CN105587797B

CN105587797B - Space wedging type overrunning belt pulley capable of reducing torsional vibration and overrunning clutch

Info

Publication number: CN105587797B
Application number: CN201610089359.XA
Authority: CN
Inventors: 洪涛
Original assignee: 洪涛
Current assignee: SHANDONG SHENGRUN AUTOMOBILE Co.,Ltd.
Priority date: 2015-02-04
Filing date: 2016-02-04
Publication date: 2020-11-20
Anticipated expiration: 2036-02-04
Also published as: CN105587797A; CN104791398A

Abstract

The space wedged overrunning belt pulley and overrunning clutch capable of reducing torsional vibration includes guide ring, intermediate ring, friction ring and belt ring or joint hub connected to the guide ring or friction ring via elastic connecting part. The intermediate ring and the guide ring form a self-excitation type rotation guide mechanism G through the one-way spiral guide teeth, and the friction ring, the intermediate ring and the guide ring form a rotary type traction friction mechanism F1 and a force transmission friction mechanism F2 respectively. The three mechanisms axially offset to form an axial force closed system. Compared with the prior art, the three friction mechanisms have the characteristics of complete surface contact, automatic wear compensation and no discrete component, so that the three friction mechanisms have various excellent qualities of ideal working reliability, no damage to the structure and no end of the service life.

Description

Space wedging type overrunning belt pulley capable of reducing torsional vibration and overrunning clutch

RELATED APPLICATIONS

The present application is a dependent patent application of the four patent applications of the present applicant disclosed in patent documents CN101936346B, CN102562859A, CN104565122A and CN104963963A, and the present application claims priority from the prior patent application of the present applicant disclosed in patent document CN 104791398A. The entire contents of the five prior published patent applications are incorporated herein by reference.

Technical Field

The present invention relates to an overrunning transmission device capable of transmitting torque/rotational motion in only one direction and automatically disengaging and freewheeling in the opposite direction by means of an endless flexible member, and capable of reducing or attenuating torsional vibrations and/or engagement shocks, and to an overrunning clutch, particularly but not exclusively to an overrunning pulley incorporating an overrunning clutch mechanism for a front end train of a crankshaft of an automotive internal combustion engine.

Background

The one-way transmission wheels used in the prior art, such as turbocharger Overrunning Pulley, crankshaft Overrunning Pulley, and Generator Overrunning Pulley (OAP, or Generator Overrunning Pulley, GOP) and/or Overrunning Decoupler (OAD) used in the front end train of the crankshaft of the internal combustion engine of the automobile, have technical defects such as too small torque capacity and/or transmission capacity, easy wear and too short service life. Moreover, they are also relatively complex in construction, manufacture and assembly. In the application fields with stronger torque impact such as petroleum and agricultural machinery, for example, in the transmission systems of oil pumping units and corn, wheat and rice harvesting/cutting machines, the service life of the existing one-way/overrunning belt pulley is shorter.

In addition, prior art overrunning clutches do not have substantial drive capability that is effective in reducing/attenuating torsional vibrations and engagement shocks.

Disclosure of Invention

The present invention seeks to obviate or at least mitigate the above-mentioned disadvantages of the prior art.

The invention aims to provide a spatial wedged overrunning belt pulley which has higher torque capacity, longer service life and simpler structure and can reduce/attenuate torsional vibration and joint impact.

The invention aims to solve another technical problem of providing a space wedge type overrunning clutch which has higher torque capacity, longer service life and simpler structure and can reduce torsional vibration.

In order to solve the above technical problems, the spatial wedge type overrunning belt pulley capable of reducing torsional vibration of the present invention comprises at least one traction friction mechanism rotating around an axis and capable of being axially engaged, the traction friction mechanism comprises an intermediate ring and a friction ring rotating around the axis and both provided with traction friction surfaces, and the traction friction surfaces of the intermediate ring and the friction ring axially abut against each other to form at least one traction friction pair so as to transmit friction torque between the two rings; at least one rotary guide mechanism which provides joint force for the traction friction mechanism and rotates around the axis, and is provided with a guide ring and an intermediate ring which rotate around the axis and are provided with corresponding guide surfaces, wherein the guide surfaces of the guide ring and the intermediate ring are axially abutted to form a guide friction pair; a force-transmitting friction mechanism which is at least non-rotatably combined with the guide ring and the friction ring respectively; the belt ring is at least non-rotatably connected with the guide ring or the friction ring, and the outer peripheral surface of the belt ring is provided with a belt groove type force transmission characteristic curved surface; and at least one annular member revolving about said axis, the annular member being non-rotatably connected to the guide ring or the friction ring by at least one elastic connection; the lead angle lambda of the mutual interference part of the guide friction pair is larger than zero and smaller than or equal to xi, namely lambda is more than 0 and smaller than or equal to xi, and xi is a small end point value of the value opening interval of the lead angle lambda, which can cause the guide friction pair and the traction friction pair not to be self-locked in the circumferential direction.

Optionally, the ring-like member is served by an engagement hub or belt ring.

Preferably, the non-rotatable connection between the annular member and the guide ring or the friction ring is a movable connection which is axially movable relative to each other but not circumferentially rotatable relative to each other.

Preferably, the traction friction surface may be a combination of a plurality of inner and/or outer truncated conical surfaces formed by a generatrix with a polygonal line shape in cross section revolving around the axis.

Preferably, the traction friction mechanism may be a multi-friction-plate friction mechanism, which has at least one friction plate in number and two axially staggered friction plates, non-rotatably connected to the friction ring and the intermediate ring, respectively.

Preferably, the traction friction pair is separated by a separate friction plate made of powder metallurgy and free in the circumferential direction, or at least one traction friction surface of the traction friction pair is adhered with a powder metallurgy adhesion layer.

