CN104806658B - One-way clutch and crank-type buncher - Google Patents

Abstract

The present invention provides a kind of one-way clutch and crank-type buncher, prevents the side of the engaging-in retainer of peripheral part of the end face of roller to be exerted a force in the axial direction by axle spring.Because the frictional force of the 2nd end face (25b) of the frictional force of the 1st end face (25a) that makes to act on roller (25) with acting on roller (25) is consistent, roller (25) thus can be suppressed when being moved from datum mark to meshing point due to the 1st, 2nd end face (25a, frictional force 25b) imbalance and tilt, prevent the 1st of inclined roller (25), 2nd end face (25a, 25b) contact and wear with the 1st side (36a) of inner ring (36) and the 2nd side (36b), and can make roller (25) smoothly engaging-in outer peripheral face (23a) and exterior part (22) to inner part (23) inner peripheral surface (22a) between and improve the engagement response of one-way clutch (21).

Description

One-way clutch and crank-type buncher

Technical field

The present invention relates to one-way clutch and with the one-way clutch crank-type buncher, it is described unidirectionally from In clutch, the multiple rollers being maintained on retainer are exerted a force in the circumferential using engagement spring, the retainer configuration Between the outer peripheral face of inner part and the inner peripheral surface of exterior part, by the inner part and the exterior part in one direction Rotate against, make the roller is engaging-in to transmit driving force between the outer peripheral face and the inner peripheral surface.

Background technology

It is well known that, it is made up of following patent documents 1 using helical spring in the circumferential to the roller of one-way clutch The engagement spring to be exerted a force, and the axially displaced stretching for limiting helical spring is set at the retainer for keeping roller Portion, thus make the attitude stabilization of helical spring and prevent roller is engaging-in in an inclined state from arriving between inner ring and outer ring.

Patent document 1：No. 3903157 publications of Japanese Patent Publication No.

In addition, in the case of using leaf spring as the engagement spring to be exerted a force in the circumferential to roller, it is not possible to adopt With the construction for the above-mentioned patent document 1 for being necessary for helical spring, thus consider, it is right in the axial direction by using axle spring 1st end face of roller is exerted a force, and the 2nd end face of roller is pressed on into the side of retainer to prevent from tilting.

However, even if setting axle spring to prevent roller inclination, when roller is being moved to datum mark from damping point During when slightly tilting, the peripheral part for also resulting in the 2nd end face of roller is hooked on the side of retainer, exist it is following can Can property：Hinder the smooth engagement of one-way clutch in datum roller inclination, or the peripheral part of the 2nd end face of roller with The side phase mutual friction of retainer and as abrasion the reason for.

The content of the invention

The present invention is made in view of the foregoing, and the purpose of the present invention is to prevent from being exerted a force in the axial direction by axle spring Roller end face the engaging-in side to retainer of peripheral part.

In order to achieve the above object, the invention according to technical scheme 1, it is proposed that a kind of one-way clutch, wherein making The multiple rollers being maintained on retainer are exerted a force in the circumferential with engagement spring, the retainer is configured at inner part Between outer peripheral face and the inner peripheral surface of exterior part, by the rotating against in one direction of the inner part and the exterior part, Make the roller is engaging-in to transmit driving force between the outer peripheral face and the inner peripheral surface, also, the retainer have with Opposed the 1st side and the 2nd side are distinguished in 1st end face of the roller and the 2nd end face, using being arranged at the 1st side Axle spring exerts a force to the 1st end face in the axial direction, the 2nd end face is abutted with the 2nd side, so as to limit The posture of the roller, the one-way clutch are characterised by, are acted on the frictional force of the 1st end face and are acted on described The frictional force of 2nd end face is consistent.

Also, according to the invention described in technical scheme 2, it is proposed that a kind of one-way clutch, except the structure of technical scheme 1 In addition, also with following characteristics：Force application part is supported in the 1st side in a manner of moving axially freely, using described Axle spring exerts a force to the force application part to the 1st end face in the axial direction, and the 2nd side formed with The convex portion that 2nd end face abuts, the roller bearing surface of the force application part and the roller bearing surface of the convex portion are phase similar shape Shape, and coaxially opposed in the axial both sides of the roller so that act on the 1st end face and the force application part it Between frictional force it is consistent with acting on the frictional force between the 2nd end face and the convex portion.

