WO2008067979A2 - Assemblage de composants sans cliquetis - Google Patents

Assemblage de composants sans cliquetis Download PDF

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Publication number
WO2008067979A2
WO2008067979A2 PCT/EP2007/010503 EP2007010503W WO2008067979A2 WO 2008067979 A2 WO2008067979 A2 WO 2008067979A2 EP 2007010503 W EP2007010503 W EP 2007010503W WO 2008067979 A2 WO2008067979 A2 WO 2008067979A2
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WO
WIPO (PCT)
Prior art keywords
component
transmission means
power transmission
force
pairing according
Prior art date
Application number
PCT/EP2007/010503
Other languages
German (de)
English (en)
Other versions
WO2008067979A3 (fr
Inventor
Claus-Hermann Lang
Original Assignee
Getrag Getriebe- Und Zahnradfabrik Hermann Hagenmeyer Gmbh & Cie Kg
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
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Application filed by Getrag Getriebe- Und Zahnradfabrik Hermann Hagenmeyer Gmbh & Cie Kg filed Critical Getrag Getriebe- Und Zahnradfabrik Hermann Hagenmeyer Gmbh & Cie Kg
Publication of WO2008067979A2 publication Critical patent/WO2008067979A2/fr
Publication of WO2008067979A3 publication Critical patent/WO2008067979A3/fr

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Classifications

    • 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
    • F16H—GEARING
    • F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
    • F16H55/02—Toothed members; Worms
    • F16H55/17—Toothed wheels
    • F16H55/18—Special devices for taking up backlash
    • 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
    • F16H—GEARING
    • F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
    • F16H55/02—Toothed members; Worms
    • F16H55/14—Construction providing resilience or vibration-damping
    • 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
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/0006—Vibration-damping or noise reducing means specially adapted for gearings