Optionally, a resilient pretensioning mechanism with at least one resilient element is also included for continuously establishing an at least indirect frictional connection between the intermediate ring and the friction ring.

Optionally, the belt loop is non-rotatably connected or integrated in one piece with one of the guide ring, the friction ring and the force limiting element.

In order to solve the above-mentioned another technical problem, the spatial wedge type overrunning clutch capable of reducing torsional vibration of the present invention includes the above-mentioned overrunning decoupler, but the belt groove type force transmission characteristic curved surface on the belt ring is replaced by a force transmission characteristic curved surface such as an interference fit surface, a gear tooth, a key groove, a pin hole, a thread or a set of screw holes.

Further developments of the invention are given in the detailed description.

It should be specifically noted that the related concepts or terms in the present specification have the following meanings:

a rotation guide mechanism: a guide mechanism for converting circumferential relative rotation into a guide mechanism including at least axial relative movement or a tendency to move. For example, sliding/rolling screw or partial screw mechanisms with strictly uniform and non-strictly uniform lead angles, radial pin slot mechanisms, end face wedge mechanisms, end face jogging mechanisms, end face ratchet mechanisms, and cylinder/end face cam mechanisms.

The space wedge-shaped mechanism comprises: the composite mechanism consists of a rotary guide mechanism and a traction friction mechanism.

ζ and ξ: the climbing angle and the extrusion angle of the spatial wedge mechanism. That is, in the rotation guide operation mode of the rotation guide mechanism G, that is, in the case where the guide ring 50 starts to continuously have a tendency to drive the intermediate ring 90 to rotate relative to the friction ring 70 in the direction indicated by the arrow P in fig. 2, for example, the minimum elevation angle λ at which the contact portions of both surfaces that can ensure the self-locking of the guide friction pair are abutted is defined as ζ, which is also referred to as the climb angle of the intermediate ring 90, and the maximum elevation angle is defined as ξ, which is also referred to as the extrusion angle of the intermediate ring 90. For a more detailed description, reference is made to the descriptions in the first four patent applications incorporated in their entirety as above, for example, paragraphs [0031] to [0035] in the specification of patent document CN101936346B and paragraphs [0029] to [0032] in the specification of patent application 201410555684.1, which are not further described herein.

Compared with the prior art, the spatial wedge type overrunning belt pulley and the overrunning clutch capable of reducing the torsional vibration have the advantages of simple structure, reliable wedge, ultra-long service life and durability, higher torque capacity and working rotating speed, easiness in manufacturing and assembling and the like. The objects and advantages of the invention will become more apparent and obvious from the following description of the embodiments and the accompanying drawings.

Drawings

Fig. 1 is an axial cross-sectional view of a first embodiment of the present invention.

Fig. 2 is a schematic partial development of the relevant contour of the mechanisms on the section K-K in fig. 1, projected radially to the same outer cylindrical surface.

Fig. 3 is an axial sectional view of a second embodiment of the present invention.

Fig. 4 is an axial sectional view of a third embodiment of the present invention.

Fig. 5 is an axial sectional view of a fourth embodiment according to the present invention.

Fig. 6 is an axial sectional view of embodiment five according to the present invention.

Fig. 7 is an axial cross-sectional view of a sixth embodiment in accordance with the present invention.

Fig. 8 is an axial sectional view of embodiment seven according to the present invention.

Fig. 9 is an axial sectional view of an embodiment eight according to the present invention.

Fig. 10 is an axial sectional view of an embodiment nine according to the present invention.

Fig. 11 is an axial sectional view of an embodiment ten according to the present invention.

Fig. 12 is an axial sectional view of embodiment eleven according to the present invention.

FIG. 13 is an axial cross-sectional view of an embodiment twelve, in accordance with the present invention.

Fig. 14 is an axial sectional view of embodiment thirteen according to the present invention.

Fig. 15 is a schematic partial development of the relevant profiles of the mechanisms on the section K-K in fig. 15, projected radially to the same outer cylindrical surface.

FIG. 16 is an axial cross-sectional view of a fourteenth embodiment in accordance with the invention.

Fig. 17 is a schematic partial development of the relevant profiles of the mechanisms on the section K-K in fig. 16, projected radially to the same outer cylindrical surface.

Fig. 18 is an axial cross-sectional view of example fifteen according to the invention.

Fig. 19 is a schematic partial development of the relevant profiles of the mechanisms on the section K-K in fig. 18, projected radially to the same outer cylindrical surface.

Fig. 20 is an axial cross-sectional view of sixteen embodiments according to the invention.

Figure 21 is an axial cross-sectional view of a seventeenth embodiment according to the present invention.

Detailed Description

The essential explanation is as follows: for the sake of clarity, the same reference numerals are used throughout the text of the description and the drawings for identical or similar components and features, and the necessary description is given only when they first appear or are modified. Likewise, the description of the mechanism or process of operation of the same or similar mechanism is not repeated. To distinguish identical components or features that are arranged in symmetrical or corresponding positions, the present specification appends letters to their reference numerals, and does not append any letters to the general description or to the exclusion.

Referring to the embodiment of FIGS. 1-2, an internally guided externally threaded space wedge overrunning pulley P1. The friction ring 70 rotating around the axis X is coaxially screwed to the complementary internal thread teeth on the inner circumferential surface of the belt ring 30 from one axial end by means of the zigzag external thread teeth 79, and the annular positioning end surface 77 thereof abuts against the annular step-shaped positioning end surface 182 at the inner end of the internal thread teeth, so as to define together with the flange-type annular force-limiting end 188 at the inner end of the step, an axially closed inner radial open annular groove formed by rotating a single bus around the axis X.

