CN105587797A - Spatial wedge-typed overrunning pulley capable of reducing torsional vibration and overrunning clutch - Google Patents
Spatial wedge-typed overrunning pulley capable of reducing torsional vibration and overrunning clutch Download PDFInfo
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- CN105587797A CN105587797A CN201610089359.XA CN201610089359A CN105587797A CN 105587797 A CN105587797 A CN 105587797A CN 201610089359 A CN201610089359 A CN 201610089359A CN 105587797 A CN105587797 A CN 105587797A
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Classifications
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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 discloses a spatial wedge-typed overrunning pulley capable of reducing torsional vibration and an overrunning clutch. The spatial wedge-typed overrunning pulley comprises a guide ring, a medium ring, a friction ring and a belt ring or an engagement hub, wherein the belt ring or the engagement hub is indirectly and irrotationally connected with the guide ring or the friction ring through an elastic connecting piece. The medium ring and the guide ring form a self-excited rotary guide mechanism G through one-way spiral guide teeth, the friction ring and the medium ring form a rotary traction friction mechanism F1, and the friction ring and the guide ring form a force transfer friction mechanism F2. The three mechanisms form an axial force closed system in an axial supporting way. Compared with the prior art, the spatial wedge-typed overrunning pulley has various excellent characters such as ideal working reliability and no life termination if no structure damage because all the three friction mechanisms have the characteristics of complete surface contact, automatic abrasion compensation and no discrete members.
Description
Related application
The application be by patent documentation CN101936346B, CN102562859A, CN104565122A andThe dependent patent application of four patent applications of the disclosed the applicant of CN104963963A, and, the application require byThe priority of the disclosed the applicant's of patent documentation CN104791398A formerly patent application. The disclosure formerly five speciallyThe full content of profit application is incorporated herein by reference.
Technical field
The one the present invention relates in all transmission fields only can be transmitted and turn in one direction by endless flexible elementSquare/rotatablely moving, and automatically separate in the opposite direction and idle running, and can reduction or damping rotary oscillations and/or joint punchingThat hits surmounts class transmission device, the invention still further relates to freewheel clutch, particularly but not only relate to a kind of in automobileThe overrunning belt pulley that includes overrunning clutch mechanism of combustion machine crankshaft front end wheel train.
Background technology
The one-way transmission wheel using in prior art, for example, for the turbocharging of car combustion engine crankshaft front end trainDevice overrunning belt pulley, bent axle overrunning belt pulley, and, generator overrunning belt pulley (OverrunningAlternatorPulley, is called for short OAP, or GeneratorOverrunningPulley, is called for short GOP) and/or surmount decoupler(OverrunningAlternatorDecoupler is called for short OAD) etc., all exist such as torque capacity and/or transmission capacityThe technological deficiency that too small, easy to wear and working life is too short etc. And, they structurally, in making and fit on also seemComparatively complicated. And in the comparatively strong application of the torque shock ends such as oil and agricultural machinery, for example, oil pumper and corn, wheat,In the transmission system of rice harves/cutting mill etc., existing unidirectional/working life of overrunning belt pulley seems more of short duration.
In addition, the freewheel clutch of prior art does not have effective reduction/damping rotary oscillations and joint impact substantiallyTransmission capacity.
Summary of the invention
The present invention is devoted to eliminate or at least alleviate the above-mentioned defect that prior art exists.
The technical problem to be solved in the present invention is to provide that a kind of torque capacity is higher, working life is longer, structure is simpler,And the spatial-wedging overrunning belt pulley of can reduce/damping rotary oscillations and joint impact.
Another technical problem that the present invention will solve is, provide that a kind of torque capacity is higher, working life is longer, structure moreSimply can reduce the spatial-wedging freewheel clutch of torsional oscillation.
For solving the problems of the technologies described above, the present invention's the spatial-wedging overrunning belt pulley that can reduce torsional oscillation comprises, around oneAxis revolution and at least one traction friction mechanism that can axial engagement, it has around above-mentioned axis and turns round and be provided with tractionThe intermediary ring of rubbing surface and drag ring, both sides' traction rubbing surface axially forms at least one traction friction pair with offseting, withBetween this two ring, transmit friction torque; For this traction friction mechanism provide engaging force and around above-mentioned axis rotating at least one turnAction-oriented mechanism, it has the guide ring and the above-mentioned intermediary ring that turn round and be provided with corresponding spigot surface around above-mentioned axis, both sidesSpigot surface axially form guiding friction pair with offseting; At least non-rotatably combine respectively with guide ring and drag ringPower transmission friction mechanism; At least non-rotatably be connected with guide ring or drag ring and outer peripheral face on be provided with belt tunnel slot type passThe strap lug of power characteristic surface; And at least one is around the rotating annular component of above-mentioned axis, this annular component is by least oneIndividual Flexible Connector is non-rotatably connected to guide ring or drag ring; Wherein, the liter at the mutual conflict position of guiding friction pairAngle λ, is greater than zero and be less than or equal to ξ, that is, 0 < λ≤ξ, ξ can cause guiding friction pair and traction friction pair week upwards all notThe small end endpoint value in the value open interval of the described lift angle λ of self-locking.
Alternatively, annular component is served as by engage hub or strap lug.
Preferably, non-rotatable being connected between annular component and guide ring or drag ring, be can axially relatively move butCan not circumferentially can be dynamically connected in relative rotation.
Preferably, traction rubbing surface can be formed around above-mentioned axis revolution by the bus that is polyline shaped on cross section manyThe combination of individual inner and/or outer frusto-conical surface.
Preferably, traction friction mechanism can be many friction disk types friction mechanism, and it is quantitatively all minimum is one and axleTo staggered two groups of friction plates, be non-rotatably connected to respectively drag ring and intermediary's ring.
Preferably, traction is separated be made up of a powder metallurgy and circumferential independent friction plate freely between friction pair, orPerson, at least one the traction rubbing surface in traction friction pair is attached with powder metallurgy boundary-layer.
Alternatively, also comprise the elasticity pre-tightening mechanism with at least one flexible member, it is for setting up constantly intermediaryAt least indirectly frictional connection between ring and drag ring.
