CN102537126B - There is a bag space wedging type friction overrunning clutch provided for shape component - Google Patents

Abstract

This free wheel device is the further in-depth to space wedging type friction overrunning clutch provided.It comprises, rotate the space wedge mechanism of guide mechanism G and traction friction mechanism F1 composition, mechanism F1 has friction member, the guiding element of mechanism G has the tooth-like guide surface of spiral best, two mechanisms also total same there is complementary guide surface and revolution rubbing surface ring-type intermediate piece and axial stiffness interlock; And axial force closes this Liang Ge mechanism and the power transmission friction mechanism combined rigidly with guiding element and friction member.It is mainly characterized in that, above-mentioned guiding element, one of intermediate piece and friction member are bag shape annular components, or the compostle member be at least fixed as one circumferentially with this bag of shape Component composition.The present invention has nearly all quality that desirable free wheel device should have, and it is simpler to have structure especially, and physical dimension is less, makes the advantage that assembling is more convenient and cost is lower.

Description

There is a bag space wedging type friction overrunning clutch provided for shape component

Related application

The application is the Chinese patent application 201010222712.X of space wedging type friction overrunning clutch provided by name that proposes of the applicant and the dependent patent of 201020186785.3 and part continuation application.The full content of the disclosure two patent applications is formerly incorporated herein by reference.

Technical field

The present invention relates to a kind of engaging and disengaging gear in all transmission fields, and comprise the device of the such as friction clutch of this engaging and disengaging gear, automatically controlled/magnet clutch, safety clutch, coupling, break, motor-vehicle skid, speed changer, drive wheel, spanner and hinge/pivot etc., particularly a kind of friction overdrive clutch.

Background technique

Statement in this part only provides the background information relevant with understanding teachings herein and analysis but does not form prior art.

Disclosed in the January, 2011 above the technological scheme of overall two the basic patent applications combined, avoid the shortcoming that transmission capacity is low, poor reliability, transmission efficiency are low, processing and assembling is difficult, cost is high, easy to wear/life-span is short, application area is little that in prior art, free wheel device has well.Wherein, the axial dock of relative usage and radial abutment formula axial force close the technological scheme of encapsulating shell, it uses the technological scheme of bag shape component/encapsulating shell at least roughly in the form of a ring, when having same performance advantage, more because it has the simplest structure, cordwood assembling, less axle/radial dimension and quality, lower making and assembly cost, and be easier to the plurality of advantages such as application comprising in higher rotating speed, huge and miniature yardstick transmission field, and be provided with larger advantage and larger use value.But above overall two the basic patent applications combined, do not provide further in-depth for this technological scheme and expand.

Summary of the invention

The technical problem to be solved in the present invention is exactly provide a kind of pointedly to have a bag space wedging type friction overrunning clutch provided for shape component, its hinge structure has simpler structure, less axial/radial size and less quality, be easier to hugeization and microminiaturization, and be far away high torque capacity.

For solving the problems of the technologies described above, the present invention's bag space wedging type friction overrunning clutch provided for shape component that has comprises, around one axis revolution and can axial engagement at least one traction friction mechanism, it has and to turn round around described axis and to be provided with the intermediate piece being at least roughly ring-type and the friction member of rubbing surface, the rubbing surface of both sides axially forms traction friction pair, to transmit friction torque between this two component with offseting; For this traction friction mechanism engaging force is provided and around above-mentioned axis pivotal at least one rotate guide mechanism, it has and to turn round around above-mentioned axis and to be provided with the guiding element being at least roughly ring-type and the intermediate piece of corresponding guide surface, and the guide surface of both sides axially forms guiding friction pair with offseting; And, connect in order to the closed conflict of axial force of setting up between guiding element, intermediate piece and friction member, and with one of them at least one bag of shape component be at least non-rotatably connected, it is provided with the inner peripheral surface around the pivotal at least roughly half cycle of above-mentioned axis, and is positioned at the circumferential recess of the roughly half cycle on this inner peripheral surface and is communicated to the entrance of this circumferential recess by the outer circumferential face of above-mentioned bag shape component; Wherein, the lift angle λ at the mutual conflict position of guiding friction pair, is greater than zero and is less than or equal to ξ, that is, 0< λ≤ξ, ξ are the minimum value that can cause all lift angle λ of not self-locking in guiding friction pair and traction friction pair circumference.

Preferably, one in bag shape component and guiding element, intermediate piece and friction member, single hard parts is combined into.

Alternatively, be provided with at least two around the pivotal friction mechanism of above-mentioned axis, one of them is above-mentioned traction friction mechanism, and wherein another is the power transmission friction mechanism at least non-rotatably combined respectively with guiding element and friction member, or another above-mentioned traction friction mechanism.

Improve as one, the span of above-mentioned lift angle λ can also be: ζ < λ≤ξ, or, 0< λ≤ζ (as ζ > 0), wherein, ζ is the minimum value of the lift angle λ that can cause self-locking in guiding friction pair circumference, is also the maximum value of the lift angle λ causing self-locking in traction friction pair circumference.

Selectively, above-mentioned bag shape component is provided with the characteristic surface for transmitting torque.

Selectively, on the outer circumferential face of guiding element, intermediate piece or friction member, be provided with the arm of force extended to above-mentioned entrance radial direction, to be non-rotatably connected with bag shape component.

For balancing the centrifugal inertia force of free wheel device, also balancing component can be set in above-mentioned entrance.

For the above-mentioned entrance of radial-plugging best, be also provided with closure member.

Preferably, rotation guide mechanism mutually nested in two radial directions and at least one elastic element also can be set.Two guiding elements of this two mechanism and two intermediate pieces, be positioned at the form on equidirectional end face with guide surface, connect into rigid unitary respectively, and non-rotatably connect into circumference one; In these two rotation guide mechanisms, the lift angle λ of each self-steering friction pair, is greater than zero respectively and is less than or equal to ζ, and be greater than ζ and be less than or equal to ξ; Elastic element is then axially at least indirectly conflicted and is greater than zero to lift angle λ and is less than or equal to the described rotation guide mechanism of ζ.

Selectively, also can have multiple traction friction mechanism and multiple rotation guide mechanism, be arranged on accordingly respectively and arrange in multiple circumferential recess of the correspondence of the multiple bags of shape components be also combined into one rigidly along above-mentioned axis.

Best, also comprise the elasticity pre-tightening mechanism at least with an elastic element, it is for setting up at least indirectly frictional connection between intermediate piece and friction member constantly.

Preferably, at least one in traction friction mechanism and power transmission friction mechanism, two corresponding rubbing surface is that half cone-apex angle is greater than 0 degree and be less than the frusto-conical surface of 180 degree.

For increasing ζ and ξ, traction friction mechanism can be many friction disk types friction mechanism, and it is quantitatively all minimum is one and axial staggered two groups of friction plates, is non-rotatably connected to friction member and intermediate piece respectively.

For increasing torque capacity, power transmission friction mechanism can be many friction disk types friction mechanism, and it is quantitatively all minimum is one and axial staggered two groups of friction plates, is non-rotatably connected to friction member and guiding element respectively.

It should be noted that, the implication of the related notion that present specification uses or term is as follows:

Rotate guide mechanism: circumference is relatively rotated the guide mechanism being converted to and at least comprising axial relative movement or mobile trend.Such as, the slides/rolls formula spiral of lead angle strict conformance and not strict conformance or part helix mechanism, radial peg groove mechanism, end face wedge mechanism, end face embeding mechanism, end ratchet mechanism, and, cylinder/end cam mechanism.

Space wedge mechanism: the composite mechanism be made up of rotation guide mechanism and traction friction mechanism.

ζ and ξ: the Important Limit angle of space wedge mechanism, intermediate piece 90 as shown in Fig. 1,16, on the one hand, at least axially conflicted by the traction rubbing surface 72 of its rubbing surface such as 104 with friction member 70, be not orthogonal to the one group of traction friction pair at least comprising of the rotary type traction friction mechanism F1 of rotational axis X with the W that makes a concerted effort forming the normal pressure at conflict position; On the other hand, by its guide surface 94 towards same circumferencial direction, at least axially conflict to the corresponding guide surface 54 of guiding element 50, be not orthogonal to the one group of guiding friction pair at least comprising of the rotation guide mechanism G of rotational axis X with the N that makes a concerted effort forming the normal pressure at conflict position; Common tangent and the mean value hung down as the angle of the plane of rotational axis X at this conflict position, be called the lift angle λ at this conflict position; Again on the one hand, other active force such as elasticity pretension or spacing object can also be acted on, see Fig. 1,4,6 ~ 15 by other surface; In the rotation guiding operating mode of rotating guide mechanism G, namely guiding element 50 starts to have driving intermediate piece 90 constantly along in the trend of arrow P direction Relative friction part 70 rotation in such as Figure 16, can guarantee that the minimum lift angle at the conflict position, both sides surface of guiding friction pair self-locking is defined as ζ, maximum lift angle is then defined as ξ.These two limiting angles define the dynamic and static only motionless every forms of motion with rotating backward of intermediate piece 90 counter-guide 50 forwards completely.Concrete meaning is as follows:

1, when ξ < λ <90 spends, guiding friction pair and traction friction pair all can not friction self-lockings, by the normal pressure N of the friction pair that leads, or its component Q and T, guiding element 50 can cause intermediate piece 90 relative its forward that is arrow P direction trackslip and/or extrude.Therefore, guiding element 50 can not be become a friction piece by intermediate piece 90 wedging with friction member 70.For no other reason than that pressure N is derived from non-resilient power or limits by element structure, just cause intermediate piece 90 only to be promoted Relative friction part 70 friction by guiding element 50 and trackslip and do not extruded by actual.

