WO2009033901A2 - Dispositif et procédé de réduction du bruit de cliquetis dans une transmission par engrenages - Google Patents

Dispositif et procédé de réduction du bruit de cliquetis dans une transmission par engrenages Download PDF

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Publication number
WO2009033901A2
WO2009033901A2 PCT/EP2008/060446 EP2008060446W WO2009033901A2 WO 2009033901 A2 WO2009033901 A2 WO 2009033901A2 EP 2008060446 W EP2008060446 W EP 2008060446W WO 2009033901 A2 WO2009033901 A2 WO 2009033901A2
Authority
WO
WIPO (PCT)
Prior art keywords
gear
spring element
teeth
rattle noise
driven gear
Prior art date
Application number
PCT/EP2008/060446
Other languages
German (de)
English (en)
Other versions
WO2009033901A3 (fr
Inventor
Luiz Carlos Proenca
Juliano Sanches
Claudemir Abreu
Original Assignee
Zf Friedrichshafen Ag
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 Zf Friedrichshafen Ag filed Critical Zf Friedrichshafen Ag
Publication of WO2009033901A2 publication Critical patent/WO2009033901A2/fr
Publication of WO2009033901A3 publication Critical patent/WO2009033901A3/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
    • F16H55/17—Toothed wheels
    • F16H55/18—Special devices for taking up backlash
    • F16H2055/185—Special devices for taking up backlash using compound gears with coincident teeth of different material, e.g. laminated construction of metal and elastomeric gear layers, where elastic layer is slightly oversized