Alternatively, in strap lug and guide ring, drag ring and limiter element one, is non-rotatably connected or mergesBecome a part.
For solving above-mentioned another technical problem, the present invention's the spatial-wedging freewheel clutch that can reduce torsional oscillation, comprisesThe above-mentioned decoupler that surmounts, but belt tunnel slot type power transmission characteristic surface on its strap lug is by such as interference fit face, the gear teeth, keyThe power transmission characteristic surface of groove, pin-and-hole, screw thread or one group of screw hole and so on replaces.
More improvement project of the present invention, is provided by detailed description of the invention part.
It should be noted that, the related notion in present specification or the implication of term are as follows:
Rotate guiding mechanism: circumference is relatively rotated to be converted at least comprise and axially relatively moving or the guiding of mobile trendMechanism. For example, the slides/rolls formula spiral of lead angle strict conformance and not strict conformance or part screw mechanism, radial pegGroove mechanism, end face wedge mechanism, end face embeding mechanism, end ratchet mechanism, and, cylinder/edge cam mechanism.
Space wedge mechanism: by rotating guiding mechanism and drawing the composite structure that friction mechanism forms.
ζ and ξ: the angle of climb of space wedge mechanism and extrude angle. That is, in the rotation guiding operating mode of rotating guiding mechanism G,Namely guide ring 50 starts to have constantly and drives intermediary ring 90 along the relative drag ring 70 of arrow P direction in Fig. 2 for exampleIn the trend of rotating, the minimum lift angle λ at the conflict position, both sides surface of the friction pair self-locking of can guaranteeing to lead is defined as ζ, and ζ alsoThe angle of climb that is called intermediary's ring 90, maximum lift angle is defined as ξ, and ξ is also referred to as the angle of extruding of intermediary's ring 90. In more detailBright, can referring to above front four patent applications of overall combination, for example, in the description of patent documentation CN101936346B[0031]～[0035] section, and, the note of [0029]～[0032] section in the description of patent application 201410555684.1Carry, be not described further herein.
Prior art relatively, according to spatial-wedging overrunning belt pulley and the overdrive clutch that reduces torsional oscillation of the present inventionDevice, not only simple in structure, wedging is reliable and have working life and the durability of overlength, but also has higher torque capacityAnd working speed, easily make and the advantage such as assembling. By explanation and the accompanying drawing of following embodiment, objects and advantages of the present inventionTo seem more clear and clear.
Brief description of the drawings
Fig. 1 is the axial cutaway view according to embodiments of the invention one.
Fig. 2 is that the relative profile of K-K section Shang Ge mechanism in Fig. 1 is to the schematic part of same external cylindrical surface radially projectingExpanded view.
Fig. 3 is the axial cutaway view according to embodiments of the invention two.
Fig. 4 is the axial cutaway view according to embodiments of the invention three.
Fig. 5 is the axial cutaway view according to embodiments of the invention four.
Fig. 6 is the axial cutaway view according to embodiments of the invention five.
Fig. 7 is the axial cutaway view according to embodiments of the invention six.
Fig. 8 is the axial cutaway view according to embodiments of the invention seven.
Fig. 9 is the axial cutaway view according to embodiments of the invention eight.
Figure 10 is the axial cutaway view according to embodiments of the invention nine.
Figure 11 is the axial cutaway view according to embodiments of the invention ten.
Figure 12 is the axial cutaway view according to embodiments of the invention 11.
Figure 13 is the axial cutaway view according to embodiments of the invention 12.
Figure 14 is the axial cutaway view according to embodiments of the invention 13.
Figure 15 is that the relative profile of K-K section Shang Ge mechanism in Figure 15 is to the schematic office of same external cylindrical surface radially projectingPortion's expanded view.
Figure 16 is the axial cutaway view according to embodiments of the invention 14.
Figure 17 is that the relative profile of K-K section Shang Ge mechanism in Figure 16 is to the schematic office of same external cylindrical surface radially projectingPortion's expanded view.
Figure 18 is the axial cutaway view according to embodiments of the invention 15.
Figure 19 is that the relative profile of K-K section Shang Ge mechanism in Figure 18 is to the schematic office of same external cylindrical surface radially projectingPortion's expanded view.
Figure 20 is the axial cutaway view according to embodiments of the invention 16.
Figure 21 is the axial cutaway view according to embodiments of the invention 17.
Detailed description of the invention
Necessary explanation: for short and sweet, in the text of this description and institute's drawings attached, same or analogous member and featurePosition all adopts identical Reference numeral, and only in the time that they occur for the first time or have modification, gives necessary explanation. Equally, alsoThe working mechanism of the same or similar mechanism of not repeat specification or process. For difference is arranged on identical on symmetry or correspondence positionMember or characteristic portion, this description has added letter after its Reference numeral, and during in general reference explanation or without difference,Not additional any letter.
Referring to the embodiment shown in Fig. 1～2, the outer type spatial-wedging overrunning belt pulley P1 that is spirally connected of ring guiding in.Wherein, around the rotating drag ring 70 of axis X by zigzag external screw thread tooth 79, by axial one end coaxial line screw to strap lugOn the complementary internal thread tooth of 30 inner peripheral surfaces, the location end face 77 of its ring-type is conflicted to the circular step shape of this internal thread tooth the innerLocation end face 182, thus with the flanged type ring-type limiter end 188 of step the inner, jointly limit by single bus around axis XOpen type annular recess radially in the axial enclosed type that forms of revolution.
Meanwhile, drag ring 70 also connects into an associative ring with the strap lug 30 that is in fact used as limiter element 180. This groupCyclization, respectively by bearing 158a and 158b in its two ends endoporus, is radially positioned in around the rotating engage hub of axis X 40 two endsCorresponding outer peripheral face 48a and 48b on. Here, bearing 158a is a needle bearing best, and is specially the bearing of deep-groove ballThe Internal and external cycle of 158b, is connected on each self-corresponding inside and outside circle side face in the mode of interference fit best. Outside two bearings 158In the annulus of end, be also respectively arranged with best seal 110a and 110b.