At the same time, the friction ring 70 is also connected to the belt ring 30, which actually serves as the force limiting member 180, as a combined ring. The unison ring is positioned radially on the corresponding outer

peripheral surfaces

48a and 48b on both ends of the engagement hub 40 that revolve about the axis X, by means of

bearings

158a and 158b in the inner bores on both ends thereof, respectively. Here, the bearing 158a is preferably a needle bearing, and the inner and outer races of the bearing 158b, which is embodied as a deep groove ball, are preferably coupled to the respective inner and outer circumferential surfaces in an interference fit manner.

Seals

110a and 110b are also preferably provided in the annular space at the outer ends of the bearings 158.

In the axially closed annular groove, the guide ring 50 and the intermediate ring 90, which are rotated about the axis X and are axially fitted to each other, are axially continuously abutted against the force limiting end 188 and the friction ring 70, respectively, by the circumferential action of the preload spring 150 provided between the two rings, so as to form two rotation-type force-transmitting friction mechanisms F2 and a traction friction mechanism F1, respectively, which are rotated about the axis X. The traction friction mechanisms F1a and F1b each have a truncated cone type traction friction pair which is not self-locking in the axial direction, and two sets of structurally complementary truncated cone type rotary traction friction surfaces 104a and 72a and 104b and 72b are respectively arranged on axially opposite end faces of the intermediate ring 90 and the friction ring 70. The force-transmitting friction means F2 has a planar force-transmitting friction pair with complementary rotary force-transmitting friction surfaces 58 and 74, respectively, arranged on axially opposite end faces of the guide ring 50 and the force-limiting end 188. The guide ring 50 is non-rotatably fitted over the outer peripheral surface of the annular member, specifically the engagement hub 40, by means of a spline pair. The engagement hub 40 has a cylindrical base section 44, a threaded connection section 42, and an operation section 46 for mounting and dismounting, which is in the form of a spline or a non-circular hole such as a hexagon, on the inner peripheral surface thereof.

In order to have a modified embodiment damping the torque shock during clutch engagement and damping the torsional vibrations that it receives upstream from the torque, a technical effect similar to what is known as OAD is obtained, wherein the non-rotatable connection, marked S in fig. 1, can also be modified or replaced by an elastic connection by means of an elastic connection 120, as will be described in detail later.

It should be noted that, in fig. 1, an intermediate ring 90b can also be arranged axially symmetrically between the friction surfaces 58 and 74 to form, together with the guide ring 50 and the force-limiting end 188, a further at least approximately symmetrical rotary guide Gb and traction friction F1b, respectively. The variant overrunning pulley will then no longer have the force-transmitting friction means F2, but simultaneously have two traction friction means F1a and F1b of the twin type, which share the same combined friction ring. All traction friction surfaces can be optimally deformed into end planes, so that the design requirement of the space wedge mechanism on the coaxiality can be completely eliminated, and the manufacturing process is obviously simplified.

With continued reference to fig. 1-2, the rotary guide mechanism G, which rotates about the axis X, includes a guide ring 50 and an intermediate ring 90, a set of constantly engaging, serrated,

helical guide teeth

52 and 92, respectively, correspondingly disposed on the facing annular end surfaces of the two rings. The guide surfaces 54 and 94 of the two guide teeth are preferably a set of complementary configured helical tooth surfaces to form a set of surface contacting helical guide friction pairs, and the respective set of circumferential clearance non-guide surfaces 56 and 96 of the two guide teeth are preferably parallel to the axis X. The expanding open ring-shaped pretensioning spring 150 of the elastic pretensioning means located in the space radially inside the

guide teeth

52 and 92 has two ends extending radially into the circumferential gap to elastically and circumferentially abut against the

non-guide surfaces

56 and 96, respectively, so that the guide surfaces 54 and 94 continuously abut against each other in the circumferential direction, the rotary guide means G is always in the rotary guide condition, and finally the traction friction means F1 and the force-transmission friction means F2 are always in the abutting state.

In general, the lead angles of the guide surfaces 54 and 94 are each λ, and 0 < λ ≦ ξ, specifically, ζ < λ ≦ ξ or 0 < λ ≦ ζ (when ζ > 0). The axial degree of freedom/clearance of the rotary guide mechanism G is more than or equal to 0. The guide surfaces 54 and 94 are angled more than 0 degrees and less than 180 degrees from the axis X in the plane of the axis X. The guide surfaces 54 and/or 94 may also be optimally provided with grooves to dissipate heat or remove liquid/gas, if desired.

As shown in fig. 2, the external thread teeth 79 are twisted in the same direction as the guide surfaces 54 and 94, and the lead angle thereof should be optimally smaller than the extrusion angle ξ. In order to improve the connection reliability of the friction ring 70, an axial or radial pin-hole type fitting mechanism or a known mechanism or structure for preventing the screw connection from loosening may be provided between the friction ring and the belt ring 30.

The operation of the overrunning pulley P1 is very simple. When the belt, not shown, rapidly rotates the belt ring 30 and the friction ring 70 together by friction with the belt groove type force transmission characteristic curved surface, for example, at the initial moment when it starts to continuously have a tendency to rotate in driving relative to the guide ring 50 in the direction indicated by the arrow R in fig. 2, the friction ring 70 passes through the traction friction torque of the traction friction mechanism F1, so that the intermediate ring 90 has a tendency to rotate synchronously relative to the guide ring 50 in the direction indicated by the arrow R. The self-excited axial expansion force generated by the tendency of rotation by the guide surfaces 94 and 54 causes the guide teeth 92 to wedge instantaneously in the wedge-shaped space defined by the guide surfaces 54 and the traction friction surface 72, thereby wedging the guide ring 50 and the friction ring 70 into a friction unit, and the traction friction mechanism F1 is axially engaged, and the expansion force also expands the guide ring 50 instantaneously against the force-transmitting friction surface 74 to form an axial force-closing interference connection, causing the force-transmitting friction mechanism F2 to synchronously engage and indirectly connect the guide ring 50 and the friction ring 70 into a friction unit.