2, as ζ < λ≤ξ and λ >0 time, guiding friction pair is in constant self-locking state, and traction friction pair is in can not the general static friction state of self-locking.Now, guiding element 50 can be become a friction piece with friction member 70 wedging by intermediate piece 90, but when friction member 70 counter-guide 50 transships, traction friction pair just can be broken through its static friction state/maximum static friction resistance and normally proceed to sliding friction state, and the friction pair that leads then is in constant self-locking state all the time because also not breaking through its static friction state/resistance.Accordingly, space wedge mechanism is in half wedging state, and free wheel device is in non-fully jointing state.

3, when 0< λ≤ζ (situation for ζ >0), traction friction pair is in constant self-locking state, and guiding friction pair is in general static friction state.Correspondingly, when friction member 70 counter-guide 50 transships, intermediate piece 90 just can be broken through the static friction state/maximum static friction resistance of guiding friction pair and have counter-guide 50 and to trackslip the trend of climbing, but because this trend of climbing is stoped (except non-pressure N is derived from elastic force) by the axial force enclosed construction rigidity of space wedge mechanism, therefore, the general static friction state being equal to self-locking is maintained with leading being forced property of friction pair.That is, intermediate piece 90, guiding element 50 and friction member 70 three are forced wedging/be combined into rotate entirety, the situation that there will not be trackslips mutually climbs, except non-overloaded is damaged to structure.Thus space wedge mechanism is in the absolute self-locking/wedging state of similar diagonal-bracing type free wheel device.

From general knowledge, λ equals the situation of ζ, is only present in and is present in reality in theory and not.That is, because of can not simultaneously self-locking and inevitable the trackslipped friction pair that there is one group of not self-locking all the time, the physical essence of space wedge mechanism transmitting torque can only be friction, instead of the friction self-locking that prior art is assert.But limiting angle ζ not by prior art theoretical be familiar with, can not be enlightened by the kinematic relation of the plane wedge mechanism as special case, imagine or disclose out, more can not be derived by its structure.Therefore, do not know that the existence of limiting angle ζ and the prior art of physical meaning just thoroughly cannot be familiar with the actual physical implication of limiting angle ξ that is the angle of wedge, comprise the normality rubbing and trackslip, more can not find, disclose and confirm the physical essence of space wedging, and and then draw the technological scheme based on space wedge mechanism of the application.

Obviously, above-mentioned lift angle λ is exactly the angle of wedge of space wedge mechanism, also claims wedging angle/choke angle, and only when 0 < λ≤ξ, and space wedge mechanism can wedging, and free wheel device can engage.

Hinge structure, according to of the present invention, there is a bag space wedging type friction overrunning clutch provided for shape component, except have above except numerous ideal performance pointed by overall two the basic patent applications combined and beneficial effect, also there is more simple structure especially, less axial/radial size and less quality, be easier to hugeization and microminiaturization, be easier to the many merits applied.By explanation and the accompanying drawing of following embodiment, objects and advantages of the present invention will seem more clear and clear.

Accompanying drawing explanation

Fig. 1 is the axial section according to mono-directional overrun clutch of the present invention.

Fig. 2 is the end view of the ring-type bag shape component in Fig. 1 with force-closed function.

Fig. 3 is the end view of the optional open annular bag shape component in Fig. 1 with force-closed function.

Fig. 4 is according to the axial section with the mono-directional overrun clutch of assembled package shell of the present invention.

Fig. 5 is the plan view in Fig. 4 with the guiding element extending the arm of force.

Fig. 6 is the axial cross-sectional views according to switchable duplex double rolling key clutch of the present invention.

Fig. 7 is the axial cross-sectional views applying bicycle freewheel of the present invention.

Fig. 8 is the axial cross-sectional views applying non-return device of the present invention.

Fig. 9 is the axial cross-sectional views applying overdrive clutch for motorcycle of the present invention.

Figure 10 is the axial cross-sectional views applying automobile-use one-way element of the present invention.

Figure 11 is the axial cross-sectional views applying unilateral bearing of the present invention.

Figure 12 is the axial cross-sectional views applying one-way belt sheave of the present invention.

Figure 13 is the axial cross-sectional views applying loader two axle assembly of the present invention.

Figure 14 is the axial cross-sectional views of the simplification of applying electric bicycle electric wheel hub of the present invention.

Figure 15 is the axial cross-sectional views of the simplification of the Unidirectional output mechanism applying electric bicycle formula drive unit of the present invention.

The flank profil of Figure 16 Shi Tu1Zhong Ge mechanism is to the local expansion figure of same external cylindrical surface radially projecting.

The flank profil of Figure 17 Shi Tu6Zhong Ge mechanism is to the local expansion figure of same external cylindrical surface radially projecting.

Embodiment

Necessary to illustrate: for short and sweet, in the text of this specification and institute's drawings attached, same or analogous component and characteristic portion all adopt identical reference character, and only occur or have during modification giving necessary explanation in their first times.Equally, the also working mechanism of the same or similar mechanism of not repeat specification or process.For distinguishing the identical component or characteristic portion that are arranged on symmetry or corresponding position, this specification addition of letter after its reference character, and when making a general reference explanation or without the need to distinguishing, then additional any letter.

Embodiment one: friction member is the space wedging type friction overrunning clutch provided C1 of ring-type bag shape component

See Fig. 1,2,16, the free wheel device C1 of single-direction transmission comprises best around axis X formation, and the guiding element 50 best in stepped annular.On the interior edge face of its ladder outer shroud, be provided with one group best around the screw type guiding tooth 52 that axis X circumference is uniform, on the inner peripheral surface of the tubular matrix 60 towards the inner extension of its ladder inner ring, be provided with spline tooth best, to be non-rotatably connected by spline pair with the inner ring 40 coaxially set within it in hole.For this reason, the outer circumferential face of the section of being fixedly connected with 45 in the middle part of inner ring 40 is configured with corresponding spline tooth in a complementary fashion.Meanwhile, inner ring 40 inner peripheral surface is provided with the power transmission characteristic surface 64 forming flat key groove, to be non-rotatably connected and transmitting torque with unshowned transmission shaft in its endoporus.Here, the form non-rotatably connected, except spline is connected with flat key, also can adopt the Placement such as not rounded cooperation of such as interference, D font or square opening and prism as required.And on the middle part outer circumferential face of tubular matrix 60, leading thread of then can trackslipping is to being positioned with intermediate piece 90 in the form of a ring best, it is by being arranged on to lead tooth 92 with one group of screw type of guiding tooth 52 in complementary structure on the end face in the face of guiding element 50, chimeric unvaryingly with guiding element 50, to form best around axis X pivotal contact type one-way rotation guide mechanism G.

Free wheel device C1 also comprises and is formed around axis X best and have the friction member 70 of axial force closing function and power transmission characteristic surface 34.This friction member 70 be best one same with the bag shape component 180 of ring-type, and the single component be combined into one best with selectable outer shroud 30.Power transmission characteristic surface 34 constructs the gear teeth 168 on the outer circumferential face of outer shroud 30.Obviously, this characteristic surface 34 can be the arbitrary surface forming such as interference cylndrical surface, the not rounded fitting surface of D font or square shaft, spline tooth, keyway, belt grooves, projection, various hole and screw thread force transferring structure etc., can also be formed directly on an independent annular component when needing, and then be fixed on the outer circumferential face of friction member 70 by known Placement, see Fig. 6 and Figure 13.Equally, this outer shroud 30 is also fastened on friction member 70 by other mode that such as nut connects.The axially middle part of the inner peripheral surface 84 around axis X formation of friction member 70, being coaxially provided with is the disk-shaped annular circumferential recess 78 of plane best.The internal surface of the about half cycle of this circumferential recess 78, extends to the outer circumferential face of friction member 70 best along the two tangent direction H be parallel to each other and H ', and forms prismatic rectangle entrance 82.The inner radial surface 80 of circumferential recess 78, thus extends into the non-closed interior radial surface with U-shaped shape of cross section.Mutually chimeric guiding element 50 and intermediate piece 90 can be directly brought into circumferential recess 78 along Fig. 2 hollow core arrow direction by entrance 82, and by axially through inner ring 40 radial location in friction member 70 endoporus.Friction member 70 is then by being arranged at two bearings 158 between inner circumferential surface and corresponding outer circumferential face 48a and 48b at inner ring 40 two ends, and coaxially radial direction is fixed in inner ring 40.Best, bearing 158 attaching has unshowned seal ring or bearing cap.