Definitions

  • the present invention relates to a mechanical component pairing with a drive component, which has a first toothing, and a driven component, which has a second toothing, wherein the first and the second toothing mesh with each other, wherein the drive member, the driven component in at least one predetermined Driving direction drives, and wherein means are provided to reduce noise caused by play between the two gears in the drive direction.
  • a mechanical component pairing is well known. An overview of the currently available means for reducing noise are described in "Losteilgehoffsche vonffygetrieben 11 by Claus H. Lang, University of Stuttgart, 1997.
  • active external gear measures can be provided, which decouple, for example, the disturbance excitation from an internal combustion engine by a dual mass flywheel.
  • dual-mass flywheels are expensive in terms of the claimed installation space, the necessary additional weight and in terms of costs.
  • passive external gear measures such as encapsulation or insulation of the gear housing. These measures are unfavorable.
  • active internal gear measures are known, which are arranged specifically to the main noise sources. Such active in-gear measures often aim to minimize game-related games or hinder agility within the free-flight within these functional games. The disadvantage here often the reduced efficiency and the generation of other unwanted noise (such as howling).
  • noise reduction passive internal gear measures that are located directly on the noise sources (ie, for example, the gears) and erase or isolate mechanical vibrations.
  • Well-known measures include idler brakes, measures to Zahnlückenverspan- tion, measures in which a disc is used with a slightly different ratio, measures with a friction wheel Mauübere, vibration absorber, magnetic solutions to prevent disengagement of the tooth flanks from each other, etc.
  • the document DE 10 2004 008171 Al discloses a spur gear drive for camshafts, in which a gear is formed in two parts.
  • the noise reduction means comprise first power transmission means fixed to one of the two components and second power transmission means fixed to the other component, the first and second power transmission means being external to the gears engaged with each other stand that between them acting against the predetermined drive direction elastic Abfederungskraft is transferable.
  • the pairing of components according to the invention makes it possible to transmit an elastic damping force, also referred to as a type of damping force, outside the teeth.
  • an elastic damping force also referred to as a type of damping force
  • This makes it possible to match the first and the second force-transmitting means to one another in such a way that they essentially engage and transmit an elastic cushioning force counter to the predetermined drive direction, if that makes sense.
  • the force transmission means may be adjusted to one another such that they normally do not engage or substantially disengage, but then, when a noise threatens to develop, dampen the relative movements of the components involved.
  • to be engaged is understood to mean that the force-transmitting means actually touch, so that the cushioning force acts directly between the components as soon as a relative movement commences between them.
  • the power transmission means are generally not in contact with drive in the drive direction, so that the Abfederungskraft comes into play only when the components have already completed a certain relative movement.
  • noise reduction means are realized by a few additional components, which also have a low weight.
  • the noise reduction means can generally replace the function of a dual mass flywheel, so that significant cost and weight savings can be realized.
  • a component is to be understood as meaning any type of component which has a toothing, that is to say in particular gears.
  • a particularly typical application are components with a face gear, but the invention is also on Component pairings in the form of bevel gear wheels, on racks, on planetary gear sets, splines, etc. applicable.
  • first and the second power transmission means are designed to transmit the elastic suspension force in a form-fitting manner.
  • the noise reduction means only act when a certain amplitude of the interference excitations is achieved.
  • the overall efficiency can be improved.
  • the first and / or the second power transmission means are formed elastically deformable. This leads to good elastic cushioning properties.
  • the components with the teeth can be constructed essentially unchanged compared to solutions that do not have noise-reducing measures.
  • the first and / or the second force transmission means have a convex contour.
  • the first power transmission means have a first plurality of nubs, which are provided laterally on one of the two components.
  • knobs can be realized structurally simple. You can either be connected to the associated component, for example by any joining techniques. However, it is also possible to provide the knobs on a separate component, which is then connected to the associated component.
  • nubs extend from a side surface of the associated component.
  • the nubs thus have an extension in the axial direction and thus the ability to transmit a force against them in the drive direction (in gears in the tangential or circumferential direction).
  • studs are formed dome-shaped or frustoconical.
  • the nubs can also be designed as a sharpened elevation.
  • the second power transmission means comprise a second plurality of power transmission members provided laterally on the other of the two components.
  • the power transmission members may in turn be separate components mounted on the associated gear.