Thus, the overrunning pulley P1 engages with the wedging of the space wedge mechanism. The drive torque M from a belt, not shown, introduced by the belt loop 30₀Divided into wedging friction torques M transmitted via the rotary guide G, traction friction mechanisms F1a and F1b₁And a force-transmitting friction torque M directly transmitted via a force-transmitting friction mechanism F2₂Respectively, to the guide ring 50, to the engagement hub 40 in its inner bore by means of a non-rotatable or elastic connection, and finally to a not shown shaft of, for example, a generator. Wherein M is₀＝M₁+M₂. Obviously, the magnitudes of the axial expansion force, the wedging force and the friction forces are all in full self-adaption proportion to M₁That is to say M₀Moreover, torque may also be transmitted in the opposite path as described above without any substantial difference.

When the belt, not shown, forces the belt ring 30 and the friction ring 70 to start rotating slowly by friction with the belt groove type force transmission characteristic curved surface, for example, at the initial moment when the belt starts to continuously have the tendency to perform the wedging rotation with respect to the guide ring 50 in the direction indicated by the arrow P in fig. 2, that is, the moment when the driving rotation tendency disappears, the friction ring 70 pulls the intermediate ring 90 to rotate with respect to the guide ring 50 by the friction torque of the traction friction mechanism F1 to release the guiding action of the rotation guide mechanism G. Thus, the normal pressure between the guide surfaces 54 and 94 and the rotary guiding action of the rotary guide mechanism G are simultaneously lost as the two guide surfaces have a tendency to move out of contact with each other. Naturally, the two friction means F1 and F2, which work on the basis of the axial self-energizing tightening force of the rotary guide means G, and the entire spatial wedge means, will then separate or de-wedge. Then, the overrunning pulley P1 ends engagement and starts overrunning rotation, i.e., the intermediate ring 90 starts frictional slip rotation in the R direction with respect to the friction ring 70 following the guide ring 50.

While the above four incorporated and integrated patent applications describe that the relevant components can still be axially force-closed interference connected as long as they can maintain a spatial wedge-shaped mechanism that meets the lift angle requirements, the construction and location of all components of the present application are not limited and can be altered or replaced, with numerous variations.

For example, it is conceivable from the basic mechanical common knowledge that the structure and positional relationship of the overrunning pulley P1 shown in FIG. 1 is turned inside out in the radial direction, and the overrunning pulley P2 shown in FIG. 3 can be obtained without any substantial difference. Of course, for ease of manufacture and structural strength, the variant shown in fig. 3 is the result of exchanging the axial positions of the traction friction means F1 and the force-transmitting friction means F2, and simplifying the zigzag thread pair into a simpler triangular thread pair. The annular positioning end face 182 of the force-limiting element 180, located at the front end of the inner tubular base 186, directly abuts against the inner end face 77 of the friction ring 70, located inside the traction friction surface 72a, so as to jointly define an annular groove of axially closed type, radially open type, turned around the axis X by a single generatrix. The ring-shaped member, in particular the belt ring 30, is at least non-rotatably connected to the guide ring 50 by means of a spline pair.

Also, it is also possible to combine the friction ring 70 in fig. 1 with the belt ring 30 at most in one piece, while modifying the force limiting end 188 to be a separate member connected to the inner peripheral surface of the belt ring 30 by a screw pair. Further, the threaded pair connection may be replaced with a fixed connection of a circumferential weld 200, resulting in an overrunning pulley P3 as shown in fig. 4. Wherein the snap ring 190 on the outer peripheral surface of the engagement hub 40 is an axial positioning member.

It will be understood that the force limiting element 180, which is incorporated at most in one piece with the belt ring 30 in fig. 1, can also be made separately and welded to the friction ring 70 of the cup-shaped shell to form a separate combined ring with an axially closed inner radially open annular groove, thus being modified as an overrunning pulley P4 as shown in fig. 5. Wherein the guide ring 50 is integrated with the engagement hub 40 in one piece for ease of manufacture. Accordingly, the friction ring 70 is non-rotatably connected to the inner circumferential surface of the belt ring 30 by means of, for example, a spline pair, to obtain an axial displacement capability that automatically responds to mechanical wear. And the pre-tensioned spring 150 may be embodied as, for example, a set of wave springs made of wire or sheet material, respectively disposed between each set of mutually facing

non-facing surfaces

56 and 96.

As described in the above-incorporated four prior patent applications, the composite ring of fig. 5 may also be modified into two radially fully symmetrical half-shell

force limiting members

160a and 160b, which are preferably secured to the inner circumferential surface of belt ring 30 by an interference connection, resulting in an overrunning pulley P5 as shown in fig. 6. The friction ring 70 is non-rotatably fitted into the corresponding tooth grooves 166 on the inner circumferential surfaces of the

force limiting members

160a and 160b by two or four end face teeth 86 on the inner and outer end faces of the inner diameter side, which are arranged in a straight line or a cross shape. Semi-annular end face

flanges

162 and 164 on both end faces on the outer diameter side of the force limiting member 160 abut against the two bearings 158, respectively.