In axial enclosed type annular recess, around axis X revolution and axial upper chimeric guide ring 50 and intermediary's ring mutually90, be arranged at the circumferential effect of the preloading spring 150 of this two interannular, conflict constantly respectively to limiter end 188 on axiallyWith drag ring 70, to form respectively around rotating two the rotary type power transmission friction mechanism F2 of axis X and traction friction mechanism F1. ItsIn, traction friction mechanism F1a and F1b respectively have one can friction self-locking on axially truncated cone type traction friction pair, its two groupsTruncated cone type swinging traction rubbing surface 104a and 72a and 104b and the 72b of textural complementation separately, be separately positioned on intermediary's ring90 and the axial opposing end surface of drag ring 70 on. Power transmission friction mechanism F2 has the power transmission friction pair of a plane, itsThe swinging power transmission rubbing surface 58 and 74 of textural complementation, is separately positioned on the axial relative of guide ring 50 and limiter end 188On end face. By spline pair, guide ring 50 is non-rotatably socketed on the outer peripheral face of the annular component that is specially engage hub 40.On the inner peripheral surface of engage hub 40, be followed successively by columniform section of foundation 44, the section of being threaded 42, and, for being of mounting and dismountingThe lever piece 46 of the non-circular hole shapes such as spline-like or such as hexagon.
Wherein, the torque shock ends while joint for thering is damping clutch, and decaying, it accepts the torsion of self-torque upstreamThe variant embodiment of vibration, obtains the technique effect of similar so-called OAD, also can be as described in detail below, by Fig. 1Be labeled as the non-rotatable connection at S position, be modified to or replace with the elasticity connection by Flexible Connector 120.
Should be pointed out that in passing, between the power transmission rubbing surface 58 and 74 in Fig. 1, also can axially arrange symmetrically one againThe ring 90b of intermediary, to form respectively another at least roughly rotation guiding mechanism Gb of symmetry with guide ring 50 and limiter end 188With traction friction mechanism F1b. So this modification overrunning belt pulley will no longer have power transmission friction mechanism F2, but have simultaneouslyShare traction friction mechanism F1a and the F1b of two amphistylies of same combined friction ring. When the time comes, its all traction frictionFace also can be modified to transverse plane best, thereby can thoroughly abandon the designing requirement of space wedge mechanism to axiality, and thenSignificantly simplify manufacture craft.
Continue referring to Fig. 1～2, comprise guide ring 50 and intermediary's ring 90, one around the rotating rotation guiding mechanism of axis X GOrganize permanent chimeric zigzag screw type guiding tooth 52 and 92, be arranged on accordingly respectively the opposed facing annular of these two ring both sidesOn end face. Wherein, the lead spigot surface 54 and 94 of tooth of both sides is one group of screw type flank of tooth with complementary structure best, withForm the spiral guiding friction pair of one group of face contact, and the non-spigot surface 56 and 96 that both sides' one group of circular gap is separately ε,X best parallels to the axis. Be arranged in the expansion type opening of the elasticity pre-tightening mechanism in guiding tooth 52 and 92 radially inner side spacesRing-type preloading spring 150, two termination just in time radially extends in this circular gap, flexibly circumferentially to conflict to non-respectivelyThe form of spigot surface 56 and 96, causes spigot surface upwards to conflict in opposite directions constantly, and then cause for 54 and 94 weeks and rotates guiding mechanism GAll the time in rotating guiding operating mode, and finally cause traction friction mechanism F1 and power transmission friction mechanism F2 all the time in laminating shapeState.
Usually, the lift angle of spigot 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 guiding mechanism G is δ, δ >=0. In axis X plane, spigot surface 54 and 94 andAngle between axis X is greater than 0 degree, is less than 180 degree. If need, spigot surface 54 and/or 94 also can be provided with best in order toThe groove of heat radiation or eliminating liquid/gas.
As shown in Figure 2, external screw thread tooth 79 is identical with spigot surface 54 and 94 rotation directions, and its lift angle should be less than best extrudes angle ξ.For improving the connection reliability of drag ring 70, also can be between itself and strap lug 30, the pin-and-hole formula axially or radially of arranging is chimericMechanism, or, prevent be threaded loosening well known organization or structure.
The course of work of overrunning belt pulley P1 is very simple. When unshowned belt by with belt tunnel slot type power transmission featureThe friction-driven strap lug 30 of curved surface and together fast rotational of drag ring 70, for example, start to have constantly along arrow R in Fig. 2Direction makes to drive the initial instant of the trend of rotating relative to guide ring 50, drag ring 70 is just by traction friction mechanism F1'sTraction friction torque, causes intermediary's ring 90 to have relative to guide ring 50 and makes synchronous trend of rotating along arrow R direction. And lead toCross the rotation guide effect of spigot surface 94 and 54, the axial tension force of auto-excitation type that this rotation trend produces, will cause guiding toothIn the wedge shape space that 92 wedgings at once surround at spigot surface 54 and traction rubbing surface 72, thereby by guide ring 50 and drag ring 70Wedging becomes a friction entirety, traction friction mechanism F1 thereby axial engagement, and meanwhile, this tension force is also at once swollen by guide ring 50Tightly, on power transmission rubbing surface 74, the mode connecting to form the closed conflict of axial force, causes power transmission friction mechanism F2 also synchronousEngage, and guide ring 50 and drag ring 70 are connected into a friction entirety indirectly.
So overrunning belt pulley P1 engages along with the wedging of space wedge mechanism. Imported into by strap lug 30 from notThe driving torque M of belt is shown0, be divided into the wedging friction of transmitting via rotating guiding mechanism G, traction friction mechanism F1a and F1bTorque M1, and, the power transmission friction torque M directly transmitting via power transmission friction mechanism F22, pass to respectively guide ring 50, relendHelp non-rotatable connection or elasticity to connect, be passed to the engage hub 40 in its endoporus, and finally pass to for example unshownedGenerator shaft. Wherein, M0＝M1+M2. Obviously, the size of above-mentioned axial tension force, wedging power and each frictional force, all completely adaptiveAnswer and be proportional to M1, namely M0, and torque also can be transmitted by path contrary to the above, can't produce any essence poorNot.