  • the transmission members may also be part of an additional component (eg, a ring) attached to the associated component.
  • the second force transmission members are formed on a power transmission, which is fixed to the associated component.
  • the second force transmission members each extend in the radial direction outwards into a region between two teeth of the toothing of the associated component.
  • the second power transmission members are arranged laterally next to, ie outside the toothing.
  • the second force transmission members protrude into an area laterally adjacent to a tooth space. In this way it is structurally relatively easy to come into contact with the first power transmission members, which are fixed laterally to the other component, preferably in the region of the respective teeth of the other component.
  • At least some of the second power transmission members for transmitting power to the first power transmission means have a transmission surface that is skewed with respect to a side surface of the associated component.
  • the first power transmission means could be designed as axially projecting cylinder (instead of nubs).
  • the second power transmission means are then preferably designed to be completely elastic so that the functional game can be completely absorbed by elastic deformation.
  • the preferred oblique embodiment has the advantage that the transmission of the damping force can be done with the least possible amount of frictional force and the elastic deformation path of the second power transmission means can be kept relatively small. As a result, it is possible to use comparatively inexpensive materials.
  • the second force transmission members are designed as lamellae, which protrude radially relative to a base body.
  • the main body may be, for example, a ring or the like.
  • the force transmission members are formed as sections, in particular as peripheral portions of a power transmission ring.
  • the portions formed as power transmission members may be formed on the power transmission ring as inclined portions, a sawtooth-profile type or the like.
  • first plurality of the first power transmission members and the second plurality of the second power transmission members are different.
  • the number of first and second power transmission members is the same.
  • the number of first and / or second power transmission members need not necessarily be equal to the number of teeth of the respective associated gears.
  • at least one pair of first and second force transmission members is preferably in engagement or in a position which enables engagement for transmitting the elastic cushioning force.
  • first and / or the second plurality of the first and second force transmission members is equal to the number of teeth of the toothing of the respective associated component.
  • the first and the second power transmission means are formed so that a transmission of the elastic Abfederungskraft substantially takes place when the driven member from a pull flank of the drive member dissolves.
  • This embodiment makes it possible for the noise reducing means to be effective only when jamming occurs.
  • the first and the second power transmission means are each arranged on a side surface of the associated component, in the case of a gear so for example on an axial end face of the respective gear.
  • first and the second force-transmitting means are designed such that they come into rolling contact with each other during drive in the predetermined drive direction.
  • the power transmission means are configured to roll against each other, thus not generating high frictional forces therebetween.
  • the force transferring means are configured to frictionally transfer the resilient cushioning force.
  • Such a frictional, in particular purely frictional transmission requires that the first and the second power transmission means are constantly biased against each other, so that it is expected that the efficiency is slightly lower than in the preferred alternative embodiment.
  • first and the second power transmission means radially engage in the region of the meshing engagement with each other to transmit the elastic Abfederungskraft.
  • the engagement takes place at the height of the pitch circle, so that relative movements of the force transmission means in the tangential and / or radial direction are largely excluded while they are engaged with each other.
  • the components are helical components, wherein the driven component undergoes an axial displacement force when driven in the predetermined drive direction.
  • the noise reducing means are adapted to transmit an axial elastic suspension force acting in the opposite direction as the axial displacement force.
  • This embodiment is considered independent of the provision of noise reduction means for elastic cushioning of relative circumferential movements or Tangen tialmonyen between the two components as a separate invention. Because in this embodiment, noise can be effectively reduced or damped, which could be caused due to axial vibrations.
  • the noise reduction means are designed to limit the axial play that is usually present.
  • the power transmission means are permanently engaged and thus resiliently deflect movements of the driven gear in the direction of the axial displacement force.
  • the power transmission means can each be firmly connected to the respective associated component.
  • the first and / or the second power transmission means are adjustably fixed thereto in the drive direction and / or in the axial direction.
  • a strain of the power transmission means in relation to the respective associated component is conceivable.
  • the adjustment in the axial direction can be done for example by suitable washers.