As described in the above-incorporated four prior patent applications, the composite ring of fig. 5 may also be modified to have an annular pocket-type shell force-limiting element 140 with a radial entry that allows the pilot ring 50 to be inserted. The pocket type force limiting member 140/pocket housing is fixed to the inner peripheral surface of the belt ring 30 by interference coupling, resulting in the overrunning pulley P6 shown in fig. 7. Wherein the friction ring 70 is non-rotatably connected with the force limiting element 140 by means of its extension arm 170 provided with a key way 81 extending radially in a complementary manner into said inlet, or directly non-rotatably connected with an annular member, in particular a belt ring 30, by means of a flat key. For more detailed description and illustration, reference may be made to the five patent applications incorporated in their entirety above, and the description will not be repeated here.

As described above, in order to make the traction friction pair have a larger friction coefficient than the force transmission friction pair, thereby obtaining a larger degree of freedom of designing/selecting the extrusion angle ξ, besides the scheme of adopting the above-mentioned two traction friction mechanisms F1 in pair, the scheme of setting the mechanism F1 into a multi-friction-piece mechanism can be used, and furthermore, a rotary friction pair with a planar end surface can be obtained, thereby completely abandoning the beneficial effect of the space wedge mechanism on the design requirement of coaxiality. For example, overrunning pulley P7 shown in fig. 8 is such a variation of overrunning pulley P1.

Wherein friction ring 70 is actually part of a rigid one-piece composite friction ring that includes belt loop 30. A set of at least one smaller inner friction plate 156 is non-rotatably engaged by its inner radial projections between the end face teeth 100 on the inner diameter side of the intermediate ring 90. A further set of larger outer friction plates 154, axially interleaved with the inner friction plates 156, are in non-rotatable connection with the belt ring 30 by their engagement of their outer spline teeth with the inner spline teeth 36 of the ring. In design, after the annular positioning end surface 77 abuts against the positioning end surface 182 of the internal spline tooth 36, the axial degree of freedom of the rotary guide mechanism G is still greater than or equal to zero. As shown in fig. 8, the traction friction surfaces 104 and 72 are at least indirectly in an axially abutting frictional engagement, and the traction friction mechanism F1 has three traction friction pairs.

It will be apparent that the outer friction plate 154 and/or the inner friction plate 156 may be made of powder metallurgy. Furthermore, all the friction plates can be combined into a single friction plate 155 made of powder metallurgy and free in the circumferential direction, see the overrunning pulley P11 shown in fig. 12. Even more preferably, the friction plate 155 is integrally attached directly to the traction friction surfaces 104 and/or 72 as a powder metallurgy facing layer. The construction of this variant is undoubtedly simpler, easier and more economical to produce, and the axial dimensions are also smaller. Of course, the traction friction surfaces 104 and/or 72 of the truncated cone type can also be provided with this powder metallurgy boundary layer, in which case all traction friction surfaces 104 and 72 can thus be optimally modified from the truncated cone type to a simpler end-face type.

It must be pointed out that, since the traction friction means F1 in the overrunning pulley P7 is of multi-friction-plate type, and the coaxiality of this means F1 is in turn adaptively and always consistent with that of the bearing 158, it is possible to ensure that the wedging force generated in response to the transmitted torque during the engagement/wedging of the spatial wedge means, no longer has a component of radial force of one millionthe, no longer has any possibility of causing the bearing 158 to bear an additional radial force, which is likely to be several or ten times its basic dynamic load rating, and thus to significantly extend the working life of the bearing 158. The additional radial forces, which are necessarily generated on the basis of the different coaxiality, which in turn necessarily bring the bearing into an excessively worn operating condition during the slipping engagement and disengagement process, are the technical drawbacks naturally present in roller-type and sprag-type overrunning clutches. As can be seen from the above description, the problem of too short bearing life in the prior art is no longer a problem in overrunning pulley P7 because it does not have the structural foundation that is created.

Similar to fig. 2, the overrunning pulley P8 shown in fig. 9 is a modified result of the radial reversal of the overrunning pulley P7. Wherein the internal spline teeth 36 are modified into the dog teeth 86 of the friction ring 70, the dog teeth 100 are moved radially outward of the intermediate ring 90. Friction ring 70 is actually part of a rigid, one-piece, modular friction ring that includes engagement hub 40.

In comparison with fig. 1-9, it can be seen that the friction ring of the overrunning pulley P1-P8 (including the subsequent pulleys P15-P17) is actually an axial force closed combination member including a force-limiting element, i.e., an annular groove-type housing member that is subjected to axial expansion force. Correspondingly, the rotary guide means G in the described embodiments have a self-energizing force application effect which attempts to expand the annular groove which accommodates the means G axially. And obviously these technical features are not necessary either. For example, fig. 10 to 15 show related modifications. Among these, the overrunning pulley P9 shown in fig. 10 can be regarded as a modification of the overrunning pulley P3 shown in fig. 4.

First, overrunning pulley P9 has axially interchanged the positions of rotational guide mechanism G and traction friction mechanism F1 in fig. 4, and traction friction mechanism F1a is eliminated. In this way, the guide ring 50 and the friction ring 70 thereof have interchanged roles, the one which is at most integrated into one part with the belt ring 30 being the guide ring, no longer the friction ring, the one which is at least non-rotatably connected to the annular member, in particular the engagement hub 40, being the friction ring, no longer the guide ring. The guide ring has been modified to be a generalized annular grooved female member with an axial force closure function.

Incidentally, if another drive bushing is non-rotatably connected to the inner or outer peripheral surface of the intermediate ring 90, as in fig. 8-10, for example, such that its guide ring 50 becomes the actual intermediate ring, as is the case, for example, in an overrunning clutch of the shaft-to-shaft drive type, then this actual intermediate ring is an annular grooved female member having an axial force-closing function.

Secondly, the rotary guides G each have a corresponding self-energizing force-application effect which attempts to axially reduce the annular groove accommodated by the guide G, as the friction ring of the accommodated member begins to bear the axially directed pressing force.

