EP1969251A1 - Chaine articulee, notamment pour un systeme d'entrainement de vehicule - Google Patents

Chaine articulee, notamment pour un systeme d'entrainement de vehicule

Info

Publication number
EP1969251A1
EP1969251A1 EP06828564A EP06828564A EP1969251A1 EP 1969251 A1 EP1969251 A1 EP 1969251A1 EP 06828564 A EP06828564 A EP 06828564A EP 06828564 A EP06828564 A EP 06828564A EP 1969251 A1 EP1969251 A1 EP 1969251A1
Authority
EP
European Patent Office
Prior art keywords
region
contact
link
curvature
pieces
Prior art date
Legal status (The legal status 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 status listed.)
Withdrawn
Application number
EP06828564A
Other languages
German (de)
English (en)
Inventor
Marcus Junig
Anton Simonov
Olga Ispolatova
Michael Pichura
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Schaeffler Buehl Verwaltungs GmbH
LuK Lamellen und Kupplungsbau GmbH
Original Assignee
LuK Lamellen und Kupplungsbau Beteiligungs KG
LuK Lamellen und Kupplungsbau GmbH
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
Publication date
Application filed by LuK Lamellen und Kupplungsbau Beteiligungs KG, LuK Lamellen und Kupplungsbau GmbH filed Critical LuK Lamellen und Kupplungsbau Beteiligungs KG
Publication of EP1969251A1 publication Critical patent/EP1969251A1/fr
Withdrawn legal-status Critical Current

Links

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
    • F16G—BELTS, CABLES, OR ROPES, PREDOMINANTLY USED FOR DRIVING PURPOSES; CHAINS; FITTINGS PREDOMINANTLY USED THEREFOR
    • F16G13/00—Chains
    • F16G13/02—Driving-chains
    • F16G13/04—Toothed chains
    • 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
    • F16G—BELTS, CABLES, OR ROPES, PREDOMINANTLY USED FOR DRIVING PURPOSES; CHAINS; FITTINGS PREDOMINANTLY USED THEREFOR
    • F16G5/00—V-belts, i.e. belts of tapered cross-section
    • F16G5/16—V-belts, i.e. belts of tapered cross-section consisting of several parts
    • F16G5/18—V-belts, i.e. belts of tapered cross-section consisting of several parts in the form of links

