CN104791398A - Space wedging type overrun belt pulley, overrun decoupler, crankshaft damping overrun belt pulley and torsional damping overrun clutch - Google Patents
Space wedging type overrun belt pulley, overrun decoupler, crankshaft damping overrun belt pulley and torsional damping overrun clutch Download PDFInfo
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- CN104791398A CN104791398A CN201510073897.5A CN201510073897A CN104791398A CN 104791398 A CN104791398 A CN 104791398A CN 201510073897 A CN201510073897 A CN 201510073897A CN 104791398 A CN104791398 A CN 104791398A
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D41/00—Freewheels or freewheel clutches
- F16D41/06—Freewheels or freewheel clutches with intermediate wedging coupling members between an inner and an outer surface
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Abstract
The invention provides a space wedging type overrun belt pulley. The space wedging type overrun belt pulley comprises a guide ring, a medium ring, a friction ring and a belt ring or a jointing hub, wherein the belt ring or the jointing hub cannot be rotatably connected with the guide ring or the friction ring at least. The medium ring and the guide ring form a self-excitation type rotation guiding mechanism G through one-way spiral guide teeth. The friction ring and the medium ring form a rotation type traction friction mechanism F1, and the friction ring and the guide ring form a force transfer friction mechanism F2. The three mechanisms abut against one another axially to form an axial force closed system. When non-rotatable connection is changed to indirect connection through an elastic connecting part, the overrun belt pulley becomes an overrun decoupler or a damping overrun belt pulley capable of attenuating torsional vibration and jointing impact. Compared with the prior art, since the three friction mechanisms has the advantages of complete surface contact, automatic abrasion compensation and no discrete components, the space wedging type overrun belt pulley has the excellent advantages that working reliability is ideal and the service life will not end as long as the structure is not damaged.
Description
Related application
The application be by disclosed in Chinese patent literature CN101936346B and CN102562859A and the dependent patent application of four patent applications of the applicant described in Chinese patent application 201410555684.1 and 201420327367.X.The full content of the disclosure four patent applications is formerly incorporated herein by reference.
Technical field
The present invention relates in all transmission fields a kind of only can in one direction transmitting torque and be automatically separated in the opposite direction and dally surmount drive wheel, or title one-way transmission wheel, comprise can reduce or damping rotary oscillations and/or joint impact surmount drive wheel, free wheel device, particularly but not only relate to a kind of overrunning belt pulley including overrunning clutch mechanism for car combustion engine crankshaft front end train.
Background technique
The one-way transmission wheel used in prior art, such as, for the turbosupercharger overrunning belt pulley of car combustion engine crankshaft front end train, bent axle overrunning belt pulley, and, generator overrunning belt pulley (OverrunningAlternator Pulley, be called for short OAP) and/or surmount decoupler (Overrunning AlternatorDecoupler, be called for short OAD) etc., all there is the technological deficiency that such as torque capacity is too small, easy to wear and operating life is too short.And, they structurally, in making and fit on also seem comparatively complicated.In the application such as oil and agricultural machinery, existing unidirectional/operating life of overrunning belt pulley then seems more of short duration.
In addition, the free wheel device of prior art does not have the transmission capacity of effective reduction/damping rotary oscillations and joint impact substantially.
Summary of the invention
The present invention is devoted to the above-mentioned defect eliminating or at least alleviate prior art existence.
The technical problem to be solved in the present invention is to provide that a kind of torque capacity is higher, operating life is longer, the simpler spatial-wedging overrunning belt pulley of structure.
Another technical problem that the present invention will solve is to provide that a kind of torque capacity is higher, operating life is longer, structure is simpler and can reduce/and the spatial-wedging of damping rotary oscillations and joint impact surmounts decoupler.
The technical problem again that the present invention will solve is, provides that a kind of torque capacity is higher, operating life is longer, structure simpler spatial-wedging bent axle vibration damping overrunning belt pulley.
Last technical problem that the present invention will solve is, provides the spatial-wedging torsion damping free wheel device that a kind of torque capacity is higher, operating life is longer, structure more simply can reduce torsional oscillation.
For solving the problems of the technologies described above, the spatial-wedging overrunning belt pulley of the present invention comprises, around one axis revolution and can axial engagement at least one traction friction mechanism, it has and to turn round around above-mentioned axis and to be provided with traction intermediary's ring of rubbing surface and friction ring, the traction rubbing surface of both sides axially forms at least one traction friction pair, to transmit friction torque between this two ring 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 guide ring and the above-mentioned intermediary ring of corresponding guide surface, and the guide surface of both sides axially forms guiding friction pair with offseting; The power transmission friction mechanism at least non-rotatably combined respectively with guide ring and friction ring; And at least one is around the pivotal annular component of above-mentioned axis, this annular component is and guide ring or at least non-rotatable engagement hub that is connected of friction ring or strap lug; 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 described lift angle λ of not self-locking in guiding friction pair and traction friction pair circumference.