Also, according to the invention described in technical scheme 3, it is proposed that a kind of one-way clutch, except the structure of technical scheme 2 In addition, also with following characteristics：It is by the engaging-in outer peripheral face to the inner part and the exterior part when the roller is in When holding fix before between inner peripheral surface is datum mark, at the peripheral part of the roller bearing surface of the force application part and the convex portion In the described 1st, inner side of the peripheral part of the 2nd end face.

Also, according to the invention described in technical scheme 4, it is proposed that a kind of crank-type buncher, the crank-type without Level speed changer has one-way clutch in 1~technical scheme of technical scheme 3 described in wantonly 1, it is characterised in that it is described unidirectionally from The inner part of clutch is fixedly installed on the periphery of the output shaft of power transfer unit, and the power transfer unit makes and driving source The rotation speed change of the input shaft of connection is simultaneously delivered to the output shaft, and the power transfer unit has：Input side fulcrum, its from The offset of the eccentric axis of the input shaft is variable, and the input side fulcrum rotates together with the input shaft；Outlet side Fulcrum, it is arranged on the exterior part of the one-way clutch；And connecting rod, it connects described input side fulcrum and described Outlet side fulcrum.

In addition, the eccentric disc 18 of embodiment corresponds to the input side fulcrum of the present invention, the pin 19c of embodiment corresponds to The outlet side fulcrum of the present invention, the engine E of embodiment correspond to the driving source of the present invention, the 1st bearing surface of embodiment P1 corresponds to the roller bearing surface of the force application part of the present invention, and the 2nd bearing surface P2 of embodiment corresponds to the convex portion of the present invention Roller bearing surface.

According to the structure of technical scheme 1, in one-way clutch, using engagement spring in the circumferential to being maintained on retainer Multiple rollers exerted a force, the retainer is configured between the outer peripheral face of inner part and the inner peripheral surface of exterior part, by interior The rotating against in one direction of part and exterior part, makes engaging-in arrive between outer peripheral face and inner peripheral surface of roller and transmits driving Power.Retainer has 1st side and 2nd side opposed with the 1st end face of roller and the 2nd end face difference, using being arranged at the 1st The axle spring of side exerts a force to the 1st end face in the axial direction, the 2nd end face is abutted with the 2nd side, so as to limit roller Posture.

Because the frictional force of the 2nd end face of the frictional force of the 1st end face that makes to act on roller with acting on roller is consistent, because And roller can be suppressed and tilted when being moved from datum mark to meshing point due to the imbalance of the frictional force of the 1st, the 2nd end face, Prevent inclined roller the peripheral part of the 1st, the 2nd end face and the 1st side of retainer and the 2nd contacts side surfaces and wear, and It can make roller smoothly between the inner peripheral surface of engaging-in outer peripheral face and exterior part to inner part and improve the engagement of one-way clutch Response.

Also, according to the structure of technical scheme 2, force application part is supported in the 1st side in a manner of moving axially freely, Force application part is exerted a force to the 1st end face in the axial direction using axle spring, and the 2nd side formed with the 2nd end face The convex portion of abutting.The roller bearing surface of force application part and the roller bearing surface of convex portion are same shape, and in the axial direction of roller Both sides are coaxially opposed, so that the frictional force acted between the 1st end face and force application part is with acting on the 2nd end face and convex portion Between frictional force it is consistent, thus can not only make force application part in the lump with roller force function and frictional force adjustment work( Can, and the 1st of roller the, the frictional force precision of the 2nd end face can be made to balance well.

Also, according to the structure of technical scheme 3, when roller is in datum mark, the roller of force application part and convex portion abuts The peripheral part in face is in the inner side of the peripheral part of the 1st, the 2nd end face, thus when roller is from i.e. by the engaging-in outer peripheral face to inner part Holding fix before between the inner peripheral surface of exterior part be datum mark to meshing point move when, can be more reliably prevented from the 1st, the The peripheral part of 2 end faces is hooked on the roller bearing surface of force application part or the roller bearing surface of convex portion and makes roller inclination.