This be to be noted that circumferential recess 78 in the form of a ring with entrance 82 in uniform section rectangle, be all realize the best of the present invention but and nonessential setting.In fact, as long as can include such as guiding element 50 and intermediate piece 90 in, circumferential recess 78 and entrance 82 can have arbitrary shape and unequal section.Such as, the cross section of circumferential recess 78 can be rectangular, and the cross section of entrance 82 can be flared trumpet shape because two extension tangent direction H and H ' are not parallel to each other.As a same reason, the inner peripheral surface 84 of friction member 70 also circumference must not closed and correspond to through endoporus, it can be the U-shaped opening shape of such as roughly half cycle completely and correspond to a blind hole, as long as can set out the circumferential recess 78 of the revolving member receiving such as intermediate piece 90 and so on this inner peripheral surface 84.In addition, bearing 158 and inner ring 40 also equal non-invention required, its effect completely can by sliding friction, and the transmission shaft with such as spline tooth or D font non-circular cross-section be arranged in inner peripheral surface 84 replaces respectively.Meanwhile, also above-mentioned radial location can be realized in such a way.Namely, as shown in Fig. 1 ~ 2, at the position axially only corresponding to guiding element 50 of the circumferential end 88 of two circumferential walls of entrance 82, cutting out one in advance can the aduncate circumferential tongue in footpath, to assemble this circumferential tongue of plastic bending afterwards in place at guiding element 50 and intermediate piece 90, realize the rotating encapsulation to this two component and location.

Obviously, the ring-type bag shape friction member 70 that axial force is closed also can be a compostle member.Such as, by such as weld, rivet or bolt connect and so on fastening means, the cup-shaped shell-type limiter element axial restraint one with center hole is connected to the end face of dish type outer shroud 30, and limits circumferential recess 78.Now, also can further by guiding tooth 52 or 92, be formed directly on the interior edge face of dish type outer shroud 30 rigid unitary, and arrange in circumferential recess 78 one independently dish type annulus to serve as friction member.For another example, mode is fastenedly connected by what such as weld, arrange with interference on the outer circumferential face comprising axially middle part and/or outer end at least one circumferential band or circular outer shroud 30 and so on, by at least roughly symmetrical in radial direction, and semicircle inner headed face being provided with two semicircle shell-type limiter elements of semicircle peripheral groove, radial direction is butted into the combined type ring-type friction member that limits complete circumferential recess 78 regularly.Dependency structure be described in more detail and illustrate can see above overall two patent applications combined, be not described further herein.

Continue see Fig. 1, disk-shaped annular circumferential recess 78 is respectively arranged with rotary type traction rubbing surface 72 and power transmission rubbing surface 74.The traction rubbing surface 72 of its left end, rubs with the revolution rubbing surface 104 be arranged on the anodontia end face of intermediate piece 90 and is connected, and forms revolving molding surface contact traction friction mechanism F1.The power transmission rubbing surface 74 of its right-hand member, rubs with the power transmission rubbing surface 58 being arranged on the anodontia end face of guiding element 50 and is connected, and forms and can contact power transmission friction mechanism F2 with the revolving molding surface that guiding element 50 directly transmits friction torque.Traction friction mechanism F1 and rotation guide mechanism G, common composition face type space wedge mechanism, this mechanism, again together with power transmission friction mechanism F2, forms the spatial-wedging friction overrunning clutch mechanism that the axial force of free wheel device C1 is closed.

It should be noted that, the implication that the application " directly transmits friction torque " refers to, the bang path of torque between two components is merely through a friction mechanism, and without any second other mechanism, the quantity of rubbing surface/sheet that itself and this friction mechanism has is without any relation.

Apparently, because disk-shaped annular circumferential recess 78 is arranged to planar disc but not cone plate-like best, therefore, free wheel device C1 can not ask the coaxial accuracy between the combination of guiding element 50 and intermediate piece 90 and friction member 70 in theory.That is, can not to the rotation guide mechanism G in overrunning clutch mechanism, between traction friction mechanism F1 and power transmission friction mechanism F2 three and the coaxality of three and axis X do excessive demand, especially when rotating speed is not high, as long as two face contact Rotating friction pair is perpendicular to axis X, and only there is perceptible guiding element in relative rotation 50 and intermediate piece 90 is hardly coaxially set each other.And relative modern crafts, the coaxality ensureing between these two annular components is only the work of a simple and low cost.Therefore, this, by the requirement and the cost that significantly reduce making, assembling and use free wheel device C1, is significantly superior to antipodal prior art.

For closing/shutoff entrance 82 best, also such as to weld, to rivet, to glued joint, screw pair, radial direction or end face screw, interference or Spielpassung (as Fig. 8,14) and so on fastening or be non-ly fastenedly connected mode, at least one sealed piece 190 is provided with, as the complete circle of the best in entrance 82 or on the outer circumferential face of the friction member 70 of its outside.Need free wheel device C for making high speed rotating] carry out revolution balance time, best in the remaining space be not filled of sealed piece 190 internal side diameter entrance 82, one such as has complementary structure best arc balancing component/balancing weight 170 with this remaining space can be set.This balancing component 170 is radially oriented best, such as, by through wherein, and is fixedly connected at least one fixing pin 172 in the axial bore 81 of friction member 70, see Fig. 1,2,10.And from general knowledge, replace fixing pin 172 more can obtain the benefit promoting friction member 70 rigidity with screw, and, also on the rubbing surface 72 and 74 corresponding to two ends bottom U-shaped internal surface 80, revolution balance can be carried out in the mode arranging axial bore.Obviously, balancing component 170 can directly replace sealed piece 190 as described above.

In conjunction with Figure 16, the detailed relation and structure characteristic of rotating guide mechanism G are described again below.Wherein, the guide surface 54 and 94 of the often pair of end-surface type indented spirals type guiding tooth 52 and 92 radially extended, can be bonded to each other, and form the spiral guiding friction pair of one group of face contact.That is, these two have the guide surface 54 and 94 of complementary structure, are respectively towards single circumferencial direction and lift angle is the screw type flank of tooth of λ best.Usually, 0< λ≤ξ, distinguishingly, ζ < λ≤ξ or 0< λ≤ζ (as ζ >0).The non-guide face 56 that is separated by, gap and 96 X that parallel to the axis best, can not cause wedging during to ensure that both sides' circumference is conflicted best.

Easy understand, multiple guiding teeth 52 on guiding element 50 end face, in fact be exactly the chisel teeth of space wedge mechanism, its guide surface 54 little by little axially draws rubbing surface 72 near the rotary type of friction member 70 towards a circumferential side, and surrounds multiple end face wedge shape space circumferentially respectively with the latter.And the multiple guiding teeth 92 be arranged in the plurality of wedge shape space are exactly wedging, it is because of must not radial motion and be mutually merged into a part best, i.e. the intermediate piece 90 of overall ring-type.

For making sliding corner as much as possible close to zero, free wheel device C1 is also provided with elasticity pre-tightening mechanism best.This mechanism mainly comprise one by Spring Steel Wire make can the ring waveform spring 150 of axial compression, it is arranged in the tubular cavity rotating guide mechanism G internal side diameter, namely be arranged on interior edge face and tubular matrix 60 outer circumferential face of guiding tooth 52,92, and in the tubular interspace that limits of the guiding element 50 therebetween end face relative with both intermediate pieces 90, see Fig. 1.Certainly, spring 150 also can be one or more torsion spring, sheet wavy spring, or the elastic element with at least one of arbitrary form and any setting position be made up of elastic material, as long as it can cause revolution rubbing surface 104 flexibly to be conflicted all the time to traction rubbing surface 72 best.Certainly, guide surface 94 preferably also should be caused also flexibly to conflict all the time to guide surface 54 simultaneously.In addition, elasticity pre-tightening mechanism also by suppressing mode to the other side by one with intermediate piece 90 or the non-rotatable component be connected of friction member 70, being set up indirect frictional connection between the two, can be produced traction friction torque equally.

Such as, radial sheet wavy spring is set between non-guide face 56 and 96, two guide surfaces 54 and 94 just can be caused to have the trend that circumference is rotated in opposite directions all the time, namely cause and rotate the trend that guide mechanism G has rotation guiding all the time.So intermediate piece 90 can remain on its accurate wedging station being positioned at wedge shape space circumference smallest end, being in can in the threshold state of wedging at any time.In this threshold state, the axial freedom/gap of rotating guide mechanism G is δ, and circumferential degrees of freedom/gap is ε, and two-freedom is greater than zero all best, see Figure 16.Wherein, the more detailed description of related elastic pre-tightening mechanism and diagram, can see above overall two patent applications combined, be not described further herein.

Easily understand, be reduce the sliding corner of free wheel device C1 and circumferential inertia impact, promote its action response and sensitivity, above-mentioned degrees of freedom δ and ε arranges the smaller the better, and little with ε be the most desirable to zero.

As above as described in overall two patent applications combined, elasticity pre-tightening mechanism also non-invention required.When not arranging this mechanism, free wheel device C1 still can rely on the special setting of the lift angle λ of 0 < λ≤ζ, and relies on inertia during such as circumference rotation to cause intermediate piece 90 to enter wedge, although reliability is not high enough.Such as, situation during output mechanism as impulse stepless gear box.Or, for reliably entering wedge, namely make intermediate piece 90 reliably proceed to guiding element 50 can be connected with friction member 70/combine with driving/wedging becomes working procedure and the state of a friction piece, the external diameter of intermediate piece 90 can be arranged best compare the slightly large of guiding element 50, in radial vibration, rubbing contact also can obtain needed for wedge frictional force whereby to internal surface 80 to make it.For this reason, corresponding radial degrees of freedom should be provided with between friction member 70, bearing 158 and inner ring 40 three.Obviously, this will pay the cost such as reducing meshed transmission gear quality.