Alternatively, also be provided with at least one limiter element for closed axial force, it with at the most in guiding element and friction member, can connect into force-closed formula compostle member at least non-rotatable mode, connects in order to the closed conflict of axial force of setting up each other.
Preferably, annular component is connected with non-rotatable between guide ring or friction ring, is can axial relative movement but can not circumference can be dynamically connected in relative rotation.
Preferably, the combination that rubbing surface can be the multiple inner and/or outer frusto-conical surface turned round around above-mentioned axis by the bus in polyline shaped on cross section is drawn.
Preferably, 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 ring and intermediary's ring respectively.
For solving another technical problem above-mentioned, the spatial-wedging of the present invention surmounts decoupler, comprises above-mentioned overrunning belt pulley, but annular component wherein, be configured to non-rotatably indirectly be connected to guide ring or friction ring by least one Flexible Connector.
Alternatively, Flexible Connector can be helical spring, serpentine spring or linear springs etc.
For solving an above-mentioned technical problem again, the spatial-wedging bent axle vibration damping overrunning belt pulley of the present invention, comprise above-mentioned overrunning belt pulley, but annular component wherein, be configured to non-rotatably indirectly be connected to guide ring or friction ring by the channel rubber of at least one ring-type.
For solving last technical problem above-mentioned, the spatial-wedging torsion damping free wheel device of the present invention, comprise and above-mentioned surmount decoupler, but the belt tunnel slot type power transmission characteristic surface on its strap lug replace by the power transmission characteristic surface of such as interference fit face, the gear teeth, keyway, pin-and-hole or one group of screw hole and so on.
More improvement project of the present invention, is provided by embodiment part.
It should be noted that, the related notion in present specification or the implication of term 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 angle of climb of space wedge mechanism and extrude angle.Namely, in the rotation guiding operating mode of rotating guide mechanism G, namely guide ring 50 starts to have driving intermediary ring 90 constantly along in the trend of arrow P direction Relative friction ring 70 rotation in such as Fig. 2, can guarantee that the minimum lift angle λ at the conflict position, both sides surface of guiding friction pair self-locking is defined as ζ, ζ is also referred to as the angle of climb of intermediary's ring 90, maximum lift angle is then defined as ξ, and ξ extrudes angle also referred to as intermediary's ring 90.More detailed description, can see above overall four patent applications combined, such as, [0031] ~ [0035] section of the specification of patent documentation CN101936346B, and, the record of [0029] ~ [0032] section of the specification of patent application 201410555684.1, is not described further herein.
Hinge structure, according to spatial-wedging overrunning belt pulley of the present invention, surmount decoupler, bent axle vibration damping overrunning belt pulley and torsion damping free wheel device, not only structure is simple, wedging is reliable and have operating life and the durability of overlength, but also there is higher torque capacity and working speed, the easily advantage such as making and assembling.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 sectional view according to embodiments of the invention one.
Fig. 2 is the schematic local expansion figure of flank profil to same external cylindrical surface radially projecting of K-K section Shang Ge mechanism in Fig. 1.
Fig. 3 is the axial sectional view according to embodiments of the invention two.
Fig. 4 is the axial sectional view according to embodiments of the invention three.
Fig. 5 is the axial sectional view according to embodiments of the invention four.
Fig. 6 is the axial sectional view according to embodiments of the invention five.
Fig. 7 is the axial sectional view according to embodiments of the invention six.
Fig. 8 is the axial sectional view according to embodiments of the invention seven.
Fig. 9 is the axial sectional view according to embodiments of the invention eight.
Figure 10 is the axial sectional view according to embodiments of the invention nine.
Figure 11 is the axial sectional view according to embodiments of the invention ten.
Figure 12 is the axial sectional view according to embodiments of the invention 11.
Figure 13 is the axial sectional view according to embodiments of the invention 12.
Figure 14 is the schematic local expansion figure of flank profil to same external cylindrical surface radially projecting of K-K section Shang Ge mechanism in Figure 13.
Figure 15 is the axial sectional view according to embodiments of the invention 13.
Figure 16 is the schematic local expansion figure of flank profil to same external cylindrical surface radially projecting of K-K section Shang Ge mechanism in Figure 15.
Figure 17 is the axial sectional view according to embodiments of the invention 14.
Figure 18 is the schematic local expansion figure of flank profil to same periphery cylinder radially projecting of K-K section Shang Ge mechanism in Figure 17.
Figure 19 is the axial sectional view according to embodiments of the invention 15.
Figure 20 is the axial sectional view according to embodiments of the invention 16.
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.
See the embodiment shown in Fig. 1 ~ 2, the outer type spatial-wedging overrunning belt pulley P1 that is spirally connected of an inner ring guiding.Wherein, around the pivotal friction ring 70 of axis X by zigzag fashion outside thread tooth 79, coaxially screw on the complementary internal thread tooth of strap lug 30 inner peripheral surface by axial one end, the location end face 77 of its ring-type is conflicted to the step end face of this internal thread tooth the inner, thus with the flanged type ring-type limiter end 188 of step the inner, jointly limit radial open type annular recess in the fixing axial enclosed type of axial width.