Also, according to the structure of technical scheme 4, the inner part of one-way clutch is fixedly installed on the defeated of power transfer unit The periphery of shaft, the rotation speed change for the input shaft that the power transfer unit makes to be connected with driving source are simultaneously delivered to output shaft, power Transfer unit has：Input side fulcrum, its from the offset of the eccentric axis of input shaft be variable, and the input side fulcrum with The input shaft rotates together；Outlet side fulcrum, it is arranged on the exterior part of one-way clutch；And connecting rod, it connects input Collateral point and outlet side fulcrum, thus when input shaft rotates and connecting rod moves back and forth, one-way clutch discontinuously connects Merge and output shaft discontinuously rotates, so as to transmit driving force.Now, one-way clutch with short time interval repeat engagement and Debonding, thus technical scheme 1 has more effectively been played to the The effect of invention of technical scheme 4, improve power and transmit list The performance of member.

Brief description of the drawings

Fig. 1 is the skeleton drawing of power transmission apparatus for vehicle.

Fig. 2 is 2 of Fig. 1 to scheme in detail.

Fig. 3 is Fig. 2 3-3 lines sectional view (OD states).

Fig. 4 is Fig. 2 3-3 lines sectional view (GN states).

Fig. 5 is the Action Specification figure under OD states.

Fig. 6 is the Action Specification figure under GN states.

Fig. 7 is the exploded perspective view of one-way clutch.

Fig. 8 is the partial perspective view of the inner ring of angular contact ball bearing.

Fig. 9 is Fig. 29 enlarged drawings (Figure 11 9-9 lines sectional view).

Figure 10 is Fig. 9 10 enlarged drawings.

Figure 11 is Fig. 9 11-11 line sectional views.

Figure 12 is Figure 10 12-12 line sectional views.

Label declaration

11：Input shaft；12：Output shaft；18：Eccentric disc (input side fulcrum)；19：Connecting rod；19c：Sell (outlet side fulcrum)； 21：One-way clutch；22：Exterior part；22a：Inner peripheral surface；23：Inner part；23a：Outer peripheral face；24：Engage spring；25：Roller； 25a：1st end face；25b：2nd end face；26：Force application part；31：Retainer；36a：1st side；36b：2nd side；36c：It is convex Portion；38：Axle spring；E：Engine (driving source)；P1：1st bearing surface (the roller bearing surface of force application part)；P2：2nd abuts Face (the roller bearing surface of convex portion)；U：Power transfer unit.

Embodiment

Hereinafter, embodiments of the present invention are illustrated according to Fig. 1~Figure 12.

As shown in FIG. 1 to 3, engine E driving force is delivered to driving wheel W, W car via left and right axletree 10,10 There is the buncher T and differential gear D of crank-type with power transmission.The buncher T of present embodiment is Make to have multiple (being 4 in embodiments) power transfer unit U of same configuration to overlap in the axial direction, these are dynamic There is power transfer units U the public input shaft 11 of configured in parallel and public output shaft 12, the rotation of input shaft 11 to be decelerated Or output shaft 12 is passed to by speedup.

Below, buncher T construction is illustrated according to Fig. 2~Fig. 6.

First, illustrated using power transfer unit U construction as representative.It is connected and is rotated with engine E Input shaft 11 rotate against freely penetrate motor as shifting actuator 14 hollow rotary shaft 14a inside.Become The rotor 14b of fast actuator 14 is fixed on rotary shaft 14a, and stator 14c is fixed on housing.The rotation of shifting actuator 14 Rotating shaft 14a can be to rotate with the same speed of input shaft 11, and can be relative at different rates relative to input shaft 11 Rotation.

Be fixed with the 1st little gear 15 on the rotary shaft 14a input shaft 11 for having penetrated shifting actuator 14, with across this The mode of 1st little gear 15 makes the planet carrier 16 of crank-like be connected with the rotary shaft 14a of shifting actuator 14.Diameter and the 1st small 15 identical of gear, 2 the 2nd little gears 17,17 are supported on by pinion pin 16a, 16a respectively to cooperate with the 1st little gear 15 The position of equilateral triangle is formed, is eccentrically formed gear ring 18a and these the 1st little gears in the inside of discoideus eccentric disc 18 15 and the 2nd little gear 17,17 engages.In the outer peripheral face of eccentric disc 18, rotating against to be fitted together to freely by ball bearing 20 has It is arranged on the ring portion 19b of the bar portion 19a of connecting rod 19 one end.

The one-way clutch 21 for being arranged on the periphery of output shaft 12 has：The exterior part 22 of ring-type, it is by pin 19c by pivot Turn to be supported on the bar portion 19a of connecting rod 19；Inner part 23, it configures in the inside of exterior part 22 and is fixed on output shaft 12；With And roller 25, it configures in the space for the wedge-like being formed between exterior part 22 and inner part 23 and applied by engaging spring 24 Power.In addition, the specific configuration of one-way clutch 21 is described in detail below.