  • the proposed measures are active internal gear measures with a small number of additional components, ideally only a single component (for example, a wheel with molded-on second power transmission means).
  • the noise reducing means according to the invention should not act substantially. Therefore, in the ideal case, no power losses, signs of wear, impaired switchability or other additional noise.
  • one of the main causes is the excitation of the mechanical system by the amplitude of the angular acceleration of the drive component.
  • These vibrations increase more and more, for example through optimization of Combustion processes of a driving internal combustion engine, by lightweight construction, etc.
  • the result is vibrations of loose parts, such as gears and gear blocks, within their function-related games.
  • shock effects At sufficiently large excitation amplitudes, there are shock effects at the game boundaries. These shock effects result in primary and secondary airborne sound pressures, which are acoustically perceived as rattles or rattles. If these games are minimized, these sounds can also be minimized, ideally even completely.
  • the basic idea of the solutions according to the invention is to compensate the rotational flank and / or axial play either completely or partially by means provided laterally on the components. This will be avoided by this "by-pass" system possibly occurring shocks on the thrust edges of the drive component and relocated to this by-pass system.
  • the clearance between the by-pass system and the engaged driven member is either zero or nearly zero, in any case many times smaller than the functional rotational backlash normally associated with these gears. This means that impact energies that occur are either zero or so low that rattling or rattle noises are no longer perceptible.
  • Means for noise reduction can be realized by simple components, for example by Kaltumformbare elastic solid state components that can be mass produced. Therefore, the cost can be set very low.
  • the noise reduction means are also very reliable, since they usually do not work permanently and come only with a sufficiently high disturbance excitation elastic cushioning effect. Furthermore, no or only slight relative movements between the first and the second force transmission members take place, so that the contacts, for example, by touching spherical or convex contours on the Wälz Vietnamese bemesser, ideally punctiform take place (ideally in the form of WälzANDen). The possibly resulting contacts lead ideally to purely elastic deformations. It is understood that the corresponding components must be designed for this purpose.
  • the components used to implement the noise reduction means may be made of metal or plastic or in a sandwich construction, for example with elastomeric interlayers, with these materials. Possibly occurring impact effects can then be prevented by impedance changes in the components of their structure-borne sound propagation.
  • the present invention can be applied to mutually movable components, such as gear pairs.
  • the invention can also be applied to non-mutually movable component pairings, for example, coupling splines (Keilnutvertechnik, etc.), or claw toothing.
  • the noise reducing means according to the invention also act in the static case and in components that oscillate around the zero position.
  • the power transmission means preferably engage with each other in the range of the pitch circle radius, it is also possible to realize this at a smaller or larger radius depending on the application.
  • Fig. 1 is a side view of a mechanical component pairing according to a
  • Fig. 2 is a perspective view obliquely from the side to illustrate the realized in the component pairing of Figure 1 noise reduction means.
  • Fig. 3 is a schematic representation of a component pairing in the form of a
  • FIG. 4 shows a schematic representation corresponding to FIG. 3 of a further mechanical component pairing according to the present invention, the general mode of operation of which corresponds to the component pairing of FIGS. 1 and 2;
  • Fig. 5 is an illustration of first and second power transmission members of
  • Noise reduction means of a component pairing according to the invention wherein the surfaces of the force transmission members are each formed convex to realize a point or line contact;
  • Fig. 6 is a representation corresponding to Figure 5, wherein a force transmission member has a convex and the other a straight surface.
  • Fig. 7 is a representation corresponding to Figure 6, in which the convex surface and the straight surface are interchanged.
  • FIG. 8 a of FIG. 4 corresponding representation of a component pairing with
  • FIG. 10 is a detailed perspective view of the component pairing of FIG. 9 for
  • FIG. 11 shows a representation corresponding to FIG. 9 of a further component pairing according to the invention, which has force transmission means for frictionally transmitting an elastic cushioning force;
  • FIG. 12 is a detailed view of the component pairing of FIG. 11 to illustrate the
  • a first embodiment of a component pairing according to the invention in the form of a gear pair of two helical gears in Stirnradbauweise is generally designated by IO.
  • the gear pair 10 has a driven gear in the form of a loose wheel 12 which is rotatably mounted on a shaft (not shown). Further, the gear pair 10 has a drive member in the form of a fixed wheel 14 which is fixed to a further shaft, not shown.
  • the idler gear 12 has a toothing 16 in the form of a spur gear toothing.
  • the fixed gear 14 has a corresponding toothing 18.
  • An axis of rotation of the idler gear 12 is shown at 20.
  • An axis of rotation of the fixed wheel 14 is shown at 22.
  • the axes 20, 22 are connected by a connecting line 24.