Meanwhile, friction ring 70 also connects into an associative ring with the strap lug 30 being in fact used as limiter element 180.This associative ring, respectively by bearing 158a and 158b in its two ends endoporus, is radially positioned on corresponding outer circumferential face 48a and 48b at axis X pivotal engagement hub 40 two ends.Here, bearing 158a is a needle bearing best, in the annulus of two bearings 158 outer end, is also respectively arranged with Sealing 110a and 110b best.
In axial enclosed type annular recess, turn round and axially mutually chimeric guide ring 50 and intermediary's ring 90 around axis X, circumference by the preloading spring 150 being arranged at this two interannular acts on, axially conflict constantly respectively to limiter end 188 and friction ring 70, to be formed respectively around pivotal two the rotary type power transmission friction mechanism F2 of axis X and traction friction mechanism F1.Wherein, traction friction mechanism F1a and F1b respectively has one axially can not the truncated cone type traction friction pair of friction self-locking, truncated cone type rotary type traction rubbing surface 104a and 72a and 104b and 72b complementary separately on its two set constructor, is separately positioned on the axial opposing end surface of intermediary's ring 90 and friction ring 70.Power transmission friction mechanism F2 then has the power transmission friction pair of a plane, and the rotary type power transmission rubbing surface 58 and 74 of its textural complementation, is separately positioned on the axial opposing end surface of guide ring 50 and limiter end 188.By spline pair, guide ring 50 is non-rotatably socketed on the outer circumferential face of engagement hub 40.The inner peripheral surface of engagement hub 40 is followed successively by columniform section of foundation 44, the section of being threaded 42, and, for the lever piece 46 poroid in the not rounded such as spline-like or such as hexagon mounted and dismounted.
Should be pointed out that in passing, between power transmission rubbing surface 58 and 74 in FIG, also can an intermediary ring 90b be axially set symmetrically again, to form another at least roughly symmetrical rotation guide mechanism Gb respectively with guide ring 50 and limiter end 188 and to draw friction mechanism F1b.So, this modification overrunning belt pulley no longer will have power transmission friction mechanism F2, but there are two traction friction mechanism F1a and F1b of shared same combined friction ring simultaneously, the optimum pattern of its traction rubbing surface can also be Transverse plane, thus the designing requirement of space wedge mechanism to coaxality can be abandoned, and then significantly reduce preparation process.
Continue referring to Fig. 1 ~ 2, comprise guide ring 50 and intermediary's ring 90 around axis X pivotal rotation guide mechanism G, one group permanent chimeric indented spirals type guiding tooth 52 and 92, is arranged on the opposed facing annular end face of these two rings both sides respectively accordingly.Wherein, the lead guide surface 54 and 94 of tooth of both sides is one group of screw type flank of tooth with complementary structure best, to form the spiral guiding friction pair of one group of face contact, both sides' one group of circular gap is separately the non-guide face 56 and 96 of ε, and parallel to the axis X best.Be arranged in the expansion open annular preloading spring 150 of the elasticity pre-tightening mechanism in guiding tooth 52 and 92 radially inner side space, two termination just in time radial direction extends in this circular gap, flexibly to conflict to the form in non-guide face 56 and 96 respectively, cause in guide surface 54 and 94 circumference and conflict in opposite directions constantly, and then cause rotation guide mechanism G to be in rotation guiding operating mode all the time, and traction friction mechanism F1 and power transmission friction mechanism F2 is finally caused to be in fit-state all the time.
Usually, the lift angle of guide surface 54 and 94 is λ, and, 0 < λ≤ξ, distinguishingly, ζ < λ≤ξ or 0 < λ≤ζ (as ζ > 0).Axial freedom/the gap of rotating guide mechanism G is 6,6 >=0.In axis X plane, guide surface 54 and the angle between 94 and axis X are greater than 0 degree, are less than 180 degree.If needed, guide surface 54 and/or 94 also can be provided with best in order to heat radiation or the groove getting rid of liquid/gas.
As shown in Figure 2, outside thread tooth 79 is identical with 94 rotation directions with guide surface 54, and its lift angle should be less than best extrudes angle ξ.For improving the connection reliability of friction ring 70, also between itself and strap lug 30, axial or radial pin-and-hole formula embeding mechanism can be set, or, prevent the loosening well known organization that is threaded.
The working procedure of overrunning belt pulley P1 is very simple.When unshowned belt drives strap lug 30 and friction ring 70 together fast rotational, such as, start that there is initial instant constantly that make to drive the trend of rotating along arrow R direction in Fig. 2 relative to guide ring 50, friction ring 70 just by the traction friction torque of traction friction mechanism F1, cause intermediary's ring 90 to have synchronous axial system made by relative guide ring 50 trend along arrow R direction.And pass through the rotation leading role of guide surface 94 and 54, the axial tension force of the auto-excitation type that this rotation trend produces, by cause guiding tooth 92 wedging at once to surround at guide surface 54 and traction rubbing surface 72 wedge shape space in, thus guide ring 50 is become the entirety that rubs with friction ring 70 wedging, traction friction mechanism F1 thus axial engagement, simultaneously, this tension force also by guide ring 50 swelling at once on power transmission rubbing surface 74, to form the closed mode connected of conflicting of axial force, power transmission friction mechanism F2 is caused also synchronously to engage, and guide ring 50 and friction ring 70 are connected into the entirety that rubs indirectly.