The working procedure of free wheel device C1 is very simple.When guiding element 50 starts to have the initial instant making to drive the trend of rotating along arrow P direction Relative friction part 70 in Figure 16 constantly, friction member 70 is by the zero load/traction friction torque by traction friction mechanism F1, draw the intermediate piece 90 rotating guide mechanism G, counter-guide 50 to rotate guide movement along arrow R direction.What this rotation guide movement produced moves axially/tension force, in the end face wedge shape space that the moment wedging of guiding tooth 92 is surrounded at guide surface 54 and traction rubbing surface 72, namely guiding element 50 is become a friction piece with friction member 70 wedging by intermediate piece 90, traction friction mechanism F1 is thus while axial engagement, this tension force also by guiding element 50 swelling at once on another interior edge face i.e. power transmission rubbing surface 74 of friction member 70, to form the closed mode connected of conflicting of axial force, power transmission friction mechanism F2 is caused also synchronously to engage, and guiding element 50 and friction member 70 are directly connected into a friction piece.

So free wheel device C1 engages along with the wedging of space wedge mechanism.The driving torque M0 from not shown transmission shaft imported into by the inner ring 40 in tubular matrix 60 endoporus, be divided into via rotating guide mechanism G and traction friction mechanism F] the wedging friction torque M1 that transmits, and via the power transmission friction torque M2 that power transmission friction mechanism F2 directly transmits, pass to friction member 70 and the outer shroud 30 with its consubstantiality respectively, then pass to the unshowned gear engaged with the gear teeth 168.Wherein, M0=M1+M2.Obviously, the size of above-mentioned axial tension force, wedging power and each frictional force, is all proportional to M1, namely M0 completely adaptively.Certainly, torque by reverse path transmission, and can not have any essential difference yet.

It should be noted that, as mentioned above, free wheel device C1 only has in the arranging of ζ < λ≤ξ, the antioverloading that driving torque overload is skidded relatively adaptively can be obtained and destroy function, but prerequisite is torque must be transmitted to friction member 70 by guiding element 50, namely edge is as above by the path direction transmission of axle to wheel, instead of on the contrary.

Afterwards, when guiding element 50 starts to have the initial instant making to separate the trend that wedge rotates along arrow R direction Relative friction part 70 in Figure 16 constantly, guiding element 50 is done to remove the rotation of rotating the leading role of guide mechanism G relative to intermediate piece 90 by starting.Therefore, the normal pressure between guide surface 54 and 94 and the rotation leading role of rotating guide mechanism G, disengage disappearing in a flash and simultaneously of trend mutually by along with two guide surfaces produce.Nature, two friction mechanism F1 and F2 worked based on the moving axially of this mechanism G/tension force and whole space wedge mechanism, will be separated immediately or separate wedge.So free wheel device C1 terminates to engage and starts to surmount rotation, that is, intermediate piece 90 follow guiding element 50 start Relative friction part 70 along R direction friction trackslip.

So far be not difficult to find, torque is all transmitted via face contact friction pair in free wheel device C1, there is not any discrete elements in its bang path, there is not any frictional force relevant to centrifugal force, more there is not any revolving member that can not balance and any uneven radial force or its component, all active forces only have axial thrust load and/or circumferential component, and the effective object of these two component all has high axis and/or circumferential rigidity.Therefore, hinge structure, especially roller type wherein and diagonal-bracing type free wheel device, according to the space wedging type friction overrunning clutch provided C1 with bag shape component of the present invention, not only be provided with the advance of matter and extremely significant comprehensive advantage, and have more the almost complete characteristic that should possess for desirable free wheel device.

Such as, because the hollow ring comparing prior art is high rigidity, and there is the transmission accuracy of more reliable wedging/latching characteristics and Geng Gao far away; Because leading surface contact friction is secondary, two torque flow transmission mode, and friction mechanism F1 and F2 can be arranged to have the structure of many friction plates, structure or the frusto-conical surface type friction pair structure of half cone-apex angle all between 0 ~ 180 degree that attaching has larger friction coefficient material/element, and there is unrivaled transmission capacity and impact resistance; Because having the high speed capability corresponding to associated materials intensity without centrifugal inertia force; There are wearing and tearing hardly because rotating guide mechanism G, the frictional force of friction mechanism F1 and F2 electrically isolates from centrifugal inertia force and can auto-compensation wearing and tearing, and the frictional strength of face contact comparatively linear contact lay be significantly low, and to have be far away the operating life of length; Because of noiseless, nonelastic fatigue and the low frictional resistance electrically isolating from centrifugal force, and there is the excellent transmission efficiency surmounting characteristic and Geng Gao; Because of the high rigidity of wedging direction/axis, there is light switching characteristics; Because the size of circumferential degrees of freedom ε crucially can be limited according to need and rigidly and then can do any perceptible inertia geometry motion without the need to intermediate piece 90 in wedging or solution wedge process, and there is high folding sensitivity and responsiveness; Surmount characteristic and folding sensitivity because of excellence, and there is when high frequency folding more stable performance; Because all wearing and tearing change the size of limiting angle ζ and ξ hardly on geometric parameter, and can break-in/running-in and along with break-in/running-in improving performance, also therefore there is the characteristic easily regulating and repair simultaneously; Because not producing radial force during wedging without the need to the thick radial rigidity that strengthens of large ring, and then there is less radial dimension; Because of the less the number of components of simpler structure, and there is more economical making and assembly cost, and higher manufacturing efficiency and broader application area.Technological merit for the present invention and beneficial effect and how to eliminate surface friction drag to realize the contactless more detailed description and the diagram that surmount rotation, can see above overall two patent applications combined, be not described further herein.

Particularly, 50mm is not less than at the internal diameter of guiding element 50,98mm is not more than at the external diameter of ring-type bag shape friction member 70, axial width is not more than 41mm, and service factor and friction factor are when being respectively 3.0 and 0.1, half cycle of only having an appointment can the free wheel device C1 of wedging and power transmission, and its nominal torque at least reaches 3,725Nm about 5 doubly to the magnitude level of prior art, exceed such as equipment for power transmission and distribution medi-spring operation mechanism or impulse stepless gear box exponentially to the actual demand of this ratchet.Further, also correspondingly the radial ring of increase ring-type bag shape friction member 70 is thick for the internal diameter of reduction guiding element 50, and nominal torque also can significantly increase.And after implementing revolving meber balance, its working speed just may be up to the design limit of bearing 158.Therefore, for equal torque capacity, free wheel device C1 will have less axial, radial dimension and quality undoubtedly.Further, the torque upper limit far beyond existing 1MNm level on high rotating speed is easy to.

It should be noted that, for seeking larger design freedom and making the easier wedging of space wedge mechanism or separate wedge, the present invention also has the technological means of various lifting limiting angle ζ and ξ numerical value.Comprise, the guide surface 54 and 94 rotating guide mechanism G is arranged to the tilted spiral type flank of tooth, the rubbing surface 72 and 104 of traction friction mechanism F1 is arranged to frusto-conical surface, to cause angle/half cone-apex angle of guide surface 54 and 94 or rubbing surface 72 and 104 and axis X in shaft section no longer to equal 90 degree, but equal other value between 0 ~ 180 degree as shown in Figure 9; Traction friction mechanism F1 is arranged to many friction disk types friction mechanism; And, the material or element that possess larger friction factor are attached at least one in rubbing surface 72 and 104.Such as, when static friction coefficient is 0.1, ζ and ξ in free wheel device C1 equals 0 degree and 11.4 degree respectively, and only the rubbing surface of traction friction mechanism F1 need be arranged to this measure of frusto-conical surface that half cone-apex angle equals 30 degree, and above-mentioned limiting angle just rises to 5.6 degree and 17.02 degree respectively.Here should incidentally, this specification has given literal definition clearly about limiting angle ζ and ξ and explanation, and without the need to paying any performing creative labour, those of ordinary skill in the art all can derive its functional relation/formula accordingly.

From general knowledge, for free wheel device C1 when increasing equivalent diameter torque capacity/transmission capacity and reduce axial internal force, traction friction mechanism F1 and power transmission friction mechanism F2 also can according to known technology, be set to many friction disk types friction mechanism respectively or simultaneously as described above, and therefore there is one group of quantitatively more than one traction friction pair or power transmission friction pair.Such as, see Fig. 1, by the two groups of axial pin be arranged in through hole or outer circumferential face breach, by axially respectively between rubbing surface 72 and 104 and power transmission rubbing surface 58 and 74, each each one group of ring-type outside friction disc at least comprising, non-rotatably be connected to traction rubbing surface 72 and power transmission rubbing surface 74 respectively, again by such as spline pair, by each each one group of ring-type inner attrition piece at least comprising of correspondence, with staggered form axial with above-mentioned outside friction disc, respectively correspondingly and be non-rotatably connected on inner ring 40 outer circumferential face, and be positioned on the outer circumferential face of annular end face flange of revolution rubbing surface 104 inner ring side.