Figure it is seen that 4 power transfer unit U share the planet carrier 16 of crank-like, and by the 2nd little gear 17, The phase of 17 eccentric discs 18 being supported on planet carrier 16 differs 90 ° respectively for each power transfer unit U.Example Such as, in fig. 2, the power transfer unit U of left end eccentric disc 18 is displaced in figure top relative to input shaft 11, from from left to right the 3 power transfer unit U eccentric disc 18 is displaced to lower section in figure relative to input shaft 11, from the 2nd from left to right and the 4th power Transfer unit U, U eccentric disc 18,18 are located among above-below direction.

Below, according to Fig. 7~Figure 12, the construction of one-way clutch 21 is illustrated.In addition, to list in Fig. 3~Fig. 6 Schematic illustration is made to clutch 21, its actual configuration is as shown in Fig. 7~Figure 12.

The one-way clutch 21 of present embodiment exterior part 22 substantially annular in shape circular inner peripheral surface 22a, with 12 rollers 25 are configured between the outer peripheral face 23a in wavy bending of the inner part 23 of tubular, connecting rod 19 is by pin 19c and folder Protuberance 22b, 22b of tight periphery of the part 40,40 with being arranged on exterior part 22 are connected, side of the output shaft 12 that can not rotate against Formula is combined with the inner peripheral portion of inner part 23.

One-way clutch 21 has the retainer for being used for supporting the engagement spring 24 to be exerted a force in the circumferential to roller 25 31.Retainer 31 by angular contact ball bearing 34,34 described later a pair of inner rings 36,36 and in the circumferential equally spaced configuration and 12 spring supporting bars 33 for being connected with each other a pair of inner rings 36,36 are formed, and a pair of configurations of inner rings 36,36 are in 12 rollers 25 Axial both sides, 12 spring supporting bars 33 are configured between 12 rollers 25.In the inner peripheral portion of inner ring 36,36 is pressed into The outer peripheral face 23a of part 23, makes retainer 31 be combined in a manner of it can not rotate against with inner part 23.

Engagement spring 24 makes 1 piece of elastic plate bend to section S shape and be formed, and one side is consolidated by welding It is scheduled on the spring supporting bar 33 of retainer 31, in its another side formed with being abutted with roller 25 and be capable of applying for elastic deformation Power portion 24a.

Also, the ring spring 39 of ring-type is configured with the inner peripheral surface 22a endless groove 22c of exterior part 22 is formed at, The ring spring 39 abuts with the side face of roller 25 and inwardly the outer peripheral face 23a of part 23 exerts a force.

An angular contact ball bearing 34 is configured between adjacent two one-way clutch 21,21, passes through the corner connection Touch in a manner of ball bearing 34 rotates against exterior part 22,22 and inner part 23 while can maintain concentric and connect Connect.Angular contact ball bearing 34 is configured with multiple balls 37, two outer rings between two outer rings 35,35 and an inner ring 36 35th, the 35 mutually opposing axial end portion for being integrally formed at two exterior parts 22,22 adjacent in the axial direction, an inner ring 36 by Separate part forms and is pressed into the outer peripheral face 23a of inner part 23.That is, an angular contact ball bearing 34 is by making Two outer rings 35,35 are supported with public ball 37, by two exterior parts 22,22 of adjacent two one-way clutch 21,21 Supported in a manner of it can rotate against.

In addition, 2 angular contact ball bearings 34,34 positioned at the axial both ends for 4 one-way clutch 21 being arranged side-by-side The ball 37 of (reference picture 9) only abuts with an inner ring 36 and an outer ring 35.

As shown in Fig. 7, Fig. 8, Figure 10 and Figure 12, a pair of angular contact rollings are configured with the axial both sides of each one-way clutch 21 Pearl bearing 34,34, the 1st side 36a being formed on the inner ring 36 of an angular contact ball bearing 34 and is formed at another angle The 2nd side 36b on the inner ring 36 of contact ball bearing 34 is mutually opposing.At the axial both ends of roller 25 formed with flat 1 end face 25a and the 2nd end face 25b, the 1st end face 25a of roller 25 is opposed with the 1st side 36a of inner ring 36, the 2nd end of roller 25 Face 25b is opposed with the 2nd side 36b of inner ring 36.