  • gears 16, 18 engage a pitch circle, with a pitch circle tangent at 26 being oriented perpendicular to the connection line 24.
  • the gear pair 10 has noise reducing means, generally indicated at 30.
  • the noise reduction means 30 include first power transmission means 32 and second power transmission means 34.
  • the first power transmission means 32 are fixed to the idler gear 12 and are formed as a plurality of nubs, which protrude axially relative to a side surface of the idler gear 12, as can also be seen in Fig. 2.
  • the shape of the knobs is approximately hemispherical, whose central axis coincides with the pitch circle of the idler gear 12.
  • the nubs 32 are each provided laterally on a tooth of the toothing 16. The number of nubs 32 thus corresponds to the number of teeth of the toothing 16th
  • the second power transmission means 34 are formed by a plurality of power transmission members, which are formed in the present case as fins 34.
  • the fins 34 protrude radially outwards relative to a lamellar ring 36.
  • the lamellar ring 36 is fixed to the side of the fixed wheel 14.
  • the fixed gear 14 has for this purpose a plurality of holes in the form of threaded holes 44.
  • the lamellar ring 36 has a plurality of recesses 38, which are formed as extending in the circumferential direction slots.
  • the lamellar ring 36 is fixed by means of a corresponding plurality of screws 40 to the fixed gear 14, wherein the relative position in the circumferential direction between the fixed gear 14 and the lamellar ring 36 through the slot configuration of the recesses 38 is adjustable.
  • An axial adjustment can be realized, for example, by inserting a washer of suitable thickness between the fixed gear 14 and the laminar ring 36.
  • the lamellar ring 36 is attached to the fixed gear 14 so that the lamellae extend in the radial direction thereof, in such a way that they pass in the radial direction at the respective tooth gaps of the toothing 18.
  • the fixed wheel 14 is driven in a drive direction 42.
  • the drive direction 42 is a preferred drive direction, as it is predetermined for example in motor vehicle transmissions (the direction when driving forward).
  • the gear pair 10 can be used both in vehicle stepped gears, in particular gears in countershaft design.
  • the gear pair 10 can also be used in a transmission for the drive of ancillaries such as engine timing gearboxes, to give another example.
  • the lamellae 34 of the lamellar ring 36 are on the one hand bent out of the radial plane something, in the direction of the fixed gear 14 away, as can be seen in particular in Fig. 2. Furthermore, the lamellae are each rotated about a radial axis, so that the faces pointing towards the fixed wheel 14 are formed as oblique transfer surfaces 52.
  • the surface of the first power transmission means in the form of the knobs 32 is designated 54 in FIG.
  • the type of engagement between the power transmission means 32, 34 is such that substantially a point-like contact between each of a blade 34 and a knob 32 is realized, wherein due to the inclination of the blade 34 a normal to the contact point obliquely to both the axial direction and the Oriented circumferential direction.
  • This standard is shown as an action line 46 in FIG.
  • the lamellar ring 36 is adjusted with respect to the fixed wheel 14 or with respect to the nubs 32 of the idler gear 12 so that when the fixed gear 14 drives the idler gear 12, essentially no or only a very small force is transmitted between the power transmission means 32, 34. If the idler gear 12 is released from the traction flank of the fixed gear 14 from such a state, a force is transmitted via the force transmission means 32, 34 along the line of action 46.
  • the transmitted force can be broken down into an axial force 48 which runs parallel to the axes 20, 22, and into a tangential force 50.
  • the tangential force 50 is directed counter to the driving force in the predetermined drive direction 42.
  • a force or movement of the idler gear 12 is attenuated away from the trailing edge of the fixed wheel 14 by the power transmission means 32, 34, by means of the tangential force 50 transmitted thereto, which counteracts the driving force.
  • a trailing edge of the teeth 18 of the fixed wheel 14 is shown in Fig. 2 at 58.
  • the opposite edge of the same tooth is formed as a trailing edge 56, which is also indicated schematically in Fig. 2.
  • FIG. 3 shows a further embodiment of a component pairing 10 'according to the invention and the component pairing 10' generally corresponds in terms of structure and mode of operation to the component pairing 10 of FIGS. 1 and 2. Only differences will be explained below.
  • FIG. 3 corresponds to a section through the rolling circle plane, which is designated in Fig. 1 with 26.
  • noise reducing means 30 ' are shown.
  • the noise reduction means 30 ' have first power transmission means 32' associated with the teeth 16 'and second power transmission means 34' associated with the teeth 18 '.
  • the power transmission means 32 ', 34' have unspecified elastic means (shown schematically by a spring) through which a damping force 50 'in the circumferential direction (counter to the drive direction 42') can be applied between the teeth 16 ', 18'.
  • the noise reduction means 30 ' are realized as a kind of "by-pass" system, which acts outside of the teeth 16', 18 'and can transmit a damping force against the drive direction.
  • FIG. 4 shows a further embodiment of a component pairing 10 "according to the invention.
  • the component pairing 10 corresponds in terms of structure and mode of operation of the component pairing 10 of FIGS. 1 and 2. In the following, only differences are discussed.