So overrunning belt pulley P1 engages along with the wedging of space wedge mechanism.The driving torque M from not shown belt imported into by strap lug 30
0, be divided into via the wedging friction torque M rotating guide mechanism G, traction friction mechanism F1a and F1b transmits
1, and, the power transmission friction torque M directly transmitted via power transmission friction mechanism F2
2, pass to guide ring 50 respectively, then by the engagement hub 40 in its endoporus, pass to unshowned such as generator shaft.Wherein, M
0=M
1+ M
2.Obviously, the size of above-mentioned axial tension force, wedging power and each frictional force, is all proportional to M completely adaptively
1, namely M
0, and torque also by reverse path transmission, can can't produce any essential difference.
And when unshowned belt drive strap lug 30 and friction ring 70 start to rotate at a slow speed, such as, start that there is initial instant constantly that make to separate the trend that wedge rotates along arrow P direction in Fig. 2 relative to guide ring 50, namely drive the moment that rotation trend disappears, friction ring 70, just by the friction torque of traction friction mechanism F1, drives intermediary's ring 90 to do relative to guide ring 50 to remove the rotation of rotating the leading role of guide mechanism G.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 working and whole space wedge mechanism based on the axial autoexcitation tension force of this rotation guide mechanism G, will be separated immediately or separate wedge.So overrunning belt pulley P1 terminates to engage and starts to surmount rotation, that is, intermediary's ring 90 follow guide ring 50 start Relative friction ring 70 along R direction friction trackslip.
As above as described in overall four patent applications combined, as long as the space wedge mechanism meeting lift angle requirement can be maintained, associated components still can form the closed conflict of axial force and be connected, the structure of all components of the application and position, be all unrestricted and can change or replace, numerous modification can be had.
Such as, be not difficult to expect by basic mechanical insight, in radial direction, the structure of inside and outside overrunning belt pulley P1 shown in flipchart 1 and position relationship, just can obtain the overrunning belt pulley P2 shown in Fig. 3, and can not produce any essence difference.Certainly, for convenience of manufacturing and improving structural strength, the modification shown in Fig. 3 is the result of having exchanged traction friction mechanism F1 and power transmission friction mechanism F2 axial position, and it is secondary buttress thread form pair to be reduced to simpler V thread screw.The location end face 182 of the ring-type of the inner tubular matrix 186 of limiter element 180, directly conflicts on the interior edge face being positioned at inside traction rubbing surface 72a of friction ring 70, thus jointly limits the fixing axial enclosed type outer radial open type annular recess of axial width.
Equally, also the friction ring 70 in Fig. 1 can be merged into a part with strap lug 30, and limiter end 188 be modified to the independent component being connected to strap lug 30 inner peripheral surface by screw pair.Further, more can connect with this screw pair of replacement that is fixedly connected with of circular weld 200, thus obtain overrunning belt pulley P3 as shown in Figure 4.Wherein, the snap ring 190 on engagement hub 40 outer circumferential face is for the object of axial limiting.
Be understood that, limiter element 180 in Fig. 1 also can be independent from strap lug 30, and with the friction ring 70 of cup-shaped shell-type in a welding manner, form the independently associative ring that has radial open type annular recess in axial enclosed type, thus be modified to overrunning belt pulley P4 as shown in Figure 5.Wherein, for convenience of making, guide ring 50 and engagement hub 40 are merged into a part.Correspondingly, friction ring 70 is non-rotatably connected to the inner peripheral surface of strap lug 30 by such as spline pair, to obtain the axial displacement ability of response mechanical wear automatically.And preloading spring 150 can be specially such as one group of straight line shape wavy spring, be separately positioned between the right non-guide face of a composition 56 and 96.
As above as described in overall four patent applications combined, associative ring in Fig. 5 also various type is semicircle shell-type limiter element 160a and 160b of full symmetric in two radial directions, this two elements is connected to by interference the inner peripheral surface of strap lug 30, thus obtains overrunning belt pulley P5 as shown in Figure 6.Wherein, friction ring 70 by its internal side diameter exterior edge face linearly or uniform two or four the dental inlay teeth 86 of cross, be non-rotatably fitted together to in the teeth groove 166 of the correspondence of limiter element 160a and 160b inner peripheral surface.Semi-circular end face boss 162 and 164 in limiter element 160 outside diameter both ends of the surface, conflicts respectively to two bearings 158.