In the 1st side 36a of the inner ring 36 of an angular contact ball bearing 34, in a circumferential direction equally spaced formed with 12 recess 36d, the discoideus force application part 26 chimeric with these recesses 36d freely that slides axially is by being incorporated in The axle spring 38 being made up of helical spring in recess 36d is exerted a force to the 1st end face 25a of roller 25.Also, at another 2nd side 36b of the inner ring 36 of angular contact ball bearing 34, in a circumferential direction equally spaced formed with 12 convex portion 36c, this 2nd end face 25b of a little convex portion 36c to rollers 25 is prominent.

The elastic force of axle spring 38 presses the 1st end face 25a of roller 25 via force application part 26, by the 2nd end of roller 25 Face 25b presses on convex portion 36c, thus prevents the inclination of roller 25 and realizes the stabilization of posture.

As shown in figure 12, roller 25 can relatively move in the circumferential relative to exterior part 22 and inner part 23, roller 25 Position have：The engaging-in wedge-like between the inner peripheral surface 22a and the outer peripheral face 23a of inner part 23 that are formed at exterior part 22 of roller 25 Space and the position (meshing point) for transmitting driving force；Roller 25 is by the engaging-in holding fix (base to before the wedge-like space On schedule)；And roller 25 is maximum round about more than datum mark from meshing point in the moment of the debonding of one-way clutch 21 The position (damping point) pushed back to limit.

The outer diameter D 1 of force application part 26 and circular convex portion 36c outer diameter D 1 be configured to it is smaller than the outer diameter D of roller 25, and And the center O1 of circular force application part 26 and circular convex portion 36c center O1 and the roller 25 positioned at datum mark center one Cause.

The of force application part 26 and the 1st end face 25a of roller 25 the 1st bearing surface P1 abutted and convex portion 36c and roller 25 The 2nd bearing surface P2 that 2 end face 25b are abutted has a same diameter D1 smaller than the diameter D of roller 25, and with positioned at datum mark The Sharing Center O1 of roller 25.

Below, to having the function that the embodiments of the present invention of said structure illustrate.

First, the effect to a buncher T power transfer unit U illustrates.When making shifting actuator 14 Rotary shaft 14a when being rotated against relative to input shaft 11, planet carrier 16 rotates around the axis L1 of input shaft 11.Now, OK Enclose at the center for the equilateral triangle that the center O of carrier 16, that is the 1st little gear 15 and 2 the 2nd little gears 17,17 are formed Axis L1 around input shaft 11 rotates.

Fig. 3 and Fig. 5 shows that the center O of planet carrier 16 is in relative to the 1st little gear 15 (that is input shaft 11) The state of the side opposite with output shaft 12, now, eccentric disc 18 are maximum, variable speed relative to the offset of input shaft 11 Device T gear ratio is minimum OD (overdrive, overgear) state.Fig. 4 and Fig. 6 shows that the center O of planet carrier 16 is relative The state with the identical side of output shaft 12, now, the phase of eccentric disc 18 are in the 1st little gear 15 (that is input shaft 11) Offset for input shaft 11 is zero, and buncher T gear ratio (geared neutral, is hung empty for infinitely great GN Shelves) state.

Under the OD states shown in Fig. 5, rotate input shaft 11 using engine E, and with fast with the identical of input shaft 11 When degree rotates the rotary shaft 14a of shifting actuator 14, input shaft 11, rotary shaft 14a, planet carrier 16, the 1st little gear 15,2 2nd little gear 17,17 and eccentric disc 18 are in the state of being integrated, (the reference counterclockwise centered on input shaft 11 Arrow A) eccentric rotary.During Fig. 5 (C) state is rotated to by Fig. 5 (B) from Fig. 5 (A), connecting rod 19 makes in its bar portion By the exterior part 22 of pin 19c pivot supports, (reference arrow B) rotates counterclockwise for 19a front end, wherein the connecting rod 19 Ring portion 19b the periphery for being supported on eccentric disc 18 freely is rotated against by ball bearing 20.Fig. 5 (A) and Fig. 5 (C) show The both ends that exterior part 22 rotates to the arrow B directions are gone out.

So, when exterior part 22 rotates to arrow B directions, the engaging-in He of exterior part 22 to one-way clutch 21 of roller 25 Wedge-like space between inner part 23, the rotation of exterior part 22 are passed to output shaft 12, thus output shaft via inner part 23 12 (reference arrow C) rotations counterclockwise.