Again, the

helical guide teeth

52 and 92 are modified into single-start or multi-start zigzag thread teeth, and are provided on the inner and outer cylindrical surfaces of the guide ring 50 and the intermediate ring 90, respectively, facing each other, as circumferential teeth.

Finally, the pre-tightening spring 150 is a torsion spring, and two ends of the torsion spring are respectively embedded in an axial hole on the outer end surface of the intermediate ring 90 and a radial hole on the inner circumferential surface of the belt ring 30.

It should be noted that for drawing reasons, what is shown in fig. 10 is the result of the entire figure being turned axially.

It is clear that overrunning pulley P9 has a simpler construction and smaller axial and radial dimensions, simpler manufacturing and assembly processes, and lower manufacturing costs relative to overrunning pulleys P1-P8, but does not reduce the operation and performance of the previous embodiments. For example, compared to the prior art, the wedge has higher wedging reliability due to the permanently fixed lead angle λ, higher torque capacity/load/transmission capacity due to the complete surface contact friction pair, higher operating speed and lower idle frictional resistance due to the absence of discrete components and the frictional force insulation from centrifugal force, and ultra-long service life and durability due to the almost permanently unchanged wedge angle and the ability to automatically compensate for wear without destroying the structure and without ending the life.

In fact, the outside diameters of the overrunning pulleys P1-P4 and the subsequent P7-P15 do not exceed 54mm, the widths do not exceed 33.5mm, and even if 45 steel and a safety factor of 2.0 are used, the allowable torque of the overrunning pulleys such as P9-P10 is not lower than 140 N.M and is far higher than the 90 N.M and the transmission capacity of the motor shaft in the prior art.

In addition, the overrunning pulley P9 can be simplified, so that the simplest technical solution of only three necessary components for implementing the invention is obtained. That is, the friction ring 70 thereof is incorporated into one piece with the annular member, specifically, the engaging hub 40, and the intermediate ring 90 is modified into a contractible elastic split ring so that its inner circumferential surface can simultaneously abut against the friction surface 72 and the corresponding outer circumferential surface 47 of the engaging hub 40, and its axial position is unidirectionally defined by a smaller flange surrounded by the outer circumferential surface 48 b.

It goes without saying that, following the previous variant, it is also possible to carry out a radially inside-outside turning variant of the figure shown in fig. 10, so as to obtain an overrunning pulley P10 as shown in fig. 11. In order to prevent the tendency of the friction ring 70 to move to the left in the axial direction during the wedging process, which may be caused by a too small truncated cone angle, a retaining ring 230 is preferably provided between its left end face and the inner end face of the inner radial flange of the outer ring 30. Of course, the anti-slip ring 230 can be combined with the friction ring 70 to form a single part, and even the axial interference connection between the part and the outer ring 30 can be modified to be a force transmission characteristic curve surface of an end surface jaw type, so that the non-rotatable connection of a spline pair can be replaced and also used.

In the same way as the above example, the anti-slip ring 230 is removed, the friction ring 70 is combined with the ring-shaped member, specifically the outer ring 30, to form a single part, the intermediate ring 90 is modified to be an expanding elastic snap ring, so that the outer circumferential surface thereof can simultaneously abut against the friction surface 72 and the corresponding inner circumferential surface 35 of the belt ring 30, and the axial position thereof is unidirectionally limited by the smaller inner radial flanges at the axial outer ends of the inner circumferential surface 35, and the overrunning belt pulley P10 can also be simplified to the simplest technical solution of implementing only three necessary members of the present invention.

It must be pointed out that, on the basis of the constructive particularity of the invention, the invention may also have a variant embodiment of damping the torque shock at the clutch engagement, and of damping the torsional vibrations it receives upstream from the torque. For example, the non-rotatable connection, labeled S-site throughout the drawings of the present invention, is fully modified or replaced with a resilient connection such as that shown in FIGS. 13-18 by means of resilient connectors 120. In this way, the space wedge overrunning pulley, overrunning decoupler (OAD) and overrunning clutch of the present invention are achieved that are capable of reducing/attenuating torsional vibrations and/or engagement shocks.

Referring to fig. 13, a prior art so-called overrunning decoupler (OAD) is shown that may be used in an automotive generator. This space-wedged overrunning decoupler P12 is the result of the above-described modification to the embodiment shown in fig. 11. Instead of the spline connection pair, an elastic connection member 120, specifically a cylindrical coil spring, has one end 122 fitted in an axial counterbore 31 of the inner end face of an inner flange at one end of the ring-shaped member, specifically the belt ring 30, and the other end fitted in a radial hole in the outer peripheral surface of the friction ring 70. The spring may have the same or opposite handedness as the guide surface 54, and accordingly, it may have a sufficient radial clearance from the inner circumferential surface of the belt ring 30 and/or the outer circumferential surface of the friction ring 70 so that its radial elastic deformation in response to the transmitted torque is not hindered.

It is easily conceivable that the elastic connection element 120 in fig. 13 may also be embodied as a set of at least one linear spring, for example, a spring wire with a square or circular cross-section, one end of which is fitted in the axial counterbore 31 and the other end of which is fitted in the axial groove 71 in the outer circumferential surface of the friction ring 70. This variation is the over-running decoupler P13 shown in fig. 14. The set of resilient couplings 120 of the over-running decoupler P13 tend to have a higher spring rate than the over-running decoupler P12 and the same annular space, thus providing greater torque capacity/torque transfer capability, while also providing superior torque shock or torsional damping capability due to their variable spring rate.