Definitions

  • the present invention relates to a device for reducing race noise in a gear transmission according to the preamble of claim 1.
  • the weather relates to a method for reducing race noise in a gear transmission
  • Rattling and rattling noises are caused by vibrations of unloaded gears and circuit parts within their funktio ⁇ s- and production-related game and are usually caused by torsional vibrations of Getriebewelien.
  • the amplitude of the torsional vibrations exceeds a threshold, the non-switched idler gears of the transmission from their trailing edge and oscillate back and forth within the backlash, the amplitude of the torsional vibrations of the moment of inertia of the idler gear and the idler wheel retarding acting drag torque depends;
  • the shocks when hitting the loose parts at the game limits are the cause of the resulting noise, which can occur both in the Neutraisteiiung the transmission and while driving.
  • the torsional vibrations of transmission gears are caused by the irregularity of the engine speed due to the periodic combustion process, the consumption and emission reduction measures increasing the nonuniformity of the engine speed curve.
  • the vibrations of the gears are transmitted directly or via bearings as WhyschalS on the shafts of the transmission, the majority being transmitted via the shaft bearings to the housing, where the vibrations often disadvantageously amplified due to resonance effects become.
  • From the gearbox part of the vibrations is directly as Luttschal! radiated, with another part as WhyschaSI on the transmission suspensions to the body niegeieitet.
  • Another way to reduce the rattle noise is to use two-mass flywheels; These are usually used in luxury vehicles or in vehicles with very high noise levels.
  • the oscillation frequency is shifted to be in an unused area; Usually wins the vibration frequency below the teerlauffitzah ) of the vehicle engine.
  • the use of dual-mass flywheels results in a significant cost increase.
  • the resonance that occurs can result in damage to the two-mass flywheels.
  • Another problem can arise in sporty driving; In this case, the masses can collide during a quick clutch actuation, resulting in a very high torque peak.
  • each of the associated wheels are repelled from each other by magnetic force
  • the magnetic or magnetized material is provided in a disc which rests firmly on the front side of each of the gears and the discs a constant over the circumference having aligned axial polarization.
  • each gear a butt! facing away and the other pole turned away; Polenen Poland on a gear are the same poles on the other gear opposite.
  • DE 4426325 A1 discloses an anti-rattle device for a pair of intermeshing teeth in a transmission, between which there is a clearance in which an elastomeric material on one of the gears is in contact with teeth of the other gear, the elastomeric Material is arranged radially on the one gear, that the outer diameter is greater than the réelle Vietnamese bemesser of the gear provided therewith.
  • the one gear has on one end face a recess into which the egg-elastic material is arranged as a ring or disc.
  • DE 19913563 C1 Within the scope of DE 19913563 C1 is an anti-rattle tooth lock washer ⁇ be written, which is intended in particular for a motor vehicle transmission, having an outer diameter corresponding to an associated gear, and with a deviating from the gear Zahnanzah !.
  • the known anti-rattle toothed disc has a hard-magnetic material which is arranged annularly, the hard-magnetic material being assigned a container component having a soft-magnetic material, in which the hard-magnetic material is arranged and which is embedded in a core material of the anti-rattle toothed disc ,
  • a biased spring element is provided to the drive gear pair and the driven gear pair a spring to transfer torque for the suppression of gear noise, wherein the spring torque is greater than the moment of inertia of the drive or the output gear pair, this construction requires a high manufacturing and assembly costs; Furthermore, the weight and the required installation space are disadvantageously increased by the additional shaft, which does not serve the torque transfer.
  • DE 10328482 A1 describes a gear transmission comprising an anti-rattle device, which comprises a first gearwheel rotatable about a first axis, a second gearwheel, which is rotatable at a predetermined distance from the first axis and meshing with the first gearwheel, and which is non-rotatably connected to the first gearwheel Reiburnfangs constitutional and a rotatably connected to the second gear Reibfusessf contains, wherein the Reibfusess vom and the transferability of a friction torque are in mutual contact.
  • the one Reibfusessf is biased in the axial direction; Preferably, this Reibfusessf is formed on the outer periphery of a plate spring washer.
  • a device for the automatic elimination of backlash in gear drives known. It includes a first and a second gear, which are respectively disposed on each side of the drive gear of the gear ratio between the input and output shafts and the same number of teeth and the same diameter as the drive gear, so that they mesh with the meshing with the drive gear also comb.
  • the first ⁇ n ⁇ the second gear are resiliently connected and non-rotatably connected to the drive shaft, wherein the corresponding spring means are biased such that when the gears mesh with the meshing with the drive gear, they are pressed radially viewed in the opposite direction.
  • This construction disadvantageously requires a large one Number of additional components, which significantly increases the manufacturing and assembly costs.
  • the present invention has for its object to provide a device for reducing rattle noise in a gear transmission, which is inexpensive to produce and assemble and avoids the disadvantages of the known from the prior art devices.
  • Another object of the invention is to provide a method for reducing rattle noise in a gear transmission.
  • the ring-shaped spring element has an outer toothing with the same number of teeth and tooth geometry as the driven gear is mounted such that its teeth are beveled with respect to the teeth of the gear by a predetermined deviation! are arranged offset.
  • the spring element can erfi ⁇ du ⁇ gsloom be connected to the driven gear by means of laser beam welding or current welding. It is also possible to connect the two parts by pressing or by positive engagement with each other. In this case, for the preparation of the connection radially considered the inner Tei! processed the Federeiementes, so that the teeth of the Federeiementes are not directly connected to the gear or with the teeth of the gear.
