

In Figure 18, gap c on the sense of rotation is very little to camming surface 62ci and export-oriented camming surface 62co in opposite directions with movable side cam part 62c interior respectively to camming surface 75i and export-oriented camming surface 75o for fixed side cam part 75 interior, and each camming surface in opposite directions is easy to contact.Thereby movable side cam part 62c is limited very for a short time to the relative rotation angle of fixed side cam part 75.

Vee-belt automatic speed variator 23 in the present embodiment is because constitute as described above, so work as following.

When the rotating speed of internal-combustion engine 21 hangs down, shown in solid line among Fig. 2, the centrifugal weight 44 that moves along the pitch 43 of drive pulley 40 sides is positioned at central side, movable half-pulley 42 is left fast pulley halfbody 41, and the effective radius around hanging of vee-belt 55 reduces, thus, in driven pulley 60 sides, movable half-pulley 62 loads and approaches fast pulley halfbody 61 by spring 80, strengthen the effective radius around extension of vee-belt 55, with very big reduction speed ratio transferring power.

When engine speed improves, shown in double dot dash line among Fig. 2, centrifugal weight 44 moves to centrifugal direction, the movable half-pulley 42 of drive pulley 40 sides is near fast pulley halfbody 41, becoming greatly of vee-belt 55 around the effective radius of hanging, thus, in driven pulley 60 sides, movable half-pulley 62 antagonistic springs 80 leave fast pulley halfbody 61, the effective radius around hanging of vee-belt 55 diminishes, and reduction speed ratio reduces gradually, at this moment, clutch 70 also is in jointing state, and the rotating speed of trailing wheel 9 is increased.

Moreover, when engine speed increases, because movable as described above half-pulley 62 moves to the direction of leaving fast pulley halfbody 61, so shown in double dot dash line among Figure 18, enter dearly among the space 72d of 75 of fixed side cam part like that with 62 one-tenth whole movable side cam part 62c of movable half-pulley.

Movable side cam part 62c shown in the double dot dash line of Figure 18 represents the high transmission ratio state of this little reduction speed ratio.In addition, the movable side cam part 62c shown in the solid line of same figure represents that state is compared in the underneath drive of aforementioned big retarding ratio.

So, the occasion that increases severely in the rapid acceleration during because of starting etc. of the tension force of vee-belt 55, be connected in trailing wheel 9 and bear the fast pulley halfbody 61 of heavy load very and vee-belt 55 between skid, on the other hand, because the load of trailing wheel 9 does not act directly on can be with respect to the movable half-pulley 62 of fast pulley halfbody 61 rotations, so movable half-pulley 62 has the tendency with vee-belt 55 rotations.

Thereby, movable half-pulley 62 produces rotation relatively for fast pulley halfbody 61, therefore, with 62 one-tenth whole movable side cam part 62c of movable half-pulley, for be fixed on the whole drive plates 72 of 61 one-tenth of fast pulley halfbodies on fixed side cam part 75 rotation in advance, the result as shown in Figure 18, movable side cam part 62c relatively moves along the arrow A direction for fixed side cam part 75.

So, the export-oriented camming surface 62co of movable side cam part 62c is contacted with the export-oriented camming surface 750 of fixed side cam part 75, movable side cam part 62c is subjected to the power of arrow B direction owing to reaction, thus, make movable half-pulley 62 near fast pulley halfbody 61, increase the clamping pressure of vee-belt 55, thereby can prevent skidding of vee-belt 55.

Because fixed side cam part 75 engages with movable side cam part 62c with being meshed, gap between the two is very little, so even the export-oriented camming surface 62co of movable side cam part 62c leaves the export-oriented camming surface 75o of fixed side cam part 75, maximum also has only very little clearance C, when quickening rapidly in when starting etc., aforementioned camming surface 62co, 75o contact torque cam mechanism mechanism action, the time lag before preventing to skid is very short, pickup lag is prevented from basically, can obtain level and smooth all the time sense of acceleration.

Figure 19 is the figure of the relation of expression engine speed Ne and vehicle velocity V, at certain engine speed n ₀Down, clutch 70 engages, and when transmission of power arrived trailing wheel 9, the torque cam mechanism mechanism action after clutch engages shown in solid line like that, did not have the ground of hysteresis and quickens down as described above.

In same figure, dotted line is represented the occasion of torque cam mechanism mechanism always, and after clutch, the time of skidding of vee-belt 55 is long, and pickup lag is arranged, and becomes the starting state that lacks sense of acceleration.

In addition, because fixed side cam part 75 is very little with the gap of movable side cam part 62c, and the interior of resinous fixed side cam part 75 is contacted with the interior to camming surface 62ci and export-oriented camming surface 62co of movable side cam part 62c respectively to camming surface 75i and export-oriented camming surface 75o, so abrasion and fatigue etc. are seldom, durability is good.