As above as described in overall four patent applications combined, the associative ring in Fig. 5 also various type is the ring-type bag shape shell-type limiter element 140 with the radial entrance allowing guide ring 50 to insert.This pocket-type limiter element 140/ bag of shape shell is connected to by interference the inner peripheral surface of strap lug 30, thus obtains overrunning belt pulley P6 as shown in Figure 7.Wherein, friction ring 70 extends to the adjutage 170 being provided with keyway 81 in described entrance by its radial direction, be non-rotatably connected with limiter element 140, or, by flat key, be non-rotatably directly connected with strap lug 30.More detailed description and diagram, can see above overall four the basic patent applications combined, no longer repeat specification herein.
Be understood that, except duplex traction friction mechanism F1, also by this mechanism F1 being arranged to the mode of many friction disk types mechanism, obtain the revolution friction pair of Transverse plane type, thus thoroughly abandoning the designing requirement of space wedge mechanism to coaxality.Such as, the overrunning belt pulley P7 shown in Fig. 8 is this kind of modification to overrunning belt pulley P1.Wherein, at least comprise the inner attrition piece 156 of one one group less, by radial protrusion in it, be non-rotatably fitted together to on the exterior edge face dental inlay tooth 100 of intermediary's ring 90 internal side diameter.The other one group of larger outside friction disc 154 be axially crisscross arranged with inner attrition piece 156, by engaging of the inner spline gear 36 of its external spline teeth and strap lug 30, forms non-rotatable connection with this ring.In design, the location end face 77 of ring-type is conflicted to the exterior edge face of inner spline gear 36, and the axial freedom of rotating guide mechanism G is still more than or equal to zero.Obviously, the traction rubbing surface 104 and 72 in Fig. 8 is in indirectly axial conflict state, and traction friction mechanism F1 has three traction friction pairs.
Similar with Fig. 2, the overrunning belt pulley P8 shown in Fig. 9 implements the modification result after radial upset to overrunning belt pulley P7.Wherein, inner spline gear 36 is modified to the dental inlay tooth 86 of friction ring 70, and dental inlay tooth 100 moves to the radial outside of intermediary's ring 90.
Comparison diagram 1 ~ 9 is not difficult to find, friction ring in the overrunning belt pulley P1 ~ P8 (comprising follow-up belt pulley P14 ~ P16) of its correspondence, in fact be all an axial force closed composition component including limiter element, that is the annular recess formula of bearing axial expansion power contains component, accordingly, rotation guide mechanism G wherein all has the autoexcitation force pattern of attempting axially expansion annular recess.And apparently, these technical characteristicss neither be required.Such as, Figure 10 ~ Figure 14 just shows relevant modification.Wherein, the overrunning belt pulley P9 shown in Figure 10, can regard the modification to the P3 of overrunning belt pulley shown in Fig. 4 as.
First, its rotation guide mechanism axially exchanged in Fig. 4 rotates the position of guide mechanism G and traction friction mechanism F1, and eliminates traction friction mechanism F1a.Like this, its guide ring 50 and friction ring 70 have just exchanged role, and what be merged into a part with strap lug 30 is guide ring, is no longer friction ring.Guide ring modification becomes the annular recess formula containing component of the broad sense with axial force closing function.
Secondly, correspondingly, rotate guide mechanism G and all have the autoexcitation force pattern of attempting axial shrinkage annular recess, friction ring starts the effect of bearing axially compressive force in opposite directions.
Again, screw type guiding tooth 52 and 92 is modified to single head or bull buttress thread form tooth, is separately positioned on guide ring 50 and the opposed facing inside and outside cylndrical surface of intermediary's ring 90 both sides, becomes side face tooth.
Finally, preloading spring 150 is specially torsion spring, and two termination is entrenched in the axial bore of intermediary's ring 90 exterior edge face respectively, and, in the radial hole of strap lug 30 inner peripheral surface.
It should be noted that the reason because drawing, the result of the whole figure that has been axial turning shown in Figure 10.
Obviously, overrunning belt pulley P9 has the more simple structure of relative overrunning belt pulley P1 ~ P8 and less axis and radial dimension, more simply makes and assembly technology, and, lower fabricating cost, and do not reduce work and the usability of previous embodiment.Such as, hinge structure, because lift angle λ permanent set is constant, there is higher wedging reliability, because face contact friction is completely secondary, there is higher torque capacity/weight bearing power, because of without discrete elements and frictional force electrically isolate from centrifugal force and there is higher working speed and lower non-load friction resistance, because wedging angle is almost forever constant and can auto-compensation wearing and tearing and have structure and do not damage the overlength operating life and durability that the life-span just not stops.
In addition, also can simplify overrunning belt pulley P9, thus obtain implementing the simplest technological scheme only having three necessary components of the present invention.Namely, its friction ring 70 is merged into a part with engagement hub 40, intermediary's ring 90 is modified to contraction elastic opening ring, makes the corresponding outer circumferential face 47 that inner circumferential surface can be conflicted to rubbing surface 72 and engagement hub 40 simultaneously, and limited axial position by the flange uniaxially at outer circumferential face 48b place.