When the little gear 15 of input shaft 11 and the 1st further rotates, gear ring 18a and the 1st little gear 15 and the 2nd little gear 17th, (reference arrow A) eccentric rotary counterclockwise of eccentric discs 18 of 17 engagements.Rotated to from Fig. 5 (C) by Fig. 5 (D) During Fig. 5 (A) state, connecting rod 19 makes in its bar portion 19a front end by the exterior part 22 of pin 19c pivot supports to clockwise Direction (reference arrow B ') rotates, wherein the ring portion 19b of the connecting rod 19 is rotated against by ball bearing 20 and propped up freely Support is in the periphery of eccentric disc 18.Fig. 5 (C) and Fig. 5 (A) shows the both ends that exterior part 22 rotates to the arrow B ' directions.

So, when exterior part 22 rotates to arrow B ' directions, the one side of 25 one side compressive engagement spring of roller 24 is by from outer Extruded in wedge-like space between part 22 and inner part 23, so as to which exterior part 22 skids relative to inner part 23, output shaft 12 Do not rotate.

As previously discussed, when exterior part 22 has carried out reciprocating rotary, only when the direction of rotation of exterior part 22 is the inverse time During pin direction (reference arrow B), (reference arrow C) rotates output shaft 12 counterclockwise, thus output shaft 12 enters in the ranks Disconnected rotation.

Fig. 6 shows the effect when operating buncher T under GN states.Now, due to the position of input shaft 11 It is consistent with the center of eccentric disc 18, thus eccentric disc 18 is zero relative to the offset of input shaft 11.When using in this condition Engine E makes input shaft 11 rotate and rotate the rotary shaft 14a of shifting actuator 14 with the same speed of input shaft 11 When, input shaft 11, rotary shaft 14a, planet carrier 16,15,2 the 2nd little gears 17,17 of the 1st little gear and eccentric disc 18 for In the state of one, (reference arrow A) eccentric rotary counterclockwise centered on input shaft 11.However, due to eccentric disc 18 offset is zero, thus the reciprocating stroke of connecting rod 19 is also zero, and output shaft 12 does not rotate.

Therefore, if driving shifting actuator 14 and the position of planet carrier 16 being set in into Fig. 3 OD states and Fig. 4 GN Between state, then it can be operated with any gear ratio between infinitely great gear ratio and minimum gear ratio.

For buncher T, because the phase of the eccentric disc 18 for 4 power transfer unit U being arranged side-by-side is mutually wrong Open each 90 °, thus 4 power transfer unit U alternately transmit driving forces, that is to say, that either one in 4 one-way clutch 21 Engagement state necessarily is in, it is possible thereby to make output shaft 12 continuously rotate.

Below, the inclination to the roller 25 of one-way clutch 21 prevents effect from illustrating.

In the moment of the debonding of one-way clutch 21, exceed datum mark positioned at the roller 25 of meshing point and nibbled while compressing Close the one side of spring 24 to be pressed back into after damping point, utilize the elastic force of compressed engagement spring 24 to return to datum mark, be unidirectional Engagement next time of clutch 21 is ready and waited.

When roller 25 is moved to datum mark from damping point, the 1st abutting of the force application part 26 to be exerted a force by axle spring 38 Face P1 abuts with the 1st end face 25a of roller 25, and the 2nd end face 25b of roller 25 and the 2nd of the 2nd side 36b of inner ring 36 Bearing surface P2 is abutted, thus inhibits the inclination of roller 25 using the 1st bearing surface P1 and the 2nd bearing surface P2 guiding function.

Now, if the frictional force for acting on the 1st end face 25a and the 2nd end face 25b of roller 25 is uneven, then rolling be present The possibility of sub 25 run-off the straights, but according to present embodiment, due to abutted with the 1st end face 25a the 1st of force application part 26 Bearing surface P1 and be same shape with the 2nd end face 25b convex portion 36c abutted the 2nd bearing surface P2, and the 1st bearing surface P1 and 2nd bearing surface P2 is symmetrically arranged at the axial both sides of roller 25, thus acts on the 1st end face 25a and the 2nd end face of roller 25 25b frictional force is formed objects.The result is that, it is therefore prevented that in the inclination of the roller 25 of datum, roller 25 is with correct appearance State is moved to meshing point from datum mark, and one-way clutch 21 can be engaged smoothly.