And when unshowned belt is by forcing strap lug 30 and friction with the friction of belt tunnel slot type power transmission characteristic surfaceRing 70 starts rotation at a slow speed, for example, starts to have constantly and makes to separate wedges along the relative guide ring of arrow P direction in Fig. 2 50 and turnThe initial instant of moving trend, the moment that namely drives rotation trend to disappear, drag ring 70 is just by traction friction mechanism F1Friction torque, drawing intermediary ring 90 relatively guide ring 50 do releasings and rotate the rotation of the guide effect of guiding mechanism G. CauseThis, the rotation guide effect of the normal pressure between spigot surface 54 and 94 and rotation guiding mechanism G, just along with two spigot surfaces produceMutually disengage disappearing in a flash and simultaneously of trend. Nature, based on the axial autoexcitation tension force of this rotation guiding mechanism GAnd two friction mechanism F1 of work and F2 and whole space wedge mechanism will separate or separate wedge immediately. So, surmount beltWheel P1 finishes to engage and starts to surmount rotation, that is intermediary encircles 90 and follows guide ring 50 and start relative drag ring 70 and rub along R directionWiping is trackslipped.
As described in front four patent applications of overall combination above, as long as can maintain the space wedge that meets lift angle requirementShape mechanism, associated components still can form the closed conflict of axial force and be connected, and the structure of all members of the application and position, be allUnrestricted and can change or replace, can there are numerous modification.
For example, be not difficult to expect by basic mechanical general knowledge, footpath is the knot of the overrunning belt pulley P1 shown in inside and outside flipchart 1 upwardsStructure and position relationship, just can obtain the overrunning belt pulley P2 shown in Fig. 3, and can not produce any essence difference. Certainly, for convenienceManufacture and improve structural strength, the modification shown in Fig. 3 is to have exchanged traction friction mechanism F1 and power transmission friction mechanism F2 is axialThe result of position, and saw-tooth thread pair is reduced to simpler triangle thread pair. Manage the inner that is positioned at of limiter element 180The location end face 182 of the ring-type of shape matrix 186 front ends, directly conflicting is positioned at traction rubbing surface 72a inner side to drag ring 70On inner face 77, turned round thereby jointly limit the axial enclosed type outer radial open type ring forming around axis X by single busShape groove. By spline pair, the annular component that is specially strap lug 30 is non-rotatably connected to guide ring in mode at least50。
Equally, also the drag ring in Fig. 1 70 and strap lug 30 can be merged into a part at the most, and by limiter endPortion 188 is modified to the individual member that is connected to strap lug 30 inner peripheral surfaces by screw thread pair. Further, more can use circular weld200 be fixedly connected with replaces this screw thread pair connection, thereby obtains overrunning belt pulley P3 as shown in Figure 4. Wherein, outside engage hub 40Snap ring 190 on side face is axial location members.
Be understood that, the limiter element 180 that is merged at the most a part with strap lug 30 in Fig. 1 also can independently go outCome, and with the drag ring 70 of the cup-shaped shell-type mode with welding, form one and there is in axial enclosed type radially open type ring-typeThe independently associative ring of groove, thus be modified to overrunning belt pulley P4 as shown in Figure 5. Wherein, for convenience of making, guide ring 50Be merged into a part with engage hub 40. Correspondingly, drag ring 70 is non-rotatably connected to strap lug by for example spline pair30 inner peripheral surface, to obtain the axial displacement ability of automatic response mechanical wear. And preloading spring 150 can be specially for example one groupThe wavy spring of being made up of wire rod or sheet material, is separately positioned between the opposed facing non-spigot surface 56 and 96 of each group.
As described in front four patent applications of overall combination above, the associative ring in Fig. 5 also changeable type be two footpaths upwardsSemicircle shell-type limiter element 160a and the 160b of full symmetric, this two elements is best by the interference strap lug 30 that is connected toInner peripheral surface, thereby obtain overrunning belt pulley P5 as shown in Figure 6. Wherein, drag ring 70 being by its internal side diameter outer faceTwo or four end face dental inlay teeth 86 that straight line or cross are uniform, non-rotatably chimeric to week in limiter element 160a and 160bIn the corresponding teeth groove 166 of face. Semi-circular end face flange 162 and 164 in limiter element 160 outside diameter both ends of the surface, supports respectivelyTouch to two bearings 158.
As described in front four patent applications of overall combination above, the associative ring in Fig. 5 also changeable type allows to lead for havingTo the ring-type bag shape shell-type limiter element 140 of the ring 50 radially entrances of inserting. 140/ bag of shape shell of this pocket-type limiter element passes throughThe interference inner peripheral surface of strap lug 30 that is connected to, thus overrunning belt pulley P6 as shown in Figure 7 obtained. Wherein, drag ring 70Radially extend to the adjutage that is provided with keyway 81 170 in described entrance by it with complimentary fashion, with limiter element 140 notRotatably be connected, or, by flat key, be directly non-rotatably connected with the annular component that is specially strap lug 30. More detailedThin explanation and diagram, can referring to above five patent applications of overall combination, no longer repeat specification herein.
As mentioned above, compare for causing traction friction pair to have the coefficient of friction that power transmission friction pair is larger, thereby obtain phaseThe free degree of angle ξ is extruded in larger design/selection, except adopting the scheme of two traction friction mechanism F1 of above-mentioned duplex,Also can be by the scheme of the F1 of this mechanism being arranged to many friction disk types mechanism, and, the revolution friction of transverse plane type more can be obtainedPair, thus the beneficial effect of the designing requirement of space wedge mechanism to axiality thoroughly abandoned. For example, shown in Fig. 8, surmount skinBelt wheel P7 is this kind of modification to overrunning belt pulley P1.
Wherein, drag ring 70 is actually of a rigidity integral type combined type drag ring who comprises strap lug 30Point. At least comprise the inner attrition piece 156 of a group less of, by radial protrusion in it, non-rotatably chimeric to intermediaryEncircle between the end face dental inlay tooth 100 of 90 internal side diameters. The other one group of larger external friction being axially crisscross arranged with inner attrition piece 156Sheet 154, engaging of the inner spline gear 36 by its external spline teeth and strap lug 30, forms non-rotatable connection with this ring. IfOn meter, the location end face 77 of ring-type is conflicted to the location end face 182 of inner spline gear 36, rotates the axial freedom of guiding mechanism GDegree is still more than or equal to zero. As shown in Figure 8, traction rubbing surface 104 and 72 is wherein the indirect modes with at least, in axiallyThe frictional connection state of collision type, its traction friction mechanism F1 has three traction friction pairs.