Certainly, copy aforementioned variant, also can implement to overturn modification, to obtain overrunning belt pulley P10 as shown in figure 11 inside and outside in radial direction to figure shown in Figure 10.And copy example, its friction ring 70 is merged into a part with outer shroud 30, intermediary's ring 90 is modified to intumescent elastic opening ring, make the corresponding inner peripheral surface 35 that its outer circumferential face can be conflicted to rubbing surface 72 and strap lug 30 simultaneously, and being limited axial position by radial flange uniaxially in inner peripheral surface 35 axial outer end, overrunning belt pulley P10 just can be reduced to and implement the simplest technological scheme only having three necessary components of the present invention.
It must be noted that, based on structural particularity of the present invention, the present invention can also have torque shock ends when damping clutch engages, and, the variant embodiment of the torsional vibration of its undertaking self-torque upstream of decaying.Such as, institute of the present invention drawings attached acceptance of the bid is designated as the non-rotatable connection at S position, the elasticity be all modified to by Flexible Connector connects.So, just can obtain of the present inventionly can reducing/spatial-wedging the overrunning belt pulley of damping rotary oscillations and/or joint impact, surmount decoupler and free wheel device.
See Figure 12, shown in it is surmount decoupler (OAD) alleged by a prior art that can be used for automobile current generator.It is exactly to result of carrying out above-mentioned modification embodiment illustrated in fig. 11 that this spatial-wedging surmounts decoupler P11.Wherein, replace being and being specially helical spring Flexible Connector 120 of spline joint pair, an one termination 122 is entrenched in the axial counterbore 31 of the interior edge face of strap lug 30 one end inward flange, and its another termination is entrenched in the radial hole of friction ring 70 outer circumferential face.This spring can have the rotation direction identical or contrary with guide surface 54, and accordingly, itself and the inner peripheral surface of strap lug 30 or the outer circumferential face of friction ring 70 leave enough radial clearances, and like this, its elastomeric radial in response to institute's transmitting torque just can not be hindered.
Easily expect, Flexible Connector 120 in Figure 12 also can be specially the spring of the one group of straight line shape being quantitatively at least, such as, has spring thread that is square or circular cross-section, its one end is entrenched in axial counterbore 31, and the other end is entrenched in the axial groove 71 of friction ring 70 outer circumferential face.This modification is and surmounts decoupler P12 shown in Figure 13.Compare and surmount decoupler P11 and identical annular space, the one group of Flexible Connector 120 surmounting decoupler P12 is easy to have higher spring rate, therefore, it has and larger turns torque capacity/square transmission capacity, simultaneously, also because it is easy to have variable spring rate, thus also can have more outstanding decay torque shock ends or the ability of torsional oscillation concurrently.
Such as, see Figure 14, by the form being arranged to gradually realize that one group of Flexible Connector 120 and the circumference of corresponding axial groove 71 are conflicted.That is, Flexible Connector such as 120a ~ 120c is arranged to gap with corresponding axial groove such as 71a ~ 71c on the conflict direction pointed by R be separated by, it after the elastic deformation amount of Flexible Connector such as 120d ~ 120e reaches corresponding gap value, must start force and deformation just now gradually.
Be understood that, the effect of the Flexible Connector 120 of the application is similar to the elastic element in known elastic coupling flexible coupling.In fact, the specific constructive form of Flexible Connector 120 and Placement, can use for reference all technological schemes of known elastic coupling flexible coupling completely.
Such as, the Flexible Connector 120 surmounted in decoupler P13 shown in Figure 15 ~ 16, is just specially the serpentine spring of a ring-type.One group of return bend of the side of this spring is entrenched in one group of corresponding axial counterbore 31, and one group of return bend of its opposite side is then articulated on one group of radial protrusion 33 of the correspondence of strap lug 30 inner peripheral surface.One group of radial protrusion 73 of the correspondence of friction ring 70 outer circumferential face, respectively by between adjacent two radial protrusions 33, axis stretches between the circumferential interval of serpentine spring.In this modification, only circular gap/the degrees of freedom of radial protrusion such as between 73d and Flexible Connector 120 need be arranged to be greater than zero, Flexible Connector 120 is just easy to have variable spring rate.
For another example, Flexible Connector 120 is specially one group of screw type circumference stage clip, just can will surmounts decoupler P14 shown in the Figure 17 of being modified to ~ 18 embodiment illustrated in fig. 1.Wherein, the inner radial portions of circumferential stage clip is divided and is arranged in place in the circumferential recess 49 of engagement hub 40 outer circumferential face, and its outer radial part is then arranged on the through groove 64 of the axialmode being arranged in guide ring 50, and conflicts to four circumferential interior edge faces of described groove simultaneously.As mentioned above, by Flexible Connector 120 and through groove, the circular gap/degrees of freedom such as between 64c is arranged to be greater than zero, and it is easy to have variable spring rate equally.