Definitions

  • the present invention relates to a link chain for a particular vehicle drive, with a plurality of hingedly interconnected via pressure pieces link plates, the pressure pieces are transverse to the longitudinal direction of the link chain and are arranged in openings of the link plates and arranged on the pressure pieces and the link plates respective curved trained contact surfaces are along which abut the pressure pieces and link plates for power transmission to each other and arranged on the pressure pieces curved rolling surfaces are arranged along which roll the plungers for power transmission to each other and the plungers are formed asymmetrically in a running in the longitudinal direction of the link chain cross section in Druck demoeux and the contact surfaces on in Druck demoeuxeux upper and lower contact surface area between the pressure piece and link plate are provided.
  • a plate chain of the type described input can be used in a vehicle drive.
  • CVT continuously variable belt pulley transmission
  • the link chain is a toothed chain, which thus has teeth on at least one side, via which the tensile force is transmitted between the gears and the chain.
  • Such a link chain in the form of a toothed chain can be used for example in a transfer case of a four-wheel drive motor vehicle or for bridging axle spacings to a differential o- example, as a power transmission means in a power take-off or for an auxiliary unit of the motor vehicle.
  • the link chain is made up of a plurality of link plates together, which are hingedly connected to each other via the pressing pieces and the link plates can be arranged in the form of link packs such that several link plates adjacent to each other and juxtaposed by the pressure pieces are interspersed, so then results in a link chain, which can transmit large forces loaded on train.
  • Such a link chain has become known, for example, from US Pat. No. 5,651,746.
  • This known link chain has plungers that are used for power transmission to rolling surfaces abut each other.
  • the radius underlying these rolling surfaces is referred to as optimal within a division-dependent window. It should be achieved so that the known link chain during a preload suffers no remaining damage in the area of the rolling surfaces.
  • the present invention is an object of the invention to provide a link chain in which a more favorable force distribution in the area of the contact surfaces of the pressure pieces and the link plates is present and thus the described problem is eliminated.
  • the invention now provides a link chain for in particular a vehicle drive, with a plurality of hingedly interconnected via pressure pieces link plates, the pressure pieces are transverse to the longitudinal direction of the link chain and arranged in openings of the link plates and the pressure pieces and the link plates each curved trained contact surfaces are arranged, along which rest the pressure pieces and link plates for power transmission to each other and arranged on the pressure pieces curved Wälz vom along which the pressure pieces for power transmission to each other and the plungers are formed asymmetrically in a running in the longitudinal direction of the link chain cross-section in Druck demoeux and the contact surfaces are provided in Druck demoeuxnraum upper and lower contact surface area between pressure piece and link plate, wherein the pressure pieces in the de R rolling surfaces have at least two areas with different curvatures.
  • a link chain of the type in question has in the elongated load area a contact area between the pressure pieces, which differs from the contact area in case of buckling, so if the link chain on a sprocket or a pair of conical disks undergoes a direction reversal.
  • the present invention makes use of this finding advantageously and provides rolling surfaces with at least two regions with different curvatures.
  • the rolling movement of the plungers can be optimized each other by adjusting the curvatures in the area of the rolling surfaces, for example, with respect to a reduction of the surface pressure in the contact surface area of the rocker and the pieces according to a wear reduction at the contact points of the rocker.
  • the curvature is always the same, that is, for example, the radii of curvature of the two regions differ, but within a respective range of curvature radius is constant.
  • a curvature variable along the rolling surface is provided within at least one region.
  • at least two regions are provided with from region to region of another curvature, and in at least one of the regions, the curvature along the rolling surface can also change, that is to say be variable along the rolling surface, for example.
  • this also includes an embodiment of the rolling surfaces of the pressure elements extending along the entire rolling surface is variably designed and therefore determined, for example by means of a mathematical function as a generator.
  • the curvature is smaller in the region of the second contact region of two adjoining pressure pieces which adjusts in the straight lashing chain center during tensile loading than in the region of the first contact region of the adjacent pressure pieces which adjusts in the event of a kink.
  • the plate-link chain according to the invention runs between the two reversal points, which are formed, for example, by two gears or two pairs of conical disks in a conical-pulley transmission, then a contact area between the rocker pressure pieces below the imaginary center line described above occurs in the plate-link chain according to the invention, and the plate-link chain according to the invention now appears by the fact that in these In the second contact region, the curvature is smaller than in the contact region of the pressure pieces in the event of buckling, which lies above the above-imaginary center line. If now both regions are formed by radii which differ from one another, then the radius in the first, that is to say upper, contact region is smaller than in the second, lower contact region. Even if the rolling surfaces are formed with variable radius over the entire arc length of the rolling surface, it is provided according to the invention that the radius in the second contact region is greater than in the first contact region.
  • the curvature in the second contact region is chosen according to the invention so that the contact point or contact area between two adjacent pressure pieces in Druck- piece height direction is shifted in the direction of the pressure piece height center.
  • the curvature in the first, so upper contact area is selected so that the contact point or contact area between two adjacent pressure pieces in Druckzhoueuxeuxnraum is also shifted in the direction of the pressure piece height center. This ensures that the contact area for power transmission between the two rocker pressure pieces in the buckling case between the upper and lower contact surfaces of the rocker plates or link plates and thus on the one hand the Vercardne Trent the plungers in the opening of the link plates counteracted and on the other hand a more uniform force distribution between the upper and lower contact surfaces is achieved.
  • the ratio of the curvatures of the second contact region to the first contact region is in the range from about 0.25 to about 0.9, preferably 0.25 to about 0.83.
  • the curvature of the first contact region can be from about 1.2 times to about 10 times the curvature of the second contact region, the curvature of which in each case is smaller than the curvature of the first contact region.