Obviously, outside friction disc 154 and/or inner attrition piece 156 can be made up of powder metallurgy. And all friction plates moreCan be merged into made by a powder metallurgy and circumferential independent friction plate 155 freely, the shown in Figure 12 belt that surmountsWheel P11. Even, this friction plate 155 more can be attached directly on traction rubbing surface 104 and/or 72 integratedly, becomes a powderMetallurgical boundary-layer. Certainly, the structure of this flexible program seems simpler, seems more easily with more economical, axially in makingSize is also compared less. Certainly, the traction rubbing surface 104 and/or 72 of truncated cone type also can be attached with this powder metallurgy boundary-layer,When the time comes, therefore and best all traction rubbing surfaces 104 and 72 can be modified to simpler transverse plane type by truncated cone type.
Must be pointed out that, because the traction friction mechanism F1 in overrunning belt pulley P7 has adopted the knot of many friction disk typesStructure, and the axiality of the F1 of this mechanism can remain consistent adaptively with the axiality at bearing 158 positions, therefore, at skyBetween in the process of wedge mechanism joint/wedging, can guarantee the produced wedging power in response to transmitted torque, no longer toolThere is the radial component of a tiny bit, no longer have and cause bearing 158 bear additional but be likely its basic dynamic load ratingSeveral times or the radial load of decades of times any may, thereby the working life that can extend significantly bearing 158. And must produceThe raw described additional radial load based on different axialities, this radial load must cause again bearing the joint of slippery formula with separateIn process, enter over worn duty, just roller and diagonal-bracing type freewheel clutch the natural technology having lackFall into. Seen from the above description, the problem that the prior art middle (center) bearing life-span is too short, in overrunning belt pulley P7 because not having and producedRaw architecture basics and be no longer a problem.
Similar with Fig. 2, the overrunning belt pulley P8 shown in Fig. 9, is that overrunning belt pulley P7 is implemented to the modification after radially upsetResult. Wherein, inner spline gear 36 is modified to the dental inlay tooth 86 of drag ring 70, and dental inlay tooth 100 moves to the radial outside of intermediary's ring 90.Drag ring 70 is actually a part for a rigidity integral type combined type drag ring that comprises engage hub 40.
Comparison diagram 1～9 is not difficult to find, its corresponding overrunning belt pulley P1～P8 (comprising follow-up belt pulley P15～P17)In drag ring, be in fact all an axial force closed composition member that includes limiter element, that is bear axially swollenThe annular recess formula of expansive force contains member. Accordingly, the rotation guiding mechanism G in described embodiment, all have attempt axially swollenThe autoexcitation formula application of force effect of the large annular recess that contains the G of this mechanism. And apparently, these technical characterictics neither be essential.For example, Figure 10～Figure 15 just shows relevant modification. Wherein, the overrunning belt pulley P9 shown in Figure 10, can regard the institute to Fig. 4 asShow the modification of overrunning belt pulley P3.
First, overrunning belt pulley P9 has axially exchanged the position of the rotation guiding mechanism G in Fig. 4 and traction friction mechanism F1Put, and cancelled traction friction mechanism F1a. Like this, its guide ring 50 and drag ring 70 have just exchanged role, with strap lug 30 toWhat how be merged into a part is guide ring, is no longer drag ring, with the annular component that is specially engage hub 40 with at leastMode non-rotatable connected be drag ring, be no longer guide ring. Guide ring modification becomes and has axial force closing functionBroad sense annular recess formula contain member.
Should be pointed out that in passing, if by another transmission with axle sleeve be non-rotatably connected in Fig. 8～10 for example inRing 90 the inner or outer side face that is situated between, will cause the intermediary ring of its guide ring 50 on coming true, for example, and super in axle one through-drive typeThe more situation in clutch, so, this actual intermediary ring is exactly that the annular recess formula with axial force closing function containsMember.
Secondly, rotating guiding mechanism G all correspondingly has and attempts axially to dwindle the annular recess that contained by the G of this mechanismAutoexcitation formula application of force effect, starts to bear the axially effect of extruding force in opposite directions as the drag ring of inclusive member.
Again, screw type guiding tooth 52 and 92 is modified to single head or bull saw-tooth thread tooth, is separately positioned on guidingRing 50 and intermediary encircle on the 90 opposed facing inside and outside faces of cylinder of both sides, become side face tooth.
Finally, preloading spring 150 is specially torsionspring, and two termination is entrenched in respectively intermediary encircles the axle of 90 outer facesXiang Kongzhong, and, in the radial hole of strap lug 30 inner peripheral surfaces.
It should be noted that the reason because drawing, the result of whole figure that has been axial turning shown in Figure 10.
Obviously, overrunning belt pulley P9 have the more simple structure of relative overrunning belt pulley P1～P8 and less axially andRadial dimension, more simply makes and assembly technology, and, lower cost of manufacture, but do not reduce previous embodimentWork and serviceability. For example, prior art, has higher wedging reliability because lift angle λ permanent set is constant relatively, because ofFace contact friction is completely secondary and have higher torque capacity/load/transmission capacity, because of without discrete elements and frictional force insulationThere is higher working speed and lower non-load friction resistance in centrifugal force, because of wedging angle almost forever constant and can be automaticCompensate for wear and there is structure and do not damage overlength working life and the durability that the life-span just not stops.
In fact, the external diameter of overrunning belt pulley P1～P4 and follow-up P7～P15 is all no more than 54mm, and width is also superCross 33.5mm, even and if use 45 steel and 2.0 safety coefficient, the torque allowable of for example P9～P10 of overrunning belt pulley is not low yetIn 140NM, far above the 90NM of prior art and the transmission capacity of motor shaft.
In addition, also can simplify overrunning belt pulley P9, thereby obtain implementing three the necessary members that only have of the present inventionThe simplest technical scheme. , its drag ring 70 and the annular component that is specially engage hub 40 are merged into a part, by intermediaryRing 90 is modified to shrinkage type elastic opening ring, and inner circumferential surface can be conflicted to the correspondence of rubbing surface 72 and engage hub 40 simultaneouslySide face 47, and the less flange uniaxially being surrounded by outer peripheral face 48b limits axial location.