Certainly, the circumferential recess 49 in Figure 17 also various type is axial groove, meanwhile, Flexible Connector 120 is specially elastic caoutchouc, and gained modification has the function of buffering and vibration damping equally.Certainly, also Flexible Connector 120 can be specially a channel rubber as the complete loop in Figure 19.Here, the bent axle vibration damping overrunning belt pulley P15 shown in Figure 19, can regard the simple variant of overrunning belt pulley P6 as.Wherein, for adapting to the increase of radial dimension, bearing 158 is nested in the endoporus of limiter element 140.One group of mounting hole 43 instead of the section of being threaded 42 in engagement hub 40.
Similarly, copy Figure 17, it is secondary that the Flexible Connector 120 in Figure 19 also can be used to replace its spline joint, and be specially the two groups of screw type circumference stage clips be set up in parallel, thus obtain bent axle vibration damping overrunning belt pulley P16 as shown in figure 20.Wherein, for reducing the magnitude of interference that adjutage 170 outer circumferential face coordinates with strap lug 30 inner peripheral surface, on the end face that this adjutage 170 is inconsistent with limiter element 140 both sides, be provided with at least one pair of axial bore, both sides are fixed into circumference one by the axial pin 210 be positioned at wherein.Here, adjutage 170 also has help and realizes dynamically balanced function, and to be full of whole described radial entrance space for the best.
In addition, bent axle vibration damping overrunning belt pulley P15 ~ P16, and all belt pulleys of the application, also can have knockdown belt grooves, reliably to transmit larger torque comparing in less radial and axial space.Dependency structure diagram and explanation, can see the applicant's open technological scheme that also be incorporated into this in full in Chinese patent literature CN102562860A and CN103527748A, and the application is repeat specification no longer.
Certainly, for surmounting decoupler P11 ~ P14 and bent axle vibration damping overrunning belt pulley P15 ~ P16, only the belt groove of the strap lug 30 in them need be modified to other power transmission characteristic surface of such as interference fit face, the gear teeth, keyway, pin-and-hole or one group of screw hole and so on, they can be modified to and can reduce or the free wheel device of damping rotary oscillations and/or joint impact.
Finally should be particularly noted that, due under identical material and physical dimension condition, torque capacity/the torque transfer capability of the spatial-wedging overrunning clutch mechanism of the application is at least several times as much as prior art, therefore, the torsional vibration eliminated or decay in car combustion engine crankshaft front end train and the best mode of impact, should be the bent axle vibration damping overrunning belt pulley such as P15 ~ the P16 only crank pulley in the source driven as train being replaced with the application, and without the need to loaded down with trivial details and redundantly using as being driven other belt pulley of target to be one by one arranged to overrunning belt pulley.The beneficial effect that this layout type compares prior art is, one is without the need to other is one by one arranged to overrunning belt pulley by drive pulley, thus the torsion damping reducing whole train is achieved with minimum cost, and eliminate internal-combustion engine sharply reduction of speed time braking that train the is produced object of impacting, two is that size without the need to increasing crank pulley just can meet torque request, three is because other belt pulleys all are again without the need to including overrunning clutch mechanism, thus the radial dimension of all belt pulleys in whole train can be reduced further, and reduce the total quality of train further, final order more to become miniaturization and lightweight to whole train.
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; and be not used in restriction the present invention and protection domain thereof; the various changes that they are carried out, equivalent, exchange and the change of member position or structure, all will be considered to the spirit and scope not being separated from the present invention's design.
Claims (10)
1. a spatial-wedging overrunning belt pulley, 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 traction intermediary's ring of rubbing surface and friction ring, the described traction rubbing surface of both sides axially forms at least one traction friction pair, to transmit friction torque between this two ring with offseting;
For described traction friction mechanism provides engaging force and around the pivotal rotation guide mechanism of described axis, it has and to turn round around described axis and to be provided with guide ring and the described intermediary ring of corresponding guide surface, and the described guide surface of both sides axially forms guiding friction pair with offseting; And
The power transmission friction mechanism at least non-rotatably combined respectively with described guide ring and described friction ring;
Wherein, the lift angle λ at the mutual conflict position of described guiding friction pair, is greater than zero and is less than or equal to ζ, namely, 0 < λ≤ζ, ζ are 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;
It is characterized in that:
Also comprise at least one around the pivotal annular component of described axis, this annular component is and described guide ring or at least non-rotatable engagement hub that is connected of described friction ring or strap lug.
2., by overrunning belt pulley according to claim 1, it is characterized in that: also comprise the elasticity pre-tightening mechanism with at least one elastic element, it is for setting up at least indirectly frictional connection between described intermediary ring and described friction ring constantly.
3. by overrunning belt pulley according to claim 1, 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 ring and described intermediary ring respectively.
4. by overrunning belt pulley according to claim 1, it is characterized in that: the described guide surface of described guide ring and described intermediary ring both sides is screw type flank of tooth, what it was arranged on both sides comprises on a surface of end face, inner peripheral surface and outer circumferential face; In axial plane, the angle between this screw type flank of tooth and described axis is greater than 0 degree, is less than 180 degree.