  • the spring element has a Telier spring geometry, so that after assembly the teeth of the spring element are pressed against the teeth of the gear due to the normal force generated by the TeSterfedergeometrie.
  • the spring element facing side of the driven gear is concave, so that after assembly of the plan executed Federeiementes a normal force is generated, which prints the teeth of the spring element against the teeth of the gear.
  • Fig. 1 A perspective view of a gear, a synchronizing ubensbauteils and a toothed, annular and circumferentially resilient spring element;
  • Fig. 2 A perspective view of a gear, a synchronizing ubensbauteils and a toothed ⁇ th, annular and spring-elastic in computers ⁇ chtung spring element in the mounted state;
  • Fig. 3 A schematic view of the driven
  • a gear comprising a toothed, annular and circumferentially resilient Federeiement and the Anlriebsschwrades which engage with each other;
  • FIG. 4 shows a schematic view of a part of the toothed, annular and circumferentially resilient spring element for illustrating the parameters used for calculating the counterforce
  • FIG. 5 shows a schematic view of a part of a weathered embodiment of the toothed, annular and circumferentially resilient spring element
  • Fig. 6 A schematic view of the driven
  • a gear comprising a toothed, annular and circumferentially resilient spring element and the drive gear, which engage with each other, wherein the position of the spring element at different values for the spring deflection is drawn;
  • FIG. 7 shows a schematic view of a part of the driven gear and the toothed, annular and spring-elastic spring element mounted thereon for the purpose of verifying the forces acting during operation of the gearbox to avoid rattling noises according to an advantageous development of the invention
  • FIG. 8 A schematic view of another embodiment of the driven gear and the toothed, annular and Umfa ⁇ gsraum resilient Federeeementes before ⁇ er assembly (left part of the figure) and in the assembled state;
  • Fig. 9 A schematic view of another embodiment of the driven gear and the toothed, annular and Umfa ⁇ gsraum resilient spring element before assembly (left part of the figure) and in the assembled state.
  • the drive gearwheel If the drive gearwheel is not rotating due to the irregularity of the motor speed! is accelerated, is due to the active connection with the ange- The driven gear accelerates it. However, if after this acceleration, the drive gear, for example due to a Zyünderdekompres ⁇ ion of the engine is decelerated, a shock between a tooth of the driven gear and a tooth of the drive gear, since the driven gear is not slowed down so much due to the inertia, whereby the rattling arises.
  • Tci J ⁇ x w, where J ⁇ is the mass moment of inertia when rotating about the z-axis, i. the axis of rotation of the gear is. It also applies:
  • the force F 0 can be determined as follows by the maximum angle of the transmission shafts, the outer diameter and the inner diameter of the gearwheel, and the density of the gearwheel material.
  • the counterforce F 0 generated by the fact that on the side facing away from the synchronization 2 of the driven gear 1, a toothed, annular and circumferentially resilient device Federelernent 3 is attached.
  • the annular spring element 3 has a toothed toothing with the same teeth and tooth geometry as the toothed wheel 1 and is connected to the toothed wheel 1 such that its teeth are offset with respect to the teeth of the toothed wheel 1 by a predetermined deviation.
  • Umfa ⁇ gsoplasty The spring deflection in Umfa ⁇ gs Vietnamese is known at the required preload force as a function of the biasing force, the modulus of elasticity of the spring material and dimensional parameters of the Federeleme ⁇ tes determinable, so that the spring element can be mounted accordingly.
  • the spring deflection or deflection SF 0 (afeo the deflection of a tooth of the spring element 3 in Umfa ⁇ gsraum) in dependence of the counterforce F c ;: determined as follows and corresponds to the bias of the spring element 3 when the driven gear 1 and the drive gear 4 are engaged.
  • V zz with ⁇ bmax maximum allowed bending stress of the
  • the maximum permitted spring deflection applies to the pretensioning of the spring element 3 and the further forces acting on the spring element 3; in the case of torque transmission by the gear pair, the forces due to the transmitted moments are higher than the spring force, resulting in a larger spring deflection , which according to the invention does not exceed s,
  • the object of FIG. 5 is an embodiment of the annular toothed spring element 3.
  • the length of the teeth is less than the length of the teeth of the gear 1 to be connected to the spring element 3, resulting in a smaller counterforce which can be generated while the thickness of the spring element remains the same results.
  • Fig. 6 is a schematic view of the driven gear 1, comprising a toothed, annular and circumferentially resilient spring element 3 and the drive gear 4, which are engaged with each other, wherein the position of the spring element 3 at different values for the spring deflection SR :! is drawn.
  • A the position of the spring element in the prestressed state by the interaction with a tooth 5 of the gear 4 is designated A;
  • Arrow B illustrates the direction of the counterforce F C: C denotes the position of the spring element 3 without AusSenkung (ie, before mounting the gear pair ⁇ and D, the position of the Federele- rnenfes 3 at maximum deflection S fnax .
  • the total counter force is increased, which allows the use of the spring element at higher loaded gears, without exceeding the maximum allowable bending stress of the spring material.
  • the load of the spring element can be reduced, resulting in the same in a longer life.
  • a further possibility for generating the normal force Fu is the subject matter of FIG. 9.
  • the side of the driven gear 1 facing the spring element 3 is concave, so that, after the assembly of the spring element 3 which is flat on the side facing the gear wheel 1, due to the elasticity properties of the spring element 3, a normal force F N is generated, which presses the teeth 6 of the spring element 3 against the teeth 7 of the gear 1.
  • the teeth 7 of the gear 1 zuge- turned surface of the teeth 6 of Federeieme ⁇ tes 3 be processed accordingly to increase Reiben friction coefficient.
  • any constructive training especially any spatial arrangement of the device for reducing rattle noise in a transmission per se and as far as technically feasible, falls within the scope of the present claims, without affecting the function of the device, as indicated in Talnen claims even if these training courses are not explicitly shown in the figures or in the description.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Gears, Cams (AREA)