Certainly, copy aforementioned variant, also can implement footpath inside and outside upset modification upwards to figure shown in Figure 10, withTo overrunning belt pulley P10 as shown in figure 11. Wherein, for preventing utterly because of the too small drag ring that may cause 70 in truncated cone angleSeparate the trend that axially moves to left in wedge process, between the inner face of the interior warp-wise flange of its left side and outer shroud 30, also can the bestA retaining ring 230 is set. Certainly, retaining ring 230 also can be merged into an independent part with drag ring 70, even,This part is connected and can be modified to the castellated power transmission characteristic surface of end face with the axial conflict of outer shroud 30, thereby can replace alsoThe non-rotatable formula that has spline pair concurrently connects.
And copy example, and remove retaining ring 230, its drag ring 70 and the annular component that is specially outer shroud 30 are merged into oneIndividual part, is modified to intumescent elastic opening ring by intermediary's ring 90, and its outer peripheral face can be conflicted to rubbing surface 72 and skin simultaneouslyThe corresponding inner peripheral surface 35 of band 30, and limited axially position by the less interior radial flange uniaxially of inner peripheral surface 35 axial outer endPut, overrunning belt pulley P10 also can be reduced to and implement the simplest technical scheme that only has three necessary members of the present invention.
It must be noted that, based on structure particularity of the present invention, when the present invention can also have damping clutch jointTorque shock ends, and decaying, it accepts the variant embodiment of the twisting vibration of self-torque upstream. For example,, by institute of the present inventionIn drawings attached, be labeled as the non-rotatable connection at S position, be all modified to or replace with borrowing shown in accompanying drawing 13～18Help the elasticity of Flexible Connector 120 to connect. So, just, can obtain can reduce/damping rotary oscillations of the present invention and/or jointImpact spatial-wedging overrunning belt pulley, surmount decoupler (OAD) and freewheel clutch.
Referring to Figure 13, shown in it be prior art that can be used for automobile current generator alleged surmount decoupler(OAD). It is exactly the result of carrying out above-mentioned modification to embodiment illustrated in fig. 11 that this spatial-wedging surmounts decoupler P12. Wherein, getBeing one and being specially the helical spring Flexible Connector 120 of column type of seville orange flower key auxiliary connection, an one termination 122 is entrenched in toolBody is that in the axial counterbore 31 of inner face of annular component one end inward flange of strap lug 30, its another termination is entrenched in frictionEncircle in the radial hole of 70 outer peripheral faces. This spring can have the rotation direction identical or contrary with spigot surface 54, accordingly, and itself and strap lugThe outer peripheral face of 30 inner peripheral surface and/or drag ring 70 leaves enough radial clearances, and like this, it is in response to the footpath of institute's transmitting torqueJust can not hindered to strain.
Easily expect, the Flexible Connector 120 in Figure 13 also can be specially the one group of linearity that is quantitatively at leastSpring, for example, there is the spring wire of square or circular cross-section, its one end is entrenched in axial counterbore 31, the other end is entrenched inIn the axial groove 71 of drag ring 70 outer peripheral faces. This modification is and surmounts decoupler P13 shown in Figure 14. Compare and surmount decouplerP12 and identical annular space, it is firm that the one group of Flexible Connector 120 that surmounts decoupler P13 is easy to have higher springDegree, therefore, it has larger torque capacity/torque transfer capability, and meanwhile, also because of it, to be easy to have variable spring firmDegree, thus also can have more outstanding decay torque shock ends or the ability of torsional oscillation concurrently.
Such as, referring to Figure 15, by one group of Flexible Connector 120 is arranged to gradually with the circumferential conflict of corresponding axial groove 71The form of inferior realization. That is, in for example R conflict direction pointed, by Flexible Connector for example 120a～120c with correspondingThe internal face of for example 71a～71c of axial groove be arranged to gap and be separated by (can varying degree), like this, at strap lug 30 along R sideIn the operating mode of rotating relative to drag ring 70, it must reach the elastic deformation amount of for example 120d～120e of corresponding Flexible ConnectorAfter corresponding gap value, start just now stressed and strain gradually. Wherein, traction friction mechanism F1 is modified to as figureMany friction plate structures shown in 8～9, and axial groove 71 is also arranged on the outer peripheral face of outside friction disc 154 simultaneously.
Be understood that, the effect of the application's Flexible Connector 120 is similar to the elasticity unit in known yielding couplingPart. In fact, the specific constructive form of Flexible Connector 120 and connected mode, can use for reference known yielding coupling completelyAll technical schemes.
For example, shown in Figure 16～17, surmount the Flexible Connector 120 in decoupler P14, be just specially a ring-typeSerpentine spring. One group of return bend of an axial side of this spring is entrenched in one group of corresponding axial counterbore 31, its axially anotherThe one group of return bend that is arranged in drag ring 70 and strap lug 30 radial clearances of side, articulates/solderless wrapped connection/is socketed in strap lug 30On one group of corresponding radial protrusion 33 of inner peripheral surface. One group of corresponding radial protrusion 73 of drag ring 70 outer peripheral faces, respectively by phaseBetween two adjacent radial protrusions 33, axially stretch between the circular gap of serpentine spring silk.
In this modification, only circular gap/the free degree between for example 73d of radial protrusion and Flexible Connector 120 need be establishedBe set to and be greater than zero, Flexible Connector 120 is just easy to have variable spring rate. In addition, surmount the belt in decoupler P14Ring 30 obviously can be made by the nonmetallic materials of for example wear-resistant plastic, to improve the wear-resisting and corrosion resistant of belt grooveAbility. Certainly, the strap lug that does not bear axial force 30 in other embodiment of the application all can be like this, for example Fig. 3,5～7,9, the strap lug 30 shown in 14,20～21. Further, all strap lugs 30 can be all shown in a similar Figure 20By nonmetallic groove outer shroud is passed through to pouring type, form and be cemented in the associative ring on the outer peripheral face encircling in metal. ToolBody consolidation style can be with reference to known technology, for example, and the fixed scheme of lining, bearing shell and axle sleeve in sliding bearing, and China is speciallyProfit document CN202659848U, CN2275164Y, CN85201131U, CN1868702A, CN2061209U, CN101408193AWith disclosed numerous schemes such as CN104653751A. And nonmetallic material can be for example PA46, PA66, PPS or PEEKThe thermoplastic of series.