  • the representation of the component pairing 10 “corresponds to the representation of the component pairing 10 'of FIG. 3, that is in the form of a section through a Wälzniktangente.
  • louvers 34 are oriented obliquely with respect to both the axial and radial directions, and accordingly, an obliquely directed force is transferable along an action line 46" between the power transmission means 32 ", 34".
  • a force component 50 "acting in the circumferential direction counteracts the drive direction 42" in order to achieve the cushioning or damping effect according to the invention in circumferential or tangential direction.
  • An axial force component 48 "dampens movements of the idler gear 14" in the axial direction or rebounds them.
  • the first power transmission means are generally formed as approximately spherical or dome-shaped or truncated cone-shaped nubs and preferably provided with a convex surface.
  • the second force transmission means 34 in the form of the lamellae essentially have a flat transmission surface 52. It is also possible to form the mutually contacting surfaces 52, 54 both convex, as shown in Fig. 5.
  • the situation of the embodiments of FIGS. 1 to 4 with a convex transfer surface 54 of the knobs 32 is shown in FIG.
  • An inverted embodiment in which the nubs have a straight surface 54 and the fins have a convex surface 52 is shown in FIG.
  • the surface pairing 52, 54 may also be convex-concave with identical or preferably different curvature.
  • Fig. 8 an embodiment corresponding to FIG. 4 is shown, wherein the teeth 16 "', 18'" are designed as helical gears.
  • the idler gear 14 '' is usually supported on an unspecified axial bearing (which could be seen on the right-hand side in Figure 8).
  • the noise-reduction means 30 '' are arranged on the same side.
  • An unspecified in Fig. 8 axial force 48 thus acts in the opposite direction as the Axialversatzkraft 62. Accordingly, it is achieved that movements of the idler gear 12 '"in the direction of Axialversatzkraft 62 by means of the noise reduction means 30'" can be attenuated.
  • FIGS. 9 and 10 show a further alternative embodiment of a component pairing 10 Iv according to the invention .
  • the component pairing 10 TM generally corresponds to the component pairing 10 of FIGS. 1 and 2. In the following, only differences will be discussed. Identical elements are provided with the same reference numerals.
  • the second power transmission means 34 1V have a power transmission ring, which is fixed to the fixed gear 14 i ⁇ and completely covers the nubs 32 TM in the radial direction.
  • a plurality of force transmission elements 34 IV are in the form of inclined sections. provided.
  • These force transmission members 34 TM each have transmission surfaces 52 IV , which generally correspond in shape and orientation to the transmission surfaces 52 of the fins 34 of FIGS. 1 and 2.
  • the force transmission sections 34 TM in the axial direction are generally not as elastic as the lamellae 34 of the lamellar ring 36 of FIGS. 1 and 2. Accordingly, can be with the embodiment of Figs. 9 and 10 generally a stronger damping effect produce.
  • the power transmission ring 36 IV in the circumferential direction with respect to the associated gear (here the fixed gear 14 IV ) is biased and biased in one direction, as shown schematically in Fig. 9 at 64.
  • the biasing means schematically illustrated would exert a force 66 on the power transmission ring 36 ⁇ v , as shown in Fig. 10 at 66.
  • the biasing force 66 would be opposite to the drive direction 42 IV aligned.
  • FIGS. 11 and 12 show a further embodiment of a component pairing 10 v according to the invention.
  • the component pairing 10 v corresponds in terms of structure and mode of operation of the component pairing 10 of FIGS. 1 and 2. Only differences will be explained below.
  • the first power transmission means 32 V is in the form of an annular disk and the second power transmission means 36 V is generally in friction contact each other without a force component in the circumferential direction could be transferred form-fitting manner between them.
  • the discs 32 V , 36 V are rather biased toward one another in the direction of their connection line 24 (not shown in FIG. 11, 12), so that due to the frictional engagement a damping force 50 V against the drive direction 42 V is frictionally transferable.
  • the biasing means 64 of FIGS. 9, 10 are generally applicable to the other embodiments of component pairings as well. Furthermore, it is understood that not only a component in the circumferential direction (50) can be transferred, but also a component in the axial direction (not shown in greater detail in FIG. 12) in the frictional or non-positive transmission of a damping force. that the power transmission pulley 36 V, the power transmission wheel covers 32 V in the radial direction somewhat.
  • the contact surfaces of the force transfer rings 36 V, 32 V obliquely v aligned both with respect to the axial direction and also in respect to the radial direction of the component pairing 10, as Fig. 12 can be seen.
  • first power transmission means eg knobs
  • second power transmission means eg disks
  • first and second power transmission means constructively identical or complementary to each other.
  • first and second power transmission means not only on one side of the components, but for example on both sides of these components. This may also involve the mating of the power transmission means on the opposite sides of the components crosswise exchange. In Kraftübertragungsstoffcrustation on both sides of a larger tangential force can be generated against the drive direction, and thus a better reduction of the rattle or rattle.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Gear Transmission (AREA)
  • Retarders (AREA)
  • Gears, Cams (AREA)
  • Lock And Its Accessories (AREA)