For example, with reference to fig. 15, the circumferential interference of a set of elastic connectors 120 with the corresponding axial slots 71 is provided in a progressive manner. That is, in the interference direction, for example, in which R is directed, the elastic connection members, for example, 120a to 120c, are spaced apart (may be unequal in degree) from the inner wall surfaces of the corresponding axial grooves, for example, 71a to 71c, so that, in an operating condition in which the belt ring 30 is rotated in the direction R relative to the friction ring 70, it is necessary to gradually start the force and elastic deformation after the elastic deformation amount of the respective elastic connection members, for example, 120d to 120e, reaches the corresponding gap amount. Wherein the traction friction mechanism F1 is modified to a multi-friction plate structure as shown in fig. 8 to 9, and the axial grooves 71 are also provided on the outer circumferential surface of the outer friction plate 154 at the same time.

It will be appreciated that the resilient coupling 120 of the present application acts like a resilient element in known resilient couplings. In fact, the specific structural form and connection mode of the elastic connecting element 120 can be fully used for reference to all technical solutions of known elastic couplings.

For example, the resilient connector 120 of the overrunning decoupler P14 shown in FIGS. 16-17 is embodied as an annular serpentine spring. The U-shaped bend on one axial side of the spring is embedded in the corresponding axial counter bore 31, and the U-shaped bend on the other axial side of the spring, which is positioned in the radial gap between the friction ring 70 and the belt ring 30, is hooked/wound/sleeved on the corresponding radial protrusion 33 on the inner circumferential surface of the belt ring 30. A corresponding group of radial protrusions 73 on the outer peripheral surface of the friction ring 70 axially extend into the circumferential gap of the serpentine spring wire from between two adjacent radial protrusions 33.

In this variant, the elastic connection 120 can easily have a variable spring rate simply by setting the circumferential clearance/degree of freedom between the radial projections, for example 73d, and the elastic connection 120 to be greater than zero. In addition, the belt loop 30 in the overrunning decoupler P14 could obviously be made of a non-metallic material, such as a wear-resistant plastic, to improve the wear and corrosion resistance of the belt grooves. Of course, belt loops 30 that do not withstand axial forces in other embodiments of the present application may do so, such as the belt loops 30 shown in FIGS. 3, 5-7, 9, 14, 20-21. Further, all the belt rings 30 may be a combined ring formed by casting a non-metal grooved outer ring and fixed to the outer circumferential surface of a metal inner ring, similar to that shown in fig. 20. For concrete fixing, reference may be made to the known techniques, such as the fixing schemes of lining layer, bush and sleeve in the sliding bearing, and the schemes disclosed in chinese patent documents CN202659848U, CN2275164Y, CN85201131U, CN1868702A, CN2061209U, CN101408193A and CN 104653751A. While the non-metallic material may be a thermoplastic of the PA46, PA66, PPS or PEEK series, for example.

For another example, the elastic connection member 120 is embodied as a set of cylindrical helical circumferential compression springs, so that the embodiment shown in fig. 1 can be modified into the overrunning decoupler P15 shown in fig. 18-19. Wherein the inner radial portions of the circumferential compression springs are disposed in the circumferential grooves 49 on the outer peripheral surface of the engagement hub 40, and the outer radial portions thereof are disposed in the axial type through grooves 64 of the guide ring 50 while interfering with the four circumferential inner end surfaces of the grooves. As mentioned above, the circumferential clearance/freedom between the resilient connecting element 120 and the through-going recess, e.g. 64c, is set to be greater than zero, which again easily has a variable spring rate.

Of course, the circumferential groove 49 in fig. 18 can also be modified to an axial groove, while the elastic connection 120 is embodied as an elastic rubber, the resulting modification also having a damping and shock-absorbing function. Further, the elastic connection member 120 may be embodied as a rubber sandwich having a complete ring shape as shown in fig. 20. Here, FIG. 20 shows crankshaft damped overrunning pulley P16, which may be considered a simple variation of overrunning pulley P6. Wherein the bearing 158 nests within the bore of the force limiting member 140 to accommodate the increase in radial dimension. A set of mounting holes 43 replace the threaded connection sections 42 in the engagement hub 40.

Similarly, following fig. 18, the splined coupling of fig. 20 may also be replaced by a resilient coupling 120 embodied as two sets of cylindrical helical circumferential compression springs arranged side by side, resulting in a crankshaft damped overrunning pulley P17 as shown in fig. 21. In order to reduce the interference of the outer peripheral surface of the extension arm 170 and the inner peripheral surface of the belt ring 30, at least one pair of axial holes are provided on the end surfaces of the extension arm 170 and the force limiting element 140 that are in contact with each other, and the axial pin 210 located therein fixes the two into a circumferential body. Here, the extension arm 170 also has the function of helping to achieve dynamic balance and is optimized to occupy the entire radial inlet space complementarily.

In addition, the crankshaft damping overrunning pulleys P16-P17, as well as all pulleys of the present application, may also have combined belt grooves to reliably transmit greater torque in a relatively smaller radial and axial space. The technical solutions disclosed in chinese patent documents CN102562860A and CN103527748A by the applicant and incorporated herein in their entireties can be referred to for illustration and description of the related structures, and the description of the present application is not repeated.

Of course, for the overrunning decouplers P12-P15 and the crankshaft damped overrunning pulleys P16-P17, the belt grooves of the belt ring 30 need only be modified into other force transmitting characteristic curves such as interference fit surfaces, gear teeth, keyways, pin holes, threads or a set of screw holes, which can be modified into overrunning clutches that reduce or attenuate torsional vibrations and/or engagement shocks.