Easily expect, if axially arrange an intermediate piece 90 symmetrically again between power transmission rubbing surface 58 and 74, and form another respectively symmetrically with guiding element 50 and friction member 70 and rotate guide mechanism G and draw friction mechanism F1, so, free wheel device C1 will no longer have power transmission friction mechanism F2 but has the traction friction mechanism F1 that two share same friction member 70 simultaneously.

It should be noted that, as described in definition, the present invention does not make concrete restriction to rotation guide mechanism G and guiding tooth 52,92 thereof, and it must not have best helical tooth structure.Therefore, this mechanism G and guiding tooth thereof can have the form and shape that possess arbitrarily and rotate guide function.Guiding tooth can be arranged on end face/side face by discrete form, also by the such as single head shown in Fig. 9 or multiple-threaded form, can be arranged on corresponding inside/outside side face to circumference continuity.And arranging in form in rear one, it can be arranged to have the helical tooth of such as rectangle, trapezoidal, zigzag fashion or triangle prismatic shapes best.As a same reason, as long as axial complementary laminating/conflict can be realized best, the tapering shape rotary type rubbing surface of respective two groups of revolution friction pairs of traction friction mechanism F1 and power transmission friction mechanism F2, can form based on the revolution of arbitrary curve/bus, and can be provided with in order to heat radiation or the discontinuous surface of groove getting rid of liquid/gas.

Therefore, free wheel device C1 can have such modification.Namely, by the screw type of mechanism G wherein guiding tooth 52 and 92, be separately positioned on the outer circumferential face of tubular matrix 60 and the inner peripheral surface of intermediate piece 90, or, the inner peripheral surface of the outer circumferential face being arranged on intermediate piece 90 and the annular end face flange being formed at the radial outer rim side of guiding element 50 (is equivalent to the position of radial upset intermediate piece 90 and guiding element 50).Or, remove its inner ring 40, by techniques such as such as precision casting, casting, die casting or injection mouldings, guiding tooth 52 or 92 is directly formed in as on the corresponding interior edge face of the friction member 70 of bag shape component rigidly, there is to make friction member 70 be modified to bag shape guiding element or the bag shape intermediate piece of axial force closing function.Correspondingly, again figure] in intermediate piece 90 or guiding element 50 and friction member 70 axial direction between, radial direction is inserted an endoporus and is fixedly linked to the dish type friction ring of a transmission shaft, thus free wheel device C1 to be modified to guiding element be bag wheel of a shape component one shaft drive formula free wheel device, or, be modified to axle-shaft drive formula free wheel device (inner peripheral surface of guiding element 50 is coupled with another transmission shaft) that intermediate piece is bag shape component.When the time comes, this dish type friction ring should finally be inserted during assembling.

In addition, if needed, such as, when being used as stepless positioning hinge, friction member 70 also can be the bag shape component of non-complete loop.That is, when need axially to extend the tubular matrix 60 of such as guiding element 50 so that its can not radial through entrance 82 time, see Fig. 1 ~ 2, circumferential breach can be set the two ends in the axial one end at entrance 82 place or when not having outer shroud 30.Such as, will be positioned at the inner peripheral surface of the just in time half cycle of inner peripheral surface 84a one end, along two tangent directions be parallel to each other being parallel to H or H ', radial direction extends to the outer circumferential face of friction member 70, and forms a breach allowing tubular matrix 60 to insert/pass through.So inner peripheral surface 84a extends into the non-closed interior radial surface with U-shaped shape of cross section equally, friction member 70 is turned into the U-shaped trip ring of a likeness in form counterweight, see Fig. 3.Certainly, now should by the above-mentioned mode arranging balancing component 170, in the entrance 82 expanded, arrange one best there is the arc casting die of complementary structure, with radial location tubular matrix 60 with this entrance.

Should be particularly noted that, free wheel device C1 also can have the modification of the parallel space wedge mechanism comprising two rotation guide mechanisms.That is, there is guiding tooth 92e and 52e of rotation guide mechanism Ge that 0 < λ≤ζ is arranged, on the inner ring side being separately positioned on intermediate piece 90 and guiding element 50e.And there is the guiding tooth 92 and 52 of the rotation guide mechanism G that ζ < λ≤ξ is arranged, be then separately positioned on on the outer rim side of the same intermediate piece 90 held of the tooth 92e that leads and guiding element 50.The annular region being positioned at guiding tooth 52 radially inner side of guiding element 50, is provided with face type circumferential recess.Be housed in the ring-type guiding element 50e in this circumferential recess actively, best by spline joint mode, be non-rotatably connected on the outer circumferential face of this groove, on the outer circumferential face of namely tubular matrix 60, thus form circumference one with guiding element 50.Meanwhile, at least one elastic element being specially belleville spring, with the form of pre-pressing, is arranged between guiding element 50e and the wall of this circumferential recess.Guiding element 50e is axially limited by the snap ring that is arranged on tubular matrix 60 outer circumferential face between itself and intermediate piece 90.Correspondingly, spring 150 is the helical compression springs being set on intermediate piece 90 and guiding element 50 outer circumferential face, conflicts the corresponding flange to these two outer circumferential faces respectively in its two ends.Relevant concrete structure, the spatial-wedging friction connector by name that can propose on the same day in the application see the applicant, and jacking equipment spatial-wedging fall-prevention by name, anti-hypervelocity emergency brake device two patent applications.

Arrange, rotate the circular gap of guide mechanism G and Ge, the latter can be caused to enter prior to the former and rotate guiding operating mode, and there is such effect.Namely, in engaging process, when guiding tooth 52 and 92 both sides' circumference starts mutually to conflict, the climbing type that trackslips corresponding to guiding tooth 52e and 92e rotates the axial compression of leading role, does not cause guiding element 50e and 50 to start indirectly rigidity each other in the axial direction and conflicts.

The effect of modification like this is, the friction torque at free wheel device C1 wedging process initial stage, has the feature of the linear rising corresponding to belleville spring elastic force.And, correspond to rotate guide mechanism Ge there is the space wedge mechanism that resilient wedge makes a concerted effort, also playing guiding simultaneously and ensure the effect with the absolute wedging of space wedge mechanism that rigid wedge is made a concerted effort corresponding to and rotate guide mechanism G, is in fact also its elasticity pre-tightening mechanism.And if be added into such as attitude reference device D enter wedge control mechanism, this modification because having flexible wedging/joint capacity, and will can be used as the glider that controllably can terminate coasting mode at any time of Motor Vehicle best.

Obviously, if on intermediate piece 90 inner peripheral surface in this modification, arrange along flange radially in tubular matrix 60 interior edge face, to non-rotatably be connected to the inner ring 40 of tubular matrix 60 again, change into and be non-rotatably connected to this flange, so, guiding element 50 and intermediate piece 90 in fact will exchange role.

Embodiment two: limiter element is the space wedging type friction overrunning clutch provided C2 of ring-type bag shape component

Free wheel device C2 is the modification to free wheel device C1 structure, its object is to guarantee as ζ < λ≤ξ, torque by outer shroud 30 have when inner ring 40 is transmitted overload skid antioverloading destroy function, and as described later attitude reference device D can be set at entrance 82 place.For this reason, ring-type bag shape component must have the function of guiding element.For easy to make, see Fig. 4 ~ 5, this guiding element is configured to force-closed formula compostle member, and being non-rotatably connected with the bag shape component 180 as ring-type by guiding element 50 forms.Wherein, bag shape component 180 has identical structure with the friction member in Fig. 1 ~ 2.For being non-rotatably connected with bag shape component 180, on the outer circumferential face of guiding element 50 roughly in the form of a ring, be provided with the flanged type arc arm of force 55 extending to sealed piece 190 internal surface in the mode of cross sectional shape complementary along entrance 82 radial direction.Two circumferential flank surface 66 of the arm of force 55, are and can complementarily engage with two circumferential walls of entrance 82 respectively simultaneously, and the power transmission characteristic surface of transmitting torque.So, together can be arranged on the outer circumferential face of tubular matrix 76 of disk-shaped annular friction member 70 with trackslipping with intermediate piece 90, and conflict to supporting the guiding element 50 of end face 189, because of its circumferential flank surface 66 and the complementary laminating of U-shaped internal surface 80 and bag shape component 180 non-rotatably connect into circumference one.In addition, tubular matrix 76 is non-rotatably linked into an integrated entity by spline with the inner ring 40 in its endoporus.And by the inner peripheral surface of ring-type sealed piece 190, the radial direction of the arc-shaped outer surface 57 of the arm of force 55 is limited, or limited by the radial direction of inner ring 40 pairs of friction members 70, guiding element 50, intermediate piece 90 and friction member 70 together radial direction are fixed in circumferential recess 78.

Visible, in free wheel device C2, as the bag shape component 180 of ring-type, be in fact exactly a friction plate be non-rotatably connected with guiding element 50 in power transmission friction mechanism F2.Further, power transmission friction mechanism F2 combines respectively rigidly with friction member 70 and guiding element 50 no longer as previously mentioned, but non-rotatably combines respectively.