Abstract

L'invention concerne un assemblage mécanique de composants (10, 12, 14), comportant un composant d'entraînement (12) présentant une première denture (16), et un composant entraîné (14) présentant une deuxième denture (18), la première et la deuxième denture (16, 18) se trouvant en engrènement. Le composant d'entraînement (12) entraîne le composant entraîné (14) dans au moins un sens d'entraînement prédéfini (42). L'assemblage mécanique selon l'invention comporte également des éléments (30) destinés à réduire les bruits provoqués par un jeu (60) entre les deux dentures (16, 18) dans la direction d'entraînement (42). Ces éléments de réduction de bruit (30) comportent de premiers éléments de transmission de force (32) fixés sur l'un des composants (12), et de deuxièmes éléments de transmission de force (34) fixés sur l'autre composant (14), les premiers et deuxièmes éléments de transmission de force (32, 34) s'encastrant en dehors des dentures (16, 18), de telle manière qu'une force d'amortissement élastique (50) agissant contre le sens d'entraînement prédéfini peut être transmise entre lesdits éléments de transmission de force.
PCT/EP2007/010503 2006-12-07 2007-12-04 Assemblage de composants sans cliquetis WO2008067979A2 (fr)

Applications Claiming Priority (2)

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DE200610058868 DE102006058868B4 (de) 2006-12-07 2006-12-07 Rasselfreie Bauteilpaarung
DE102006058868.1 2006-12-07

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WO2008067979A2 true WO2008067979A2 (fr) 2008-06-12
WO2008067979A3 WO2008067979A3 (fr) 2008-08-14

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DE102009031240A1 (de) 2009-07-01 2011-01-05 Schaeffler Technologies Gmbh & Co. Kg Getriebliche Verbindung
DE102013021824A1 (de) * 2013-12-21 2015-06-25 Valeo Schalter Und Sensoren Gmbh Sensorvorrichtung zum Erfassen eines Positionswinkels eines drehbaren Bauteils eines Kraftfahrzeugs und Kraftfahrzeug

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WO2008067979A3 (fr) 2008-08-14
DE102006058868B4 (de) 2008-10-16

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