For another example, Flexible Connector 120 is specially to one group of circumferential stage clip of cylindrical screw-type, just can be by embodiment illustrated in fig. 1Be modified to and surmount decoupler P15 shown in Figure 18～19. Wherein, the interior radial component of circumferential stage clip is arranged on and is positioned at engage hub 40In the circumferential recess 49 of outer peripheral face, its outer radial part is arranged on the axialmode perforation groove 64 that is arranged in guide ring 50, andConflict to four circumferential inner faces of described groove simultaneously. As mentioned above, by Flexible Connector 120 and such as 64c of perforation grooveBetween circular gap/free degree be arranged to be greater than zero, it is easy to have variable spring rate equally.
Certainly, the circumferential recess 49 in Figure 18 also changeable type is axial groove, meanwhile, Flexible Connector 120 is specially to bulletProperty rubber, gained modification has buffering and the function of vibration damping equally. Further, also Flexible Connector 120 can be specially to oneThe channel rubber of individual complete ring-type as shown in Figure 20. Here, the bent axle vibration damping overrunning belt pulley P16 shown in Figure 20, can seeWork is the simple variant of overrunning belt pulley P6. Wherein, for adapting to the increase of radial dimension, bearing 158 is nested in limiter element 140Endoporus in. One group of installing hole 43 has replaced the section of being threaded 42 in engage hub 40.
Similarly, copy Figure 18, the spline joint pair in Figure 20 also can be specially two groups of cylindrical screws that are set up in parallelThe Flexible Connector 120 of the circumferential stage clip of type replaces, thereby obtains bent axle vibration damping overrunning belt pulley P17 as shown in figure 21. ItsIn, the magnitude of interference coordinating with strap lug 30 inner peripheral surfaces for reducing the outer peripheral face of adjutage 170, at this adjutage 170 and limiter unitOn the inconsistent end face of part 140 both sides, be provided with at least one pair of axial hole, the axial pin 210 being positioned at is wherein fixed into both sidesCircumferentially one. Here, adjutage 170 also has and helps to realize dynamically balanced function, and with complementally occupy whole described in radiallyEntrance space is best.
In addition, bent axle vibration damping overrunning belt pulley P16～P17, and all belt pulleys of the application, also can have combined typeBelt grooves, to transmit reliably larger torque comparing in less radial and axial space. Dependency structure illustrates and saysBright, can also be incorporated into this in full referring to the applicant is open in Chinese patent literature CN102562860A and CN103527748ATechnical scheme, the application is repeat specification no longer.
Certainly, for surmounting decoupler P12～P15 and bent axle vibration damping overrunning belt pulley P16～P17, only need be by itIn the belt groove of strap lug 30 be modified to for example interference fit face, the gear teeth, keyway, pin-and-hole, screw thread or one group of screwOther power transmission characteristic surface in hole and so on, they can be modified to can reduction or damping rotary oscillations and/or joint impactFreewheel clutch.
Finally should be particularly noted that, under the material identical and physical dimension condition, the application's space wedgingTorque capacity/the torque transfer capability of formula overrunning clutch mechanism is at least several times as much as prior art, therefore, eliminates or decay automobileTwisting vibration in front end of crankshaft of internal combustion engine train and the best mode of impact should be only using the song in the source driving as trainShaft pulley replaces with for example P16～P17 of bent axle vibration damping overrunning belt pulley of the application, and without loaded down with trivial details and will do redundantlyFor other belt pulley that is driven target is one by one arranged to overrunning belt pulley. This layout type is compared the beneficial effect that has of prior artReally be, the one, without other is one by one arranged to overrunning belt pulley by drive pulley, thereby cost that can be minimum is realNow reduce the torsion damping of whole train, and, the order that braking that internal combustion engine sharply produces train when reduction of speed is impacted eliminated, the 2nd, just can meet torque request without increasing the size of crank pulley, the 3rd, due to all other belt pulleys again withoutInclude overrunning clutch mechanism, thereby can further reduce the radial dimension of all belt pulleys in whole train, and furtherReduce the total quality of train, final order is to whole train more become miniaturization and lightweight.
Below be only to the present invention is directed to description and the diagram that its limited embodiment gives, there is to a certain degree specialProperty, but it should be understood that mentioned embodiment and accompanying drawing are all only for explanation, and be not used in restriction the present invention and guarantor thereofProtect scope, various variations that they are carried out, be equal to, the change of exchange and member position or structure, all will be considered to not take offLeave the spirit and scope of the present invention's design.
Claims (10)
1. the spatial-wedging overrunning belt pulley that can reduce torsional oscillation, comprising:
Around an axis revolution and at least one traction friction mechanism that can axial engagement, it has around described axis revolution and all establishesThe intermediary's ring and the drag ring that are equipped with traction rubbing surface, described intermediary ring and described drag ring both sides' described traction rubbing surface is axialForm at least one traction friction pair, to transmit friction torque with offseting;
For described traction friction mechanism provides engaging force and around the rotating rotation guiding mechanism of described axis, it has around described axleLine turns round and is provided with guide ring and the described intermediary ring of corresponding spigot surface, described guide ring and the ring both sides' of described intermediary instituteState spigot surface and axially form guiding friction pair with offseting; And
The power transmission friction mechanism at least non-rotatably combining respectively with described guide ring and described drag ring;
Wherein, the lift angle λ at the mutual conflict position of described guiding friction pair, is greater than zero and be less than or equal to ξ, that is, 0 < λ≤ξ, ξ isCan cause upwards equal value open interval of the described lift angle λ of not self-locking of described guiding friction pair and described traction friction pair weekSmall end endpoint value;
It is characterized in that:
On outer peripheral face, be provided with the strap lug of belt tunnel slot type power transmission characteristic surface and described guide ring or described drag ring at leastNon-rotatably be connected; And
Also comprise that at least one is around the rotating annular component of described axis, this annular component is not by least one Flexible ConnectorBe rotationally attached to described guide ring or described drag ring.