Obviously, bag shape component 180 also can with outer circumferential face on be provided with the above-mentioned arm of force intermediate piece 90 roughly in the form of a ring form combined type ring-type bag shape intermediate piece.As mentioned before, guiding tooth 52 or 92 also can be set directly on such as support end face 189 best, or, with similar single head or multiple-threaded form, be separately positioned on to circumference continuity the outer circumferential face of guiding element 50 or intermediate piece 90, and on the internal surface 80 of the about half cycle of circumferential recess 78.In this way, clutch C2 various type is axle-shaft drive formula free wheel device, and can have intermediate piece self and provide wedge shape space and the unexistent outside wedging pattern of prior art being subject to tension force effect from inside to outside.Certainly, guiding element 50 now should be same as shown in Fig. 1 completely, and in the axial direction with friction member 70 arranged in series.Meanwhile, therefore this modification will have larger design freedom, and more convenient configuration controls the attitude reference device D in the similar clutch C3 in its wedgeable ability and direction.

In addition, for the benefit of friction mechanism F1 and F2 is arranged to many friction disk types friction mechanism, friction member 70 itself also can be combinations thereof component.That is, rubbing surface 104 and 72 in FIG and/or between 58 and 74, radial direction inserts the dish type friction ring in a roughly ring-type outer circumferential face being provided with the above-mentioned radial arm of force.In fact, the friction member 70 in Fig. 1 is exactly product and the result that this friction ring and bag shape component are combined into single component best or at the most.

Except arranging the arm of force 55, the mode be non-rotatably connected between two co-axial member also can adopt any one known solution of the prior art.Such as, by arranging the mode of connecting pin in axial bore 81 and 59, by the projection of cotter way formula embeding mechanism and groove being separately positioned on the mode between two components on opposed facing end face or on side face, or, by arranging the mode etc. of spline tooth between inner peripheral surface 84 and the corresponding outer circumferential face of the annular end face flange of respective members.

Embodiment three: the two-way space wedging type friction overrunning clutch provided C3 of switchable duplex

See Fig. 6, free wheel device C3 is the controllable clutch of the mixing/dual power drive system that can be applied to large-scale water surface naval vessels best, is the modification to free wheel device C1.

First, for transmitting the torque from two different prime mover, it comprises two overrunning clutch mechanisms arranged along axis X.Friction member 70a and 70b same respectively with ring-type bag shape component 180a and 180b of these two clutch mechanismes, be axially combined into a part best, and two entrance 82 circumferences is just in time staggered half cycle, are namely staggered 180 degree.For transmitting large torque, conveniently change component separately, the outer shroud 30 being formed with the gear teeth 168 is arranged to an independent component best.The dual Placement that this outer shroud 30 uses interference fit to be connected with key 202 simultaneously, be fixed on the outer circumferential face of friction member 70, and by being arranged on bearing 158a and 158b be positioned on friction member 70 liang of outer end annular end face flange 162a and 162b outer circumferential face, be rotatably mounted in unshowned gear-box/frame.Simultaneously, intermediate piece 90a and guiding element 50a and intermediate piece 90b and guiding element 50b combination separately, secondary by incomplete spline tooth, be non-rotatably connected to respectively and be coupled directly to best on the transmission shaft 200a of two prime mover and the outer circumferential face of 200b end.

In fact, also more ring-type bag shape friction member 70 coaxially can be combined into a part when needing, or rigid unitary, such as 3 or 4, to accommodate the combination of more intermediate piece 90 and guiding element 50, form more overrunning clutch mechanism, and by corresponding Hollow Transmission Shafts with more with to hold or heterodoxy prime mover is coupled, to import driving torque into.Certainly, also driving torque/poower flow can be spread out of inversely, such as, when the double clutch in motor drive system.

Secondly, for transmitting the torque of two circumferencial directions, the corresponding guiding tooth of free wheel device C3 has been endowed two circumferential wedging/force transfer capacity.For this reason, see Figure 17, the non-guide face 56 and 96 of guiding tooth 52 and 92, is set individually to go up circumferentially and is symmetrical in guide surface 54 and 94 best.That is, respectively towards the lift angle λ that four groups of guide surface 54a and 94a, 54b and 94b, 54c and 94c and 54d and 94d four of two circumferencial directions are complementary _a, λ _b, λ _cand λ _d, equal λ all symmetrically, and, 0 < λ≤ξ.So guiding tooth 52 and 92 is modified to cross section and is at least roughly trapezoidal radial mode end-tooth.

Again, for selectively limiting the transmission condition of free wheel device C3, be also respectively arranged with two duplicate cylinder cam-type attitude reference device Da and Db.This Liang Ge mechanism Da and Db comprises, and can be separately positioned on verge ring 120a and 120b on transmission shaft 200a and 200b outer circumferential face axially slidably, and the radial mode orienting pin 124a be arranged on intermediate piece 90a and 90b inner peripheral surface and 124b.Wherein, on the inner peripheral surface of verge ring 120a and 120b, be evenly equipped with at least one axial pawl 122a and 122b extended in opposite directions respectively best, the latter's head is respectively arranged with cylinder cam-type guide groove 130a and 130b with three different step sections.Orienting pin 124a and 124b dodges breach 62a and 62b through what be arranged at tubular matrix 60 outer end, extends in guide groove 130a and 130b respectively accordingly, is limited on the different circumferential positions of guiding element 50 to cause intermediate piece 90a and 90b by axial pawl 122.Accordingly, transmission shaft 200a and 200b end do not cut out on the outer circumferential face of spline tooth, be respectively arranged with axial baseline trough 126a and 126b extending to end receiving axial pawl 122a and 122b slidably.

Contrast Figure 17, attitude reference device Da and Db has respectively and such arranges effect, namely, when verge ring 120a with 120b respectively relative transmission shaft 200a and 200b move axially along arrow Y or Z direction, when causing orienting pin 124a and 124b to be positioned at three different step sections of guide groove 130a and 130b, intermediate piece 90a and 90b is by circumferential positions different for three of being in counter-guide 50a and 50b respectively accordingly, corresponding to it be greater than best zero circumferential degrees of freedom, can to conflict allowing to correspond to one group of guide surface 54a and 94a or 54b and 94b of a certain circumferencial direction/wedging, as shown in left one side of something of Figure 17, or/wedging of all cannot conflicting, as shown in right one side of something of Figure 17.

Should it is emphasized that, the object of attitude reference device D is set, exactly intermediate piece 90 is each defined in the two or more different circumferential zones of counter-guide 50, be in order the circumferential degrees of freedom that the intermediate piece 90 in this region has, only allow intermediate piece 90 can in zero, one or two circumferentially enters wedge.Therefore, attitude reference device Da and Db must not have transmission shaft 200a and 200b, more must not be arranged in the inner peripheral surface 84 of friction member 70.What attitude reference device D also can be arranged on friction member 70 corresponds to K, J place of entrance 82, when the arm of force 55 be particularly provided with as shown in Figures 4 and 5 when guiding element 50.This mechanism D can be cylinder cam-type moving guiding mechanism, can be by the eccentric wheel be arranged in axial bore 81 and/or 59, the embeding mechanism that the elasticity peripheral groove that the straight spring of two rhizoid shapes that can be extended out by intermediate piece 90 radial direction is formed forms also can be arranged on the epicyclic singleplent helical gear mechanism etc. being also engaged to the such as duplex of guiding element 50 and intermediate piece 90 outer circumferential face in entrance 82 respectively.About the more detailed structure of attitude reference device D and guiding groove thereof etc., modification and explanation, can see above overall two patent applications combined, and the patent application being called the spatial-wedging twisting operation instrument that can work continuously that the applicant proposes on the same day in the application, be not described further herein.

Therefore, by handling attitude reference device Da and Db, just can change the operative orientation of two the space wedge mechanisms being positioned at double rolling key clutch C3 left and right side respectively, namely surmount the circumferencial direction corresponding to rotation, and can at least make it enter the operating mode being definitely separated idle running partially.This is by being particularly suitable for needing carrying out at any time the large surface warship being provided with dual power drive system of powershift, on-bne repair and test run arbitrarily, to replace the SSS timing clutch of the prior art without this function.Certainly, free wheel device C3 may be used for the application of all mixing/double dynamical driving taking gear as common the first component driven, comprise the drive line etc. of double dynamical helicopter, double-power motor vehicle, especially for eliminating the more simple variant handled after attitude reference device D.Except having the advantage of torque advantage and the above-mentioned use pointed out, such as being not more than 150mm/300mm and service factor in the inside/outside footpath of friction member 70 is when 3.0, its nominal torque is at least not less than 55, (be set to unidirectional to then double during tooth) outside 000Nm, also have especially without rigid impulse and the greater advantages that do not take up room.In fact, free wheel device C3 is integrated with the function of two SSS timing clutches and a gear, and only need the space that shared original gear must occupy, thus eliminate two needs SSS timing clutches of independent support and the axial space shared by corresponding four coupling, reduce the axial length of transmission system exponentially, reduce installation difficulty, installation work-hour and financial cost etc.

Apparently, the simple rotating member of the first component jointly driven when mixing/dual power source not such as gear, belt pulley and so on, but when such as generator, blower fan or water pump etc. cannot be arranged at the working machine of its outer rim side, the free wheel device C3 of duplex will be no longer applicable, and two independently axle-shaft drive formula clutches (friction member 70 and another transmission shaft direct-coupling) should be resolved into, as prior art, be separately positioned on the axial two ends of working machine.Easy understand, the clutch of this decomposition also directly can be used as the bidirectional-sliding device that controllably can terminate coasting mode at any time of Motor Vehicle.