In addition, the axle head that concentrates on the 62a of this outer sleeve portion owing to 3 movable side cam part 62c forms, so maintenance is fine.

Because same with fast pulley halfbody 61, movable half-pulley 62 also is up to the 62a of outer sleeve portion and movably side cam part 62c is by aluminium cast form integrally, so part number reduces, designs simplification can make productivity improve.

And, because resinous fixed side cam part 75 also is the core 72b that integrally is molded to drive plate 72, thus the operation of independent manufacturing and assembling cam part can be omitted, thus can further boost productivity.

As Figure 17 was illustrated, the core 72b of drive plate 72 is relative, and 1 fixed side cam part 75 was divided into 2 bodies, makes the shape of cross section bending respectively, thereby integrally the resin system of mold pressing fixed side cam part 75 is positively fixed, and does not produce and rocks.

The fixed structure of this fixed side cam part 75 can be done all considerations, for example, such as illustrated in Figure 20, the core 90 of drive plate 72 also can be made intricately curved cross section shape, by with core 90 mold pressing integrally of this bending, resinous fixed side cam part 91 can not have with rocking and firmly fixes.

Moreover Figure 20 is an expression fixed side cam part 90 and the unfolded drawing of the jointing state of movable side cam part 92, and is identical substantially in the shape of cam part 91,92 and the previous embodiment.

Though in the present embodiment, as the bearing between the 62a of outer sleeve portion of the 61a of inner sleeve portion of fast pulley halfbody 61 and movable half-pulley 62, adopted bearing sleeve 27, but, because the sleeve as another part so must be arranged, part number increases, and it is miscellaneous that assembling procedure becomes.Therefore, also can adopt following device to replace it.

In other words, on the inner peripheral surface of the 62a of outer sleeve portion of the outer circumferential face of the 61a of inner sleeve portion of fast pulley halfbody 61 and movable half-pulley 62, carry out anode oxide film respectively and handle, and in this porous matter facial mask, soak oiling agents such as containing molybdenum disulfide.So, as the coaxial configuration bearing that integrally forms with these sleeves (Cylindorical rod), constitute the bearing between the 62a of outer sleeve portion of the 61a of inner sleeve portion of fast pulley halfbody 61 and movable half-pulley 62.Then, between these two coaxial configuration bearings, be coated with into grease, and by oil sealing that it is airtight.

So, even driven pulley 60 rotates around extension by vee-belt 55, the 61a of inner sleeve portion of fast pulley halfbody 61 and the movably 62a of the outer sleeve portion thermal expansion of half-pulley 62 are also because the heat conduction of bearing portion is good, so can reduce the variation of the bearing play between them.

In addition, owing to constitute bearing by the surface treatment and the grease of bearing portion slip surface, so do not need to specialize in other parts such as sleeve that bearing is used, part number reduces, and assembling procedure is simplified.And correspondingly lightweight also becomes possibility.

Claims (3)

1. V-shape belt automatic speed variator, this vee-belt automatic speed variator has by aluminium and integrally is shaped and axle is bearing in fast pulley halfbody on the running shaft, and integrally be shaped by aluminium, opposed with the aforementioned fixation half-pulley, the movable half-pulley of axle on the Cylindorical rod of this fast pulley halfbody sliding freely for clamping V shape belt, and having a torque cam mechanism mechanism in that the Cylindorical rod of aforementioned two half-pulley is distolateral, this torque cam mechanism mechanism can become aforementioned movable half-pulley the end thrust of this movable half-pulley to relatively rotating of aforementioned fixation half-pulley; It is characterized in that:

Bearing between the Cylindorical rod of aforementioned fixation half-pulley and the Cylindorical rod of aforementioned movable half-pulley is made of slide member cylindraceous,

The slip body that this slide member has the inner peripheral surface of the Cylindorical rod that is supported on aforementioned movable half-pulley, is made of synthetic resin with self lubricity,

This slip body forms thin-walled, and its wall thickness can compensate the Cylindorical rod of aforementioned fixation half-pulley and the dimensional changes of Cylindorical rod because of produced by heating power of aforementioned movable half-pulley, and the bearing play between these Cylindorical rods is constant substantially.

2. vee-belt automatic speed variator as claimed in claim 1 is characterized in that: aforementioned slip body forms thin-walled by polytetrafluoroethylene floor is carried out machining.

3. as claim 1 or the described vee-belt automatic speed variator of claim 2, it is characterized in that: aforementioned slide member is prevented to come off clipping this slide member side opposite with aforementioned torque cam mechanism mechanism by the back-up ring that prevents to come off.

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