2. by overrunning belt pulley claimed in claim 1, it is characterized in that: described Flexible Connector is at least one spiral bulletThe channel rubber of spring, serpentine spring, linear springs or ring-type.
3. by overrunning belt pulley claimed in claim 2, it is characterized in that: described in described guide ring and the ring both sides of described intermediarySpigot surface is the screw type flank of tooth, it is arranged on the ring both sides of described guide ring and described intermediary opposed facing comprise end face, inOn a surface of side face and outer peripheral face; In axial plane, the angle between the described screw type flank of tooth and described axis is greater than 0Degree, is less than 180 degree.
4. by overrunning belt pulley claimed in claim 3, it is characterized in that: the described screw type flank of tooth is separately positioned on described guidingOn ring and the ring both sides' of described intermediary the inner peripheral surface and outer peripheral face mutually directly faced, described guide ring is provided with flanged type limiterEnd.
5. by the overrunning belt pulley described in claim 1～4 any one, it is characterized in that: described traction rubbing surface is by transversalThe bus that is polyline shaped on face turns round the combination of the multiple inner and/or outer frusto-conical surfaces that form around described axis.
6. by the overrunning belt pulley described in claim 1～5 any one, it is characterized in that:
Also comprise that at least one is for sealing the limiter element of axial force; And
In described guide ring and described drag ring one at the most, be at least include by non-rotatable connected mode described inThe force-closed formula combined member of limiter element, connects with the closed conflict of axial force of setting up each other.
7. by the overrunning belt pulley described in claim 1～6 any one, it is characterized in that: described traction friction mechanism is to rub moreScraping-piece type friction mechanism, it is quantitatively all minimum is one and axial staggered two groups of friction plates, non-rotatably distinguishesBe connected to described drag ring and described intermediary ring.
8. by the overrunning belt pulley described in claim 1～7 any one, it is characterized in that: described annular component and described guidingDescribed non-rotatable being connected between ring or described drag ring is to connect into being rigidly connected of being fixed as one.
9. by overrunning belt pulley claimed in claim 8, it is characterized in that: described in to be rigidly connected be to be merged into one of a partBody connects.
10. the spatial-wedging freewheel clutch that can reduce torsional oscillation, is characterized in that: by claim 1～9 any one instituteThe overrunning belt pulley of stating, the belt tunnel slot type power transmission characteristic surface described in it on strap lug by interference fit face, the gear teeth, keyway,Pin-and-hole, screw thread or one group of screw hole replace.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| 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 (3)
| 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 |
| CN2015100738975 | 2015-02-04 | ||
| CN201610089359.XA CN105587797B (en) | 2015-02-04 | 2016-02-04 | Space wedging type overrunning belt pulley capable of reducing torsional vibration and overrunning clutch |
Publications (2)
| Publication Number | Publication Date |
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| CN105587797A true CN105587797A (en) | 2016-05-18 |
| CN105587797B CN105587797B (en) | 2020-11-20 |
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| Application Number | Title | Priority Date | Filing Date |
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| 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 |
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| 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 |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| DE102016206378A1 (en) * | 2016-04-15 | 2017-10-19 | Bayerische Motoren Werke Aktiengesellschaft | Connecting arrangement of a first component to a second component, in particular for a vehicle, and connecting device, in particular for a vehicle |
| CN111425581B (en) * | 2019-01-09 | 2024-08-30 | 舍弗勒投资(中国)有限公司 | Belt pulley decoupler |
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| JPH1030450A (en) * | 1996-07-16 | 1998-02-03 | Nok Megurasutikku Kk | Damper |
| 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 |
| US20030006112A1 (en) * | 2001-07-03 | 2003-01-09 | Asmo Co., Ltd. | Actuator with clutch mechanism |
| US20090107791A1 (en) * | 2007-10-25 | 2009-04-30 | Lin Zhu | 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 |
| CN102562859A (en) * | 2010-12-30 | 2012-07-11 | 洪涛 | One-way transmission device containing space-wedged-type frictional overrun clutch mechanism |
| CN102619902A (en) * | 2010-12-30 | 2012-08-01 | 洪涛 | Spatial wedge type double-clutch |
| CN102758859A (en) * | 2012-07-27 | 2012-10-31 | 罗俊 | Friction type overrunning 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
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH1030450A (en) * | 1996-07-16 | 1998-02-03 | Nok Megurasutikku Kk | Damper |
| US20030006112A1 (en) * | 2001-07-03 | 2003-01-09 | Asmo Co., Ltd. | Actuator with clutch mechanism |
| 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 |
| US20090107791A1 (en) * | 2007-10-25 | 2009-04-30 | Lin Zhu | 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 |
| CN102562859A (en) * | 2010-12-30 | 2012-07-11 | 洪涛 | One-way transmission device containing space-wedged-type frictional overrun clutch mechanism |
| CN102619902A (en) * | 2010-12-30 | 2012-08-01 | 洪涛 | Spatial wedge type double-clutch |
| CN102758859A (en) * | 2012-07-27 | 2012-10-31 | 罗俊 | Friction type overrunning clutch |
Also Published As
| Publication number | Publication date |
|---|---|
| CN104791398A (en) | 2015-07-22 |
| CN105587797B (en) | 2020-11-20 |
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Effective date of registration: 20210507 Address after: 272600 quanpu Industrial Park, Liangshan County, Jining City, Shandong Province (1 Tongya Road) Patentee after: SHANDONG SHENGRUN AUTOMOBILE Co.,Ltd. Address before: 524019 No. 2, No. 4, building 2, 302 West Jianxin Road, Xiashan District, Guangdong, Zhanjiang Patentee before: Hong Tao |
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Denomination of invention: Space wedge type overrunning pulley and overrunning clutch for reducing torsional vibration Effective date of registration: 20230320 Granted publication date: 20201120 Pledgee: Liangshan County sub branch of Postal Savings Bank of China Ltd. Pledgor: SHANDONG SHENGRUN AUTOMOBILE Co.,Ltd. Registration number: Y2023980035532 |
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