Understandable equally, attitude reference device D also can be applicable to unidirectional free wheel device, surmounts ability with what controllably cancel mono-directional overrun clutch.Such as, mono-directional overrun clutch is used as the situation of Motor Vehicle one-way sliding device, overrunning clutch sheet, or, reciprocal for operative orientation two mono-directional overrun clutchs are combined into one according to axial stiffness shown in Fig. 6, and substitute transmission shaft 200a and 200b with same inner ring 40 as shown in Figure 1, cause the clutch of duplex to become one, with mono-directional overrun clutch, there is the double rolling key clutch of equal transmission capacity or the situation of motor-vehicle skid.

Typical apply embodiment illustrates

Shown in Fig. 7 is application bicycle freewheel C4 of the present invention, and it is the direct modification of free wheel device C1.Wherein, replace nonessential bearing 158 with two groups of balls 192, replace the gear teeth 168 with sprocket tooth 222.On the other end outer circumferential face of inner ring 40 with outer raceway, be correspondingly provided with the end cap 224 equally with outer raceway by screw pair, to retrain this two groups of rollers 192.The nominal torque of this flywheel C4 when the external diameter of friction member 70 is not more than 44mm is at least not less than 358Nm (service factor is 3.0), is far longer than needed for prior art and reality.Apparently, this flywheel C4 also can be used as the flywheel of electric bicycle etc.And if need less sprocket wheel radial dimension, sprocket tooth 222 also can change on the outer circumferential face of the such as right-hand member being located at inner ring 40, see Figure 14.Now, friction member 70 should non-rotatably be connected on the rotary member in the torque downstreams such as wheel hub.

When removal outer shroud 30 and inner ring 40, with screw 176, sealed piece 190 is removably fastened on the outer circumferential face of friction member 70, and radially go out in one end of friction member 70 outer circumferential face the arm of force 196 that can be fixedly attached to frame, free wheel device C1 is just modified to non-return device C5, therefore bag shape component 180 is ring-type roughly, see Fig. 8.Best, bearing 158 should have sealing function, such as, by arranging the mode of bearing (ball) cover in axial outer end.In parameter, when the external diameter of friction member 70 and transmission shaft 200 equals 965mm and 490mm respectively, the nominal torque of non-return device C5 is at least not less than 3.79MN.m (service factor 3.0), the level of 0.9492MN.m when being far longer than prior art equivalent diameter.

In addition, be not difficult to expect as those of ordinary skill in the art, according to the present invention, such as, remove the outer shroud 30 shown in Fig. 1, inner ring 40 and sealed piece 190, best bearing 158 is replaced with sliding bearing or needle bearing, free wheel device C1 just various type is small-sized or miniature free wheel device.It is not only significantly better than prior art, can have less external diameter and larger torque etc., and is easier to the follow-up making of user's additional resin parts etc. voluntarily on such as outer circumferential face.Such as, when the internal-and external diameter of friction member 70 equals 3.0mm/8.2mm respectively, its nominal torque is at least not less than 2.0Nm (service factor is 3.0), 4 times of load levels to prior art 0.49Nm (internal-and external diameter is respectively 6mm/12mm), and when internal-and external diameter is respectively 6mm/12mm, its nominal torque is more at least not less than 6.0Nm (service factor is 3.0).Visible, above-mentioned torque and size are better than the technical parameter of the prior art stepless positioning hinge that the tight product of the such as electronics such as notebook, duplicating machine in reality use all exponentially.

Shown in Fig. 9 is motorcycle starting free wheel device C6, and it is the direct modification of free wheel device C1 equally.Wherein, intermediate piece 90 is sleeved on the outer circumferential face of tubular matrix 60 rotationally.For being easier to make and reduce fabricating cost, the one group of screw type guiding tooth 52,92 rotating guide mechanism G, with similar single head or multiple-threaded form, is separately positioned on the relative interior and outer circumferential face of this two component to circumference continuity.Spring 150 is modified to and is arranged on intermediate piece 90 small end outer circumferential face, and two terminations are housed in the torsional mode helical spring of the corresponding axial bore of the opposing end surface being arranged in intermediate piece 90 and guiding element 50 respectively.When the internal-and external diameter of friction member 70 is 24mm/49mm, the nominal torque of free wheel device C6 is at least not less than 450N.m (service factor is 3.0), be far longer than needed for prior art and reality, only need to change interface setting simply and can meet needed for the starting of all types and specification motorcycle.And the material of the large friction factor of attaching or friction plate on outer shroud 30, free wheel device C6 also various type is the overrunning clutch friction plate of Motor Vehicle.

Shown in Figure 10 is apply the one-way element C7 in motor vehicle starter of the present invention.The outer circumferential face of the tubular matrix 76a extended towards one end of its friction member 70 is provided with the gear teeth 168, to engage the flywheel of motor, transmits the torque of actuating motor.The outer circumferential face of the tubular matrix 76b extended towards the other end of friction member 70 is provided with circumferential chute 218, drives its shift fork (not shown) moved axially to accommodate.For adapting to surmount rotation at a high speed, arc balancing component/balancing weight 170 is arranged in entrance 82 as described above.If needed, also can remove tubular matrix 76a, 76b, and on an exterior edge face of friction member 70, some projections are set to serve as planet pin, or some axial bores are set to accommodate planet pin, and then make one-way element C7 be modified to the one-way element that can be used for decelerating starter.Undoubtedly, analogy clutch C6 can determine, one-way element C7 possesses to be enough to meet from minicar until heavy truck is at interior all Motor Vehicle, and the torque capacity needed for starting of boats and ships, aircraft, generator set, industrial fan etc.

That Figure 11 provides is unilateral bearing C8.Wherein, the power transmission characteristic surface 34 in order to form keyway is set directly on the outer circumferential face of friction member 70.Bearing sealed ring 110 is arranged in the annular space of one group of ball 192 outer end.Rubber seal 100 is arranged between the radial direction of the outer circumferential face 48b of inner ring 40 and the inner peripheral surface 84b of friction member 70.Maximum radial spacing between outer circumferential face 48b and inner peripheral surface 84b, greatly at least allowing one group of ball 192 by the axial degree inserting its raceway of the other end.Further, seal ring 100 be fitted into position, must after one group of ball 192 all enters position.In parameter, when the external diameter of friction member 70 equals 35mm, the nominal torque of unilateral bearing C8 is at least not less than 129Nm (service factor is 3.0), is have at least 7 ~ 9 times to isodiametric CSK15 in prior art.

Shown in Figure 12 is the one-way belt sheave C9 going for motor generator input shaft end.For obtaining maximum transmission capacity with minimum radial dimension, the spatial-wedging friction overrunning clutch mechanism combined rigidly with outer shroud 30, is biased in same one end of axis of outer shroud 30 and two spring bearing 158.These two axially spaced-aparts for radial location outer shroud 30 and inner ring 40 have the bearing 158 of spacer ring 210, be arranged on two corresponding shaft shoulders of outer circumferential face 48b and inner peripheral surface 84b the inner respectively, and snap ring 184a and 184b be arranged in this corresponding peripheral groove in two side faces outer end limits completely.The outer circumferential face of outer shroud 30 is provided with the power transmission characteristic surface 34 limiting belt grooves 32.The inner peripheral surface of inner ring 40 is then provided with the thread section 42 for connecting generator input shaft, for the cylinder section of foundation 44 of locating, and the additional holes section 46 of such as hexagonal hole shape for mounting and dismounting.As arranging result, be 15mm at internal orifice dimension, when pulley outer diameter is not more than 48mm, the nominal torque of belt pulley C9 at least reaches 400Nm (service factor is 3.0), the level of torque (pulley outer diameter 51mm) of the prior art 90Nm of 4.4 times to 2010.

Shown in Figure 13 is the two axle assembly C10 applying loader speed changer of the present invention.It is formed on transmission shaft 200 with being provided with small gear 220 rigid unitary of gear teeth 168a.It is provided with the outer shroud 30 (because axial position relation can only make separately) of gear teeth 168b, use the dual Placement that is connected with key 202 of interference fit to be fixed on the outer circumferential face of friction member 70 simultaneously, and by bearing 158 be radially positioned in transmission shaft 200 towards on the axle journal of one end extension.Guiding element 50 is non-rotatably connected to by spline on the outer circumferential face of transmission shaft 200.Obviously, two axle assembly C10 simplify the structure of existing two axle assemblies exponentially and reduce fabricating cost, except two gears and an axle, are different from prior art completely.Further, its nominal torque, when the external diameter of friction member 70 be 175mm and service factor is 3.0, just at least reaches the level of 22,500Nm, breakdown torque possible when exceeding real work more exponentially.

As described in embodiment one, friction member 70 in two axle assembly C10 also can be formed by identical two semi circular shells radial abutment best, and the two outer shroud 30 be arranged on the two outer circumferential face by the dual mode be connected with key with interference connection best realizes interfixing.