And when roller 25 tilts, the 1st end face 25a or the 2nd end face 25b peripheral part are engaging-in to the 1st side 36a or 2 side 36b and probably promote to wear, but by preventing the inclination of roller 25, it is suppressed that the abrasion.Particularly, when When roller 25 is located at datum mark, the of the 1st end face 25a and the 2nd end face 25b of roller 25 and the smaller force application part 26 of diameter 1 bearing surface P1 and convex portion 36c the 2nd bearing surface P2 is abutted, thus reliably prevent the 1st end face 25a's or the 2nd end face 25b Peripheral part is engaging-in to the 1st side 36a or the 2nd side 36b, more effectively inhibits the abrasion.

Also, the buncher T of crank-type one-way clutch 21 repeats engagement with short time interval and releasing connects Close, thus require high engagement response, but by the way that the one-way clutch 21 of the present invention to be supplied to the stepless change of crank-type Fast device T, has more effectively played its effect.

Embodiments of the present invention are this concludes the description of, but the present invention can be carried out in scope without departing from the spirit Various design alterations.

For example, the purposes of the one-way clutch of the present invention is not limited to the buncher T of embodiment.However, due to The buncher T of embodiment one-way clutch 21 repeats engagement and debonding with short time interval, thus passes through Apply the present invention to the one-way clutch 21, more effectively play effect.

Also, in embodiments, make retainer by the way that angular contact ball bearing 34 to be used as to a part for retainer 31 31 construction is simplified and reduces part count, but the part different from angular contact ball bearing 34 can be used to form and kept Frame 31.

Claims (3)

1. A kind of 1. one-way clutch, wherein using engagement spring (24) multiple rollings to being maintained on retainer (31) in the circumferential Sub (25) are exerted a force, and the retainer (31) is configured at the outer peripheral face (23a) of inner part (23) and the inner circumferential of exterior part (22) Between face (22a), by the rotating against in one direction of the inner part (23) and the exterior part (22), make the rolling (25) are engaging-in transmits driving force between the outer peripheral face (23a) and the inner peripheral surface (22a) for son, also,

   The retainer (31) has 1st opposed with the 1st end face (25a) of the roller (25) and the 2nd end face (25b) difference Side (36a) and the 2nd side (36b), using being arranged at the axle spring (38) of the 1st side (36a) in the axial direction to institute State the 1st end face (25a) to be exerted a force, the 2nd end face (25b) is abutted with the 2nd side (36b), it is described so as to limit The posture of roller (25),

   The one-way clutch is characterised by,

   Force application part (26) is supported in the 1st side (36a) in a manner of moving axially freely, uses the axle spring (38) force application part (26) is exerted a force to the 1st end face (25a) in the axial direction, and in the 2nd side (36b) is formed with the convex portion (36c) abutted with the 2nd end face (25b), the roller bearing surface (P1) of the force application part (26) Roller bearing surface (P2) with the convex portion (36c) is same shape, and in the axial both sides of the roller (25) coaxially It is opposed, so that the frictional force acted between the 1st end face (25a) and the force application part (26) and acting on described the Frictional force between 2 end faces (25b) and the convex portion (36c) is consistent.
2. 2. one-way clutch according to claim 1, it is characterised in that arrive institute by engaging-in when the roller (25) is in Holding fix i.e. benchmark before stating between the outer peripheral face (23a) of inner part (23) and the inner peripheral surface (22a) of the exterior part (22) During point, the peripheral part of the force application part (26) and the convex portion (36c) roller bearing surface (P1, P2) is in the 1st end The inner side of the peripheral part of face and the 2nd end face (25a, 25b).
3. 3. a kind of crank-type buncher, the crank-type buncher has described in claim 1 or claim 2 One-way clutch (21), it is characterised in that

   The inner part (23) of the one-way clutch (21) is fixedly installed on power transfer unit (U) output shaft (12) Periphery, the rotation speed change for the input shaft (11) that the power transfer unit (U) makes to be connected with driving source (E) are simultaneously delivered to the output Axle (12),

   The power transfer unit (U) has：Input side fulcrum (18), its bias from the eccentric axis of the input shaft (11) Amount is variable, and the input side fulcrum (18) rotates together with the input shaft (11)；Outlet side fulcrum (19c), it is arranged on On the exterior part (22) of the one-way clutch (21)；And connecting rod (19), its connect described input side fulcrum (18) and The outlet side fulcrum (19c).