  • a curvature ratio recognized as being advantageous lies in the range of approximately 0.5, that is to say the curvature of the second contact region is half the curvature of the first contact region and, in the case of a further In another advantageous embodiment, the ratio of the curvature of the second contact region to the curvature of the first contact region is approximately 7:16.
  • the curvature in the second contact region is chosen such that the force distribution which occurs in the region of the abutment surfaces of the pressure piece and the link plate counteracts a tendency of the rocking piece to be displaced in relation to the link plate.
  • the rolling surfaces of the rocker pressure pieces have at least two areas with different curvatures and each along the rolling surface on a certain arc length and it is provided according to the invention that the ratio of the arc lengths of the area with a smaller curvature, this is the second contact area to the area with greater curvature this is the first contact area, about 1 to 2.
  • the link chain can take a large bending angle in the direction reversal on a gear or a conical disk pair.
  • Fig. 1 is a plan view of a schematically illustrated rocker pressure piece according to an embodiment of a link chain according to the present invention
  • FIG. 2 shows a view of a weighing-pressure piece according to a modified embodiment of the plate-link chain
  • 3 shows a detail of a link chain according to the present invention
  • 4 is a plan view of a pressure piece pair of a link chain according to the present invention for explaining a displacement of a contact surface area.
  • Fig. 5 is a view similar to Fig. 4;
  • Fig. 6 in two views an explanation of the force distribution in the load case in a known link chain
  • Fig. 7 is a view similar to Figure 6 for explaining the force distribution in a link chain according to the present invention.
  • FIG. 8 is an illustration of a pressure piece pair for explaining the surface pressure distribution which occurs in the event of loading
  • Fig. 9 is an illustration for explaining geometric relationships.
  • Fig. 1 shows in a plan view a pressure piece 1 of a link chain 2 (Fig. 3) according to the present invention.
  • the pressure piece 1 is formed asymmetrically in pressure piece height direction, thus has in the upper region in the width direction (double arrow B) in the direction (arrow L) of the link chain 2 greater width extension.
  • this pressure piece 1 another pressure piece 13 is arranged opposite one another, so that both pressure pieces roll on a curved rolling surface 5 opposite each other.
  • the pressure piece 1 in this case has a first contact area 6, which then adjusts when the pressure piece 1 rolls together with the thrust piece 13 lying opposite him in case of buckling, said buckling case is shown for example in Fig. 3 of the drawing.
  • the rolling surface 5 of the pressure piece 1 also has a second contact area 7, on which the two pressure pieces roll off each other when the plate chain is exposed in the straight straps chaining a tensile load.
  • the dotted lines shown in Fig. 1 of the drawing in the first contact area represent the length of the radius starting from the center 8 shown in FIG. 9 of the drawing, from which the first contact area 6 is formed, this radius in Fig. 9 with Ri is designated. Similarly, the dotted lines shown in FIG.
  • Fig. 2 of the drawing shows a pressure piece 10 according to a modified embodiment of a plate chain, the rolling surface 11 over the entire arc length has a continuously changing radius, which in turn is shown in Fig. 2 with reference to the dotted lines 12, the envelope is shown in solid ,
  • Fig. 4 of the drawing shows a pressure piece pair in a plan view for explaining a shift of the contact point or contact surface area between the rocker pressure piece 1 and 13 from Pi to P r .
  • Pi is the contact area which would set in a known link chain and is shown for reference purposes
  • Pr is the contact surface area which occurs in the link chain according to the present invention, namely in the straight link chain center.
  • the contact surface area has been further displaced toward a die center M.
  • FIG. 5 shows a representation of the cradle pair having a pad area P 2 corresponding to the location of the pad area in a known link chain and drawn for reference purposes in the buckling case illustrated in Figure 3 of the drawing, while P 2 - Position of the contact surface area in the described load case of the plate-link chain according to the invention.
  • the contact surface area between the two pressure pieces 1, 13 has been moved in the direction of the Druckfeldeuxeuxeux M also in this load case.
  • FIGS. 6 and 7 of the drawings show in the left half of the drawing, the force distribution in the straight Laschenkettentrum a known link chain, wherein the impressed at point P 1 force F divides into acting on a lower contact surface 14 at point B force F 6 , which is greater than the acting on the upper contact surface 15 at point A force F A , so that due to the uneven force distribution indicated by the arrow 16 tendency of the pressure element 1 for twisting in the opening 3 of the link plate 4 is.
  • FIG. 6 of the drawing shows in the left half of the drawing, the force distribution in the straight Laschenkettentrum a known link chain, wherein the impressed at point P 1 force F divides into acting on a lower contact surface 14 at point B force F 6 , which is greater than the acting on the upper contact surface 15 at point A force F A , so that due to the uneven force distribution indicated by the arrow 16 tendency of the pressure element 1 for twisting in the opening 3 of the link plate 4 is.
  • FIG. 16 shows in the left half of the drawing, the force distribution in the
  • Fig. 7 shows in the left half of the drawing corresponding to the left half of the drawing in Fig. 6 load case on an inventively designed tab chain.
  • Fig. 7 shows in the right half of the drawing the right half of the drawing of FIG. 6 corresponding load case, wherein the displacement of the contact surface area P 2 to P 2 'in the direction of Druck Georgia Godnmitte the resulting reaction forces F A and F B are much less different in the right half of the drawing of FIG. 6, so that according to the corresponding component voltages in the link plate decrease accordingly and thus the risk of cracking in the link plate is reduced.
  • FIG. 8 of the drawing now shows a qualitative course of the surface pressure in the second contact region 7 of a pressure piece pair 1, 13 of a plate-link chain 2 according to the invention.
  • FIG. 9 of the drawing now shows that the centers 8, 9 of the radii which serve to form the first contact region 6 and the second contact region 7 are above a vertical straight line 17 which defines the connection path between the beginning 18 of the first contact region 6 and viewed at the beginning 19 of the second contact region 7 in each case viewed in the pressure piece height direction H outside, divides at the Lotmitte.
  • the longitudinal extension of the first contact region 6, that is to say the arc length along the rolling surface 5, has approximately twice the arc length of the rolling surface 5 in the region of the second contact region 7.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Devices For Conveying Motion By Means Of Endless Flexible Members (AREA)
  • Transmissions By Endless Flexible Members (AREA)