Shown in Figure 14 is the application wheel hub of electric bicycle C11 with integrated flywheel of the present invention.Wherein, two ring-type bag shape friction member 70a and 70b of coaxial two operative orientations spatial-wedging friction overrunning clutch mechanism in the same way arranged, are combined into one according to the mode axial stiffness shown in Fig. 6, and are formed as a part with wheel hub shell 206.Wheel hub shell 206 is fixed on hub spindle 216 by bearing 158 radial direction, is provided with retarder pedestal 214 in it.The shaftgear 212 being coupled in motor output shaft is fixed with rotationally in retarder pedestal 214.Shaftgear 212 by the inner ring 40a of driving torque by engaging with it from motor, pass to the overrunning clutch mechanism inside wheel hub, and then drive hub shell 206 can rotate.Now, the overrunning clutch mechanism outside wheel hub is naturally in and surmounts state.And if need, the driving torque that drive hub shell 206 rotates also can from the overrunning clutch mechanism outside wheel hub, the pedalling force of the bicycler namely transmitted from the inner ring 40b of flywheel mechanism.Here, for ball 192 provides two of outer raceway to be arranged on ring support 204 on hub spindle 216 outer circumferential face, the corresponding shaft shoulder of hub spindle 216 the inner and other component axially locating, such as vehicle frame etc. of outer end are arranged on respectively.

Obviously, to wheel hub C11 modification a little, the Unidirectional output mechanism C12 of the middle drive unit of electric bicycle just can be obtained.As shown in figure 15, being combined into ring-type bag shape friction member 70a and 70b of a part rigidly, by being provided with the bearing 158b of seal ring best, being rotatably mounted on the endoporus side face of mid-gearbox casing 198 one end.Axis 230, by bearing 158a, 158c, is rotatably mounted on the endoporus side face of mid-gearbox casing 198 the other end, and on the inner peripheral surface of friction member 70b.Belong to guiding element 50a and 50b of two friction overrunning clutch mechanisms, be non-rotatably connected with inner ring 40 and axis 230 respectively by spline pair.Inner ring 40 to be arranged on rotationally on axis 230 outer circumferential face and to be coupled to unshowned motor.For transmitting crank 166a and 166b of bicycler's pedalling force, be fixedly attached to the two ends of axis 230 respectively.So, from the driving force of motor or bicycler, just can respectively by two spatial-wedging friction overrunning clutch mechanisms, relay-type ground drives outer shroud 30 also to transfer a driving force to driving wheel by unshowned chain.

Undoubtedly, the torque capacity of the 358Nm of simple analogy flywheel C4, can confirm that wheel hub C11 and Unidirectional output mechanism C12 has the transmission capacity needed for super reality far away.And the driving force of these two embodiments obviously can respectively from two mechanical power sources, such as, from motor and internal-combustion engine.

In addition, when pedalling force only from bicycler of the driving force of Unidirectional output mechanism C12, crank 166a and 166b can be arranged on best simultaneously scrunch the round half cycle being positioned at headstock direction, as long as arrange a reversing mechanism such as disclosed in patent documentation CN1621304A between two cranks, just can realize scrunching continuously the seesaw-type of two cranks.Like this, pedaling action and scrunch circle no longer there is the stop up and down that can cause in such as uphill condition failure of riding, and be all positioned near most high driving efficiency point.Not only meet most structoure of the human body, save bicycler's muscle power, and be easier to promote stepping frequency and be beneficial to quick acceleration.

Required it is emphasized that, as mentioned above, as ζ < λ≤ξ and λ > 0 time, the present invention can have the destruction-proof function that overload is skidded, and namely can be used as the unidirectional or bidirectional safe clutch without the need to the complete self adaption action of special setting overload torque value.About this detailed description on the one hand and diagram, the spatial-wedging friction coupling by name that can propose on the same day in the application see the applicant and the patent application of safety clutch, the application is not described further.

Below be only the present invention is directed to the description and diagram that its limited embodiments gives; there is particularity to a certain degree; but it should be understood that; mentioned embodiment and accompanying drawing all only for illustration of object; and be not used in restriction the present invention and protection domain thereof; to its various changes carried out, equivalent, exchange and the change of structure or each member position, all will be considered to the spirit and scope not being separated from the present invention's design.

Claims (15)

1. there is a bag space wedging type friction overrunning clutch provided for shape component, comprising:

Around one axis revolution and can axial engagement at least one traction friction mechanism, it has and to turn round around described axis and to be provided with the intermediate piece being at least roughly ring-type and the friction member of rubbing surface, the described rubbing surface of described intermediate piece and described friction member both sides axially forms at least one traction friction pair, to transmit friction torque between this two component with offseting; And

For described traction friction mechanism engaging force is provided and around described axis pivotal at least one rotate guide mechanism, it has and to turn round around described axis and to be provided with the guiding element being at least roughly ring-type of corresponding guide surface and described intermediate piece, and the described guide surface of described guiding element and described intermediate piece both sides axially forms guiding friction pair with offseting; It is characterized in that:

Also comprise at least one bag of shape component, connect in order to the closed conflict of axial force of setting up between described guiding element, described intermediate piece and described friction member, and be at least non-rotatably connected with one of them, it is provided with the inner peripheral surface around the pivotal at least roughly half cycle of described axis, and is positioned at the circumferential recess of the roughly half cycle on this inner peripheral surface and is communicated to the entrance of this circumferential recess by the outer circumferential face of described bag shape component; And

The lift angle λ at the mutual conflict position of described guiding friction pair, be greater than zero and be less than or equal to ξ, that is, 0 < λ≤ξ, wherein, ξ is the minimum value that can cause all described lift angle λ of not self-locking in described guiding friction pair and described traction friction pair circumference.

2. by free wheel device according to claim 1, it is characterized in that: comprise at least two around the pivotal friction mechanism of described axis, one of them is described traction friction mechanism, wherein another is the power transmission friction mechanism at least non-rotatably combined respectively with described guiding element and described friction member, or draws friction mechanism described in another.

3. by free wheel device according to claim 2, it is characterized in that: at least one in described traction friction mechanism and described power transmission friction mechanism, two corresponding rubbing surface is that half cone-apex angle is greater than 0 degree and be less than the frusto-conical surface of 180 degree.

4., by free wheel device according to claim 3, it is characterized in that: also comprise the elasticity pre-tightening mechanism at least with an elastic element, it is for setting up at least indirectly frictional connection between described intermediate piece and described friction member constantly.

5. by free wheel device according to claim 4, it is characterized in that: described lift angle λ is greater than ζ, namely, ζ < λ≤ξ, wherein, ζ is the minimum value of the described lift angle λ that can cause self-locking in described guiding friction pair circumference, and be also the maximum value of the described lift angle λ causing self-locking in described traction friction pair circumference, the implication of ξ is the same.

6., by free wheel device according to claim 4, it is characterized in that: as ζ >0, described lift angle λ is less than or equal to ζ, namely, 0< λ≤ζ, wherein, ζ is the minimum value of the described lift angle λ that can cause self-locking in described guiding friction pair circumference.

7. by the free wheel device described in any one of claim 1 ~ 6, it is characterized in that: described traction friction mechanism is many friction disk types friction mechanism, it is quantitatively all minimum is one and axial staggered two groups of friction plates, is non-rotatably connected to described friction member and described intermediate piece respectively.

8. by the free wheel device described in any one of claim 2 ~ 6, it is characterized in that: described power transmission friction mechanism is many friction disk types friction mechanism, it is quantitatively all minimum is one and axial staggered two groups of friction plates, is non-rotatably connected to described friction member and described guiding element respectively.

9. by the free wheel device described in any one of claim 1 ~ 6, it is characterized in that: it has multiple described traction friction mechanism and multiple described rotation guide mechanism, be arranged in the multiple described circumferential recess of the correspondence of multiple described bag shape component respectively accordingly, the plurality of described bag shape component arranges along described axis and is combined into one rigidly.

10., by the free wheel device described in any one of claim 1 ~ 6, it is characterized in that:

Be provided with described rotation guide mechanism mutually nested in two radial directions, two described guiding elements of this two mechanism and two described intermediate pieces, be positioned at the form on equidirectional end face with described guide surface, connect into rigid unitary respectively, and non-rotatably connect into circumference one;

The lift angle λ of described guiding friction pair respective in two described rotation guide mechanisms, is greater than zero respectively and is less than or equal to ζ, and be greater than ζ and be less than or equal to ξ;

Be provided with at least one elastic element, its extremely described lift angle λ that axially at least indirectly conflicts is greater than zero and is less than or equal to the described rotation guide mechanism of ζ.

11., by free wheel device described in any one of claim 1 ~ 6, is characterized in that: one in described bag shape component and described guiding element, described intermediate piece and described friction member is combined into single hard parts.

12. by the free wheel device described in any one of claim 1 ~ 6, it is characterized in that: on the outer circumferential face of described guiding element, one of described intermediate piece and described friction member, be provided with the arm of force extended to described entrance radial direction, to be non-rotatably connected with described bag shape component.

13. by the free wheel device described in any one of claim 1 ~ 6, and it is characterized in that: also comprise balancing component, it is arranged in described entrance, to balance the centrifugal inertia force of described free wheel device.

14., by the free wheel device described in any one of claim 1 ~ 6, is characterized in that: the closure member also comprising entrance described in shutoff in radial direction.

15., by the free wheel device described in any one of claim 1 ~ 6, is characterized in that: described bag shape component is provided with the characteristic surface for transmitting torque.