5., by overrunning belt pulley according to claim 4, it is characterized in that: the described screw type flank of tooth be separately positioned on both described guide ring and described intermediary ring mutually directly faced by inner peripheral surface and outer circumferential face on, described guide ring is provided with flanged type limiter end.
6. by overrunning belt pulley according to claim 1, it is characterized in that: described annular component is connected with described non-rotatable between described guide ring or described friction ring, is connect into being rigidly connected of being fixed as one.
7., by overrunning belt pulley according to claim 6, it is characterized in that: described in be rigidly connected be that the one being merged into a part connects.
8. spatial-wedging surmounts a decoupler, it is characterized in that: by the described annular component in overrunning belt pulley according to claim 1, is non-rotatably indirectly connected to described guide ring or described friction ring by least one Flexible Connector.
9. a spatial-wedging bent axle vibration damping overrunning belt pulley, it is characterized in that: by the described annular component in overrunning belt pulley according to claim 1, be non-rotatably indirectly connected to described guide ring or described friction ring by the channel rubber of at least one ring-type.
10. a spatial-wedging torsion damping free wheel device, it is characterized in that: surmount decoupler by according to claim 8, the belt tunnel slot type power transmission characteristic surface on strap lug described in it by interference fit face, the gear teeth, keyway, pin-and-hole or one group of screw hole replace.
Priority Applications (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510073897.5A CN104791398A (en) | 2015-02-04 | 2015-02-04 | Space wedging type overrun belt pulley, overrun decoupler, crankshaft damping overrun belt pulley and torsional damping overrun clutch |
| CN201610089359.XA CN105587797B (en) | 2015-02-04 | 2016-02-04 | Space wedging type overrunning belt pulley capable of reducing torsional vibration and overrunning clutch |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510073897.5A CN104791398A (en) | 2015-02-04 | 2015-02-04 | Space wedging type overrun belt pulley, overrun decoupler, crankshaft damping overrun belt pulley and torsional damping overrun clutch |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN104791398A true CN104791398A (en) | 2015-07-22 |
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Family Applications (2)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201510073897.5A Pending CN104791398A (en) | 2015-02-04 | 2015-02-04 | Space wedging type overrun belt pulley, overrun decoupler, crankshaft damping overrun belt pulley and torsional damping overrun clutch |
| CN201610089359.XA Active CN105587797B (en) | 2015-02-04 | 2016-02-04 | Space wedging type overrunning belt pulley capable of reducing torsional vibration and overrunning clutch |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201610089359.XA Active CN105587797B (en) | 2015-02-04 | 2016-02-04 | Space wedging type overrunning belt pulley capable of reducing torsional vibration and overrunning clutch |
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109075501A (en) * | 2016-04-15 | 2018-12-21 | 宝马股份公司 | In particular for vehicle, first structure element and the second structural detail connection component and in particular for the connection equipment of vehicle |
| CN111425581A (en) * | 2019-01-09 | 2020-07-17 | 舍弗勒技术股份两合公司 | Belt pulley decoupler |
Family Cites Families (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP3383740B2 (en) * | 1996-07-16 | 2003-03-04 | エヌ・オー・ケー・ビブラコースティック株式会社 | damper |
| JP2003014003A (en) * | 2001-07-03 | 2003-01-15 | Asmo Co Ltd | Clutch mechanism, actuator and door engine |
| CN2489997Y (en) * | 2001-07-11 | 2002-05-08 | 株洲庆云电力机车配件工厂 | Coupler for oleo-gear of electric locomotive |
| US7891475B2 (en) * | 2007-10-25 | 2011-02-22 | The Gates Corporation | Isolator decoupler |
| CN201747821U (en) * | 2010-04-20 | 2011-02-16 | 洪涛 | Space wedge-type friction overrunning clutch |
| CN201872944U (en) * | 2010-11-26 | 2011-06-22 | 中国船舶重工集团公司第七一九研究所 | Automatic centering device for ship stern bearing |
| CN102619902B (en) * | 2010-12-30 | 2016-06-01 | 洪涛 | Spatial wedge type double-clutch |
| CN102758859B (en) * | 2012-07-27 | 2015-09-09 | 重庆大易用机械有限公司 | Friction overdrive clutch |
-
2015
- 2015-02-04 CN CN201510073897.5A patent/CN104791398A/en active Pending
-
2016
- 2016-02-04 CN CN201610089359.XA patent/CN105587797B/en active Active
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109075501A (en) * | 2016-04-15 | 2018-12-21 | 宝马股份公司 | In particular for vehicle, first structure element and the second structural detail connection component and in particular for the connection equipment of vehicle |
| CN109075501B (en) * | 2016-04-15 | 2021-10-19 | 宝马股份公司 | Connecting assembly and connecting device for a first and a second structural element |
| CN111425581A (en) * | 2019-01-09 | 2020-07-17 | 舍弗勒技术股份两合公司 | Belt pulley decoupler |
Also Published As
| Publication number | Publication date |
|---|---|
| CN105587797A (en) | 2016-05-18 |
| CN105587797B (en) | 2020-11-20 |
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Application publication date: 20150722 |