Finally, it should be particularly noted that since the torque capacity/torque transmission capacity of the space-wedged overrunning clutch mechanism of the present application is at least several times that of the prior art under the same material and geometric conditions, the best way to eliminate or attenuate torsional vibrations and shocks in the front end train of the crankshaft of an automotive internal combustion engine should be to replace only the crankshaft pulley that is the source of the train drive with the crankshaft damped overrunning pulley of the present application, such as P16-P17, without the need for cumbersome and redundant setup of other pulleys that are the driven target one by one as overrunning pulleys. Compared with the prior art, the layout mode has the advantages that firstly, other driven belt pulleys do not need to be set into overrunning belt pulleys one by one, so that the torsion vibration reduction of the whole gear train can be realized at the lowest cost, the purpose of braking impact on the gear train generated when the internal combustion engine is rapidly decelerated is eliminated, secondly, the torque requirement can be met without increasing the size of the crankshaft belt pulley, thirdly, because all other belt pulleys do not need to contain an overrunning clutch mechanism, the radial sizes of all belt pulleys in the whole gear train can be further reduced, the overall quality of the gear train is further reduced, and finally, the whole gear train is more miniaturized and lightened.

The foregoing description and drawings represent only limited embodiments of the invention, with a certain degree of particularity, it should be understood that the embodiments and accompanying drawings are presented for purposes of illustration only and not limitation, and that various changes, equivalents, substitutions and alterations in component position or arrangement may be made therein without departing from the spirit and scope of the inventive concept.

Claims

1. A space-wedged overrunning pulley for reducing torsional vibration, comprising:

at least one traction friction mechanism which rotates around an axis and can be axially connected, wherein the traction friction mechanism comprises an intermediate ring and a friction ring which rotate around the axis and are provided with traction friction surfaces, and the traction friction surfaces of the intermediate ring and the friction ring are axially abutted to form at least one traction friction pair so as to transmit friction torque;

the rotary guide mechanism provides joint force for the traction friction mechanism and rotates around the axis, and is provided with a guide ring and an intermediate ring which rotate around the axis and are provided with corresponding guide surfaces, and the guide surfaces of the guide ring and the intermediate ring are axially abutted to form a guide friction pair; and

a force-transmitting friction mechanism which is at least non-rotatably coupled to each of the guide ring and the friction ring;

the lead angle lambda of the mutually conflicting parts of the guide friction pair is larger than zero and smaller than xi, namely lambda is more than 0 and less than xi, and xi is a small end point value of a value opening interval of the lead angle lambda, which can cause the guide friction pair and the traction friction pair not to be self-locked in the circumferential direction;

the method is characterized in that:

the belt ring with the belt groove type force transmission characteristic curved surface on the outer peripheral surface is at least non-rotatably connected with the guide ring or the friction ring; and

further comprising at least one ring-shaped member revolving around said axis, which ring-shaped member is non-rotatably connected to said guide ring or said friction ring by means of at least one elastic connection.

2. The overrunning pulley according to claim 1 wherein: the elastic connecting piece is at least one spiral spring, a serpentine spring, a linear spring or an annular rubber interlayer.

3. The overrunning pulley according to claim 2 wherein: the guide surfaces of both the guide ring and the intermediate ring are spiral tooth surfaces provided on one of the surfaces of both the guide ring and the intermediate ring, the surfaces including an end surface, an inner peripheral surface, and an outer peripheral surface, the surfaces facing each other; in the axial plane, the included angle between the spiral tooth surface and the axial line is larger than 0 degree and smaller than 180 degrees.

4. The overrunning pulley according to claim 3 wherein: the spiral tooth surfaces are respectively arranged on the inner circumferential surface and the outer circumferential surface of the guide ring and the intermediate ring which are directly opposite to each other, and the guide ring is provided with a flange type force limiting end part.

5. The overrunning pulley according to any one of claims 1 to 4, wherein: the traction friction surface is a combination of a plurality of inner and/or outer truncated conical surfaces formed by rotating a generatrix with a broken line shape on the cross section around the axis.

6. The overrunning pulley according to any one of claims 1 to 4, wherein:

the device also comprises at least one force limiting element for closing the axial force; and

at most one of the guide ring and the friction ring is a force-closing combined member comprising the force-limiting element at least by means of a non-rotatable connection to establish an axial force-closing interference connection with each other.

7. The overrunning pulley according to any one of claims 1 to 4, wherein: the traction friction mechanism is a multi-friction-plate friction mechanism, the number of the traction friction mechanism is at least one, and two groups of friction plates are axially staggered and are non-rotatably connected to the friction ring and the intermediate ring respectively.

8. The overrunning pulley according to any one of claims 1 to 4, wherein: the ring-shaped member is connected with the guide ring or the friction ring in a non-rotatable manner and is a rigid connection which is fixedly connected into a whole.

9. The overrunning pulley of claim 8 wherein: the rigid connection is an integral connection that is incorporated into one piece.

10. The overrunning pulley according to any one of claims 1 to 4, wherein: the friction ring is provided with at least one elastic element, and the elastic pretensioning mechanism is provided with at least one elastic element and is used for continuously establishing at least indirect friction connection between the intermediate ring and the friction ring.

11. The overrunning pulley according to any one of claims 1 to 4, wherein: the ring member is an engagement hub.

12. The overrunning pulley according to any one of claims 1 to 4, wherein: the ring-shaped member is combined with the belt ring into the same member.

13. The overrunning pulley according to any one of claims 1 to 4, wherein: the non-rotatable connection between the annular member and the guide ring or the friction ring is a movable connection that is axially relatively movable but not circumferentially relatively rotatable.

14. The overrunning pulley according to claim 6 wherein: the belt loop is non-rotatably connected or integrated in one piece with one of the guide loop, the friction loop and the force limiting element.

15. A spatial wedge type overrunning clutch capable of reducing torsional vibration is characterized in that: a pulley as claimed in any one of claims 1 to 4 in which the grooved force transmitting characteristic curve of the belt ring is replaced by an interference fit, gear teeth, key slots, pin holes, threads or a set of screw holes.