Abstract

L'invention concerne une chaîne articulée, notamment pour un système d'entraînement de véhicule, comprenant une pluralité d'éclisses (4) de chaîne reliées entre elles de manière articulée par le biais d'éléments de pression (1, 13). Les éléments de pression s'étendent transversalement par rapport au sens longitudinal de la chaîne articulée (2) et sont disposés dans des ouvertures (3) des éclisses de chaîne. Des surfaces d'appui (14, 15) de forme curviligne sont formées sur les éléments de pression et les éclisses de chaîne, surfaces le long desquelles les éléments de pression et les éclisses de chaîne reposent les uns contre les autres pour la transmission des forces. Des surfaces primitives de fonctionnement (5) de forme curviligne sont formées sur les éléments de pression, surfaces le long desquelles les éléments de pression roulent les uns sur les autres pour la transmission des forces. Les éléments de pression sont de forme asymétrique dans le sens (H) de la hauteur des éléments de pression dans une section transversale qui s'étend dans le sens longitudinal de la chaîne articulée. Les surfaces d'appui sont situées dans la zone des surfaces de contact supérieure et inférieure dans le sens de la hauteur des éléments de pression entre l'élément de pression et l'éclisse de chaîne, les éléments de pression présentant dans la zone des surfaces primitives de fonctionnement au moins deux zones (6, 7) ayant des courbures différentes.
EP06828564A 2005-12-24 2006-11-29 Chaine articulee, notamment pour un systeme d'entrainement de vehicule Withdrawn EP1969251A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102005062312 2005-12-24
PCT/DE2006/002103 WO2007073712A1 (fr) 2005-12-24 2006-11-29 Chaine articulee, notamment pour un systeme d'entrainement de vehicule

Publications (1)

Publication Number Publication Date
EP1969251A1 true EP1969251A1 (fr) 2008-09-17

Family

ID=37807991

Family Applications (1)

Application Number Title Priority Date Filing Date
EP06828564A Withdrawn EP1969251A1 (fr) 2005-12-24 2006-11-29 Chaine articulee, notamment pour un systeme d'entrainement de vehicule

Country Status (6)

Country Link
EP (1) EP1969251A1 (fr)
JP (1) JP5391442B2 (fr)
KR (1) KR20080077350A (fr)
CN (1) CN101346558B (fr)
DE (1) DE112006003375A5 (fr)
WO (1) WO2007073712A1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102016204024B4 (de) 2016-03-11 2018-02-01 Schaeffler Technologies AG & Co. KG Laschenkette
DE102018117404A1 (de) * 2018-07-18 2020-01-23 Schaeffler Technologies AG & Co. KG Laschenkette mit einem eine hervorstehende Nase als Anlagepunkt ausbildenden Sicherungselement sowie ein Verfahren zur Herstellung einer Laschenkette

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4010656A (en) * 1974-02-07 1977-03-08 Borg-Warner Corporation Power transmission drive
JP2616959B2 (ja) * 1988-05-17 1997-06-04 アイシン・エィ・ダブリュ株式会社 伝動用無端ベルト
JPH0632515Y2 (ja) * 1989-05-26 1994-08-24 株式会社椿本チエイン 摩擦伝動用チェーン
JPH051747A (ja) * 1991-06-25 1993-01-08 Nissan Motor Co Ltd 伝動ベルト
US5651746B1 (en) * 1994-08-29 2000-01-04 Borg Warner Automotive Kk Power transmission chain
NL1000294C2 (nl) * 1995-05-03 1996-11-05 Gear Chain Ind Bv Transmissieketting voor een kegeldrijfwerk.

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2007073712A1 *

Also Published As

Publication number Publication date
WO2007073712A1 (fr) 2007-07-05
CN101346558B (zh) 2012-06-27
JP5391442B2 (ja) 2014-01-15
CN101346558A (zh) 2009-01-14
JP2009521647A (ja) 2009-06-04
DE112006003375A5 (de) 2008-09-11
KR20080077350A (ko) 2008-08-22

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