Abstract

La présente invention concerne un dispositif destiné à réduire le bruit de cliquetis dans une transmission par engrenages. Ce dispositif comprend un élément ressort (3) annulaire denté à résilience circulaire monté contre la face du pignon mené (1) d'une paire de pignons, qui est opposée à l'élément synchroniseur (2). Cet élément ressort, qui présente le même nombre de dents et la même géométrie de dents que le pignon mené (1), est relié au pignon (1) de façon que les dents (6) de l'élément ressort présentent, par rapport aux dents (7) du pignon mené (1), un décalage angulaire correspondant à une inclinaison prescrite, de sorte que l'élément ressort (3) subisse une précontrainte lorsque le pignon mené est en prise à l'état monté avec le pignon menant (1).
PCT/EP2008/060446 2007-09-07 2008-08-08 Dispositif et procédé de réduction du bruit de cliquetis dans une transmission par engrenages WO2009033901A2 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE200710042762 DE102007042762A1 (de) 2007-09-07 2007-09-07 Einrichtung und Verfahren zur Reduzierung von Rasselgeräuschen in einem Zahnradgetriebe
DE102007042762.1 2007-09-07

Publications (2)

Publication Number Publication Date
WO2009033901A2 true WO2009033901A2 (fr) 2009-03-19
WO2009033901A3 WO2009033901A3 (fr) 2009-09-24

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PCT/EP2008/060446 WO2009033901A2 (fr) 2007-09-07 2008-08-08 Dispositif et procédé de réduction du bruit de cliquetis dans une transmission par engrenages

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DE (1) DE102007042762A1 (fr)
WO (1) WO2009033901A2 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2965029A1 (fr) * 2010-09-21 2012-03-23 Peugeot Citroen Automobiles Sa Ensemble a pignon et disque dente pour un engrenage avec rattrapage de jeu

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102013204781A1 (de) 2012-04-04 2013-10-10 Ford Global Technologies, Llc Getriebezahnrad
CN103382990B (zh) * 2013-07-01 2016-02-03 浙江吉利汽车研究院有限公司杭州分公司 一种改善齿轮啮合噪音的齿轮结构
CN103953695A (zh) * 2014-04-28 2014-07-30 四川大学 高阻尼滤波减速器

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5980563A (ja) * 1982-10-30 1984-05-10 Hino Motors Ltd エアコンプレツサ駆動用ギヤ装置
EP0881411A2 (fr) * 1997-05-26 1998-12-02 Bayerische Motoren Werke Aktiengesellschaft, Patentabteilung AJ-3 Roue dentée
DE102005041357A1 (de) * 2004-09-07 2006-04-06 Honda Motor Co., Ltd. Scherzahnrad und spielfreier Mechanismus
DE102005019349A1 (de) * 2005-04-26 2006-11-02 Bayerische Motoren Werke Ag Zahnrad
EP1748226A1 (fr) * 2005-07-28 2007-01-31 Rudolf Schwarz GmbH & Co. KG Roue dentée avec compensation de jeu

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2567229B1 (fr) 1984-07-05 1990-02-02 James Damas Procede et dispositif pour le rattrapage automatique des jeux dans les systemes a engrenages
US4811615A (en) 1987-12-14 1989-03-14 Borg-Warner Automotive, Inc. Mechanism for eliminating gear rattle in a shiftable transmission
DE9318792U1 (de) 1993-02-25 1994-03-03 Inst Maschinenelemente Uni Stu Getriebe
DE4426325B4 (de) 1993-08-26 2004-07-15 Volkswagen Ag Anti-Klappervorrichtung für ein Getriebe
DE19616503C2 (de) 1995-05-10 2003-08-28 Volkswagen Ag Getriebezahnrad mit magnetischer Zahnscheibe
DE19913563C1 (de) 1999-03-25 2000-06-08 Volkswagen Ag Antirasselzahnscheibe, insbesondere für ein Kraftfahrzeuggetriebe, und Verfahren zur Herstellung einer Antirasselzahnscheibe
SE526564C2 (sv) 2002-06-27 2005-10-11 Atlas Fahrzeugtechnik Gmbh Kugghjulsväxel med anordning för att hindra rassel

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5980563A (ja) * 1982-10-30 1984-05-10 Hino Motors Ltd エアコンプレツサ駆動用ギヤ装置
EP0881411A2 (fr) * 1997-05-26 1998-12-02 Bayerische Motoren Werke Aktiengesellschaft, Patentabteilung AJ-3 Roue dentée
DE102005041357A1 (de) * 2004-09-07 2006-04-06 Honda Motor Co., Ltd. Scherzahnrad und spielfreier Mechanismus
DE102005019349A1 (de) * 2005-04-26 2006-11-02 Bayerische Motoren Werke Ag Zahnrad
EP1748226A1 (fr) * 2005-07-28 2007-01-31 Rudolf Schwarz GmbH & Co. KG Roue dentée avec compensation de jeu

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2965029A1 (fr) * 2010-09-21 2012-03-23 Peugeot Citroen Automobiles Sa Ensemble a pignon et disque dente pour un engrenage avec rattrapage de jeu

Also Published As

Publication number Publication date
DE102007042762A1 (de) 2009-04-02
WO2009033901A3 (fr) 